US20190390882A1 - Refrigeration Appliance And Method For The Operation Thereof - Google Patents
Refrigeration Appliance And Method For The Operation Thereof Download PDFInfo
- Publication number
- US20190390882A1 US20190390882A1 US16/483,905 US201816483905A US2019390882A1 US 20190390882 A1 US20190390882 A1 US 20190390882A1 US 201816483905 A US201816483905 A US 201816483905A US 2019390882 A1 US2019390882 A1 US 2019390882A1
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- Prior art keywords
- temperature
- evaporator
- temperature zone
- compressor
- throttling point
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 34
- 238000000034 method Methods 0.000 title claims description 16
- 239000003507 refrigerant Substances 0.000 claims abstract description 44
- 238000001816 cooling Methods 0.000 claims abstract description 40
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 16
- 230000008859 change Effects 0.000 description 23
- 238000001704 evaporation Methods 0.000 description 9
- 230000000694 effects Effects 0.000 description 7
- 238000005259 measurement Methods 0.000 description 6
- 230000009467 reduction Effects 0.000 description 6
- 239000007788 liquid Substances 0.000 description 5
- 238000011017 operating method Methods 0.000 description 5
- 230000006978 adaptation Effects 0.000 description 3
- 238000012937 correction Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000010257 thawing Methods 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000000644 propagated effect Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Chemical compound O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
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- F25B41/062—
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
- F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
- F25D11/022—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures with two or more evaporators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/02—Compressor control
- F25B2600/025—Compressor control by controlling speed
- F25B2600/0253—Compressor control by controlling speed with variable speed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/11—Fan speed control
- F25B2600/112—Fan speed control of evaporator fans
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2700/00—Means for sensing or measuring; Sensors therefor
- F25D2700/10—Sensors measuring the temperature of the evaporator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2700/00—Means for sensing or measuring; Sensors therefor
- F25D2700/12—Sensors measuring the inside temperature
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B40/00—Technologies aiming at improving the efficiency of home appliances, e.g. induction cooking or efficient technologies for refrigerators, freezers or dish washers
Definitions
- the present invention relates to a refrigeration appliance, in particular a household refrigeration appliance, having a plurality of temperature zones, and a method for operating a refrigeration appliance of this kind.
- DE 10 2013 226 341 A1 discloses a refrigeration appliance having a first and a second temperature zone, in which a refrigerant circuit includes a compressor, a first evaporator for cooling the first temperature zone and, connected in series with the first evaporator, a second evaporator for cooling the second temperature zone, and in which a controllable expansion valve is connected upstream of each evaporator in the refrigerant circuit.
- the object is achieved, in a first aspect, in that in a refrigeration appliance having at least a first and a second temperature zone and a refrigerant circuit that includes a compressor, a first evaporator for cooling the first temperature zone and a second evaporator for cooling the second temperature zone, wherein the first evaporator is connected in series with the second evaporator, downstream thereof in the refrigerant circuit, and a first controllable throttling point is connected in the refrigerant circuit upstream of the first evaporator and downstream of the second evaporator, a first regulator controls the degree of opening of the first controllable throttling point, independently of the temperature of the first temperature zone, by way of the temperature of the second temperature zone.
- the basic concept here is that the mass flow in the refrigerant circuit is determined by the intake conditions (pressure and temperature) that prevail at a suction connector of the compressor and an outlet of the first evaporator leading to this suction connector. If the degree of opening of the first controllable throttling point is changed, it takes considerable time before this results in a change in the intake conditions (superheated gas at evaporation pressure) in the first evaporator, which lies between the first throttling point and the suction connector. As long as the intake conditions remain the same, adjustment of the degree of opening has no effect on the mass flow but does have an effect on the cooling power of the second evaporator, which lies upstream of the first controllable throttling point.
- the first regulator should be set up to increase the degree of opening of the first controllable throttling point when a setpoint temperature in the second temperature zone is exceeded, and to reduce the degree of opening of the first controllable throttling point when the temperature falls below a setpoint temperature in the second temperature zone. If for example the first regulator increases the degree of opening of the first controllable throttling point, then the pressure in the second evaporator falls, and the temperature thereof then also falls, with the result that the second temperature zone is cooled to a greater extent, as desired; conversely, the pressure and temperature of the second evaporator rise when the degree of opening of the first controllable throttling point is increased.
- the first regulator should be a proportional regulator, preferably a PI controller—that is to say the change in the degree of opening caused by the first regulator should include a term that is proportional to the deviation between the actual and the setpoint temperature, and preferably also a term that is proportional to the duration of the deviation.
- the second temperature zone should have a temperature sensor that is connected to an input to the first regulator. Further measurement variables are not required to control the first controllable throttling point—that is to say that this input may be the only input to the first regulator to receive a measurement variable.
- the compressor regulator should be set up to increase the speed of the compressor when a setpoint temperature in the last temperature zone, as seen in the direction of flow, is exceeded, and to reduce the speed of the compressor when the temperature falls below a setpoint temperature in the last temperature zone, as seen in the direction of flow.
- increasing the speed brings about not only a reduction in the pressure and temperature in the first evaporator but at the same time also an increase in the mass flow of refrigerant, with the result that an additional cooling power that is required is provided in one of the temperature zones.
- this favors rapid reinstatement of an energy-efficient steady operating state of the refrigeration appliance if the need for cooling has changed in all the temperature zones after a change in the ambient temperature.
- the compressor regulator may be coupled to the first regulator and be set up to increase the speed when the degree of opening of the first controllable throttling point is increased and to reduce it when the degree of opening of the first controllable throttling point is reduced. In this way, a proactive adaptation of the compressor speed is already possible at a point in time before a change in the degree of opening of the first controllable throttling point has had any effect on the cooling power of the first evaporator.
- the compressor regulator may also be a proportional or PI controller.
- the principle of the invention may be extended to an indefinite number of evaporators connected in series, for example by connecting a third evaporator, which is for controlling the temperature of a third temperature zone, upstream of the second evaporator in the refrigerant circuit by way of a second controllable throttling point, and by providing a second regulator in order to control the degree of opening of the second controllable throttling point by way of the temperature of the third temperature zone independently of the temperature of the second temperature zone.
- the compressor regulator may in that case also be coupled to the second regulator in order to take account of a change to the degree of opening of the second controllable throttling point when the compressor speed is established.
- the second regulator for controlling the second throttling point may operate entirely independently of the first regulator.
- both regulators may be implemented in the form of software on the same processor; the fact that they are mutually independent is seen in the fact that the two do not have access to the same temperature sensors, nor does one of the regulators use output data from the other as input data.
- an upstream controllable throttling point Between a pressure-side connector of the compressor and the evaporators there may be provided an upstream controllable throttling point.
- the degree of opening of this throttling point may be controlled by way of a drop in temperature at the first evaporator.
- a distribution regulator that is used for this purpose may in turn be independent, in the sense specified above, of the first, second and any further regulators.
- the object is further achieved by a method for operating a refrigeration appliance having at least a first and a second temperature zone and a refrigerant circuit that includes a compressor, a first evaporator for cooling the first temperature zone and a second evaporator for cooling the second temperature zone, wherein the first evaporator is connected in series with the second evaporator, downstream thereof in the refrigerant circuit, and a first controllable throttling point is connected in the refrigerant circuit upstream of the first evaporator and downstream of the second evaporator, in which the temperature of the second temperature zone is measured and the degree of opening of the first controllable throttling point, independently of the temperature of the first temperature zone, is controlled by way of the temperature of the second temperature zone.
- the speed of the compressor may be increased, and if the degree of opening of the same controllable throttling point is reduced the speed of the compressor may be reduced.
- FIG. 1 shows a schematic illustration of the refrigeration appliance according to the invention, according to a first embodiment
- FIG. 2 shows a flow chart of an operating method of a regulator of the refrigeration appliance
- FIG. 3 shows a modified detail of the refrigeration appliance
- FIG. 4 shows an illustration analogous to FIG. 1 , according to a second embodiment
- FIG. 5 shows a flow chart of an operating method of a compressor regulator.
- FIG. 1 shows schematically a refrigeration appliance according to a first embodiment of the invention.
- the refrigeration appliance is a combination appliance, and includes a plurality of temperature zones 1 , 2 , 3 , 4 , typically in the form of storage compartments in a housing 5 , which are each closable by a door and are separated from one another by heat-insulating walls.
- Each temperature zone 1 , 2 , 3 , 4 has an evaporator 6 , 7 , 8 and 9 respectively, which are connected within a refrigerant circuit having a compressor 10 and a condenser 11 .
- At least two evaporators, in this case the evaporators 6 , 7 , 8 are connected in series along a branch 13 of a refrigerant line 12 ; as shown, the refrigerant line 12 may have further branches 14 that are parallel to the branch 13 and supply further evaporators, in this case the evaporator 9 .
- Each evaporator 6 , 7 , 8 , 9 and the condenser 11 are combined with a respective ventilator 25 for increasing the heat transfer output.
- the temperature zones 1 , 2 , 3 , 4 may each be divided, in a manner known per se, into a storage compartment and an evaporator chamber, which receives the evaporator 6 , 7 , 8 or 9 , in which case the ventilator 25 drives the air exchange between the storage compartment and the evaporator chamber.
- the temperature difference that must prevail between an evaporator and the storage compartment cooled thereby in order to be able to keep the storage compartment at its setpoint temperature depends on the extent of the air exchange between the storage compartment and the evaporator chamber. If this is small, then the evaporator temperature must be low, and since maintaining a low evaporator temperature requires a high output from the compressor 11 the energy efficiency of the appliance is limited. Because of the low evaporator temperature, almost all the water vapor reaching the evaporator chamber from the storage compartment is precipitated at the evaporator, so the air humidity in the storage compartment is low. Conversely, the temperature difference between the evaporator and the storage compartment can be kept small if the ventilator 25 provides a high exchange of air.
- a high-pressure portion 15 of the refrigerant line 12 extends from a pressure-side connector 16 of the compressor 10 , through the condenser 11 and, in this case, a branching point 17 , to an upstream throttling point 18 , 19 .
- the upstream throttling point 18 , 19 has a constant flow resistance. In this case, it is formed in each case in a manner known per se by a capillary that opens into the evaporator 8 and 9 respectively.
- zone 3 is the warmest of the temperature zones 1 , 2 , 3 and zone 1 is the coldest.
- the zone 3 may for example form a normal refrigerator compartment
- the zone 2 may form a crisper compartment
- the zone 1 may form a freezer compartment.
- the branches 13 , 14 meet again at a merge point 22 , and a low-pressure portion 23 of the refrigerant line 12 leads to a suction connector 24 of the compressor 10 .
- a plurality of regulators 27 , 28 , 29 are implemented on a microprocessor 26 .
- the regulators 27 , 28 , 29 comprise utilities that share the processing power of the microprocessor 26 but do not access common data.
- Each regulator 27 , 28 , 29 receives and processes measurement values from one particular temperature sensor 30 , 31 and 32 respectively.
- FIG. 2 shows an operating method for the regulator 27 .
- step S 1 a measurement value of the temperature is read off from the associated sensor 30 .
- step S 2 the measurement value is compared with a setpoint temperature for the temperature zone 6 that is predetermined by the user. If the measurement value is within a tolerance range around the setpoint temperature, the method moves on to step S 3 , in which a time span ⁇ t is allowed to elapse before the program returns to step S 1 in order to repeat the method at regular intervals.
- step S 2 If it is determined in step S 2 that the measured temperature is above the tolerance range, then there is clearly a need for greater cooling power in the temperature zone 8 .
- the regulator 27 actuates the throttling point 20 in step S 4 in order to reduce the flow resistance thereof by a fixed value OR.
- the extent of the reduction may be fixedly predetermined or be proportional to the discrepancy between the measured temperature and the setpoint temperature.
- step S 2 is repeated and the measured temperature continues to be above the tolerance range, then the flow resistance of the throttling point 20 is reduced again. In this way, the flow resistance is varied in a manner proportional to the time integral of the standard deviation until the cooling requirement in the temperature zone 3 is sufficient and the temperature measured by the sensor 30 is within the tolerance range.
- step S 5 the regulator increases the flow resistance of the throttling point 20 by the value OR such that the temperature of the evaporator 8 rises. Increasing the flow resistance may, again, be repeated in successive iterations of the method.
- the operating method of the regulator 28 comprises the same steps as those illustrated in FIG. 2 .
- step S 1 the temperature of the temperature zone 2 or its evaporator 7 is read off from the sensor 31 ; in step S 2 , it is compared with the setpoint value established for this temperature zone and, depending on the result, the flow resistance of the throttling point 21 is maintained unchanged, reduced (step S 4 ) or increased (S 5 ).
- the extent OR of the change may but need not be identical to that used in the regulator 27 .
- the reduction results in a fall in the pressure and temperature in the evaporator 7 and, to a lesser extent, in the evaporator 8 , such that a greater cooling power is available in both evaporators 7 , 8 .
- the regulator 29 performs a slightly modified method, in which, if the setpoint temperature is exceeded, the speed of the compressor 10 is increased in step S 4 and, if the temperature falls below the setpoint temperature, it is reduced in step S 5 .
- S 4 results in a fall in the evaporating temperature in the associated evaporator 6 but at the same time an increase in the mass flow, so that overall more cooling power to be distributed to the different evaporators is available.
- S 5 raises the evaporating temperature while at the same time throttling the mass flow.
- the compressor regulator 29 may be coupled to the regulators 27 , 28 in order to receive therefrom information on a change in the flow resistance of the throttling points 20 , 21 controlled thereby and to track the speed of the compressor 10 that corresponds to the change before the change in the flow resistance has taken effect as a change to the temperature in the temperature zone 1 .
- a coupling of this kind may for example comprise, whenever one of the regulators 27 , 28 has increased or reduced the flow resistance by OR step S 4 , having the compressor regulator 29 reduce or raise the speed of the compressor 10 by a corresponding increment AU.
- FIG. 5 shows an operating method of the compressor regulator 29 that implements a coupling of this kind. Steps S 1 to S 5 correspond to those in FIG.
- step S 2 apart from the fact that if, in step S 2 , the measured temperature is above the setpoint value for the temperature zone 1 , then the speed is increased by a fixed value ⁇ U′ in step S 4 , or if it is below the setpoint value it is reduced by the value ⁇ U′ in step S 5 .
- a check is carried out in step S 6 of whether, since the preceding iteration, at least one of the regulators 27 , 28 has made a change OR to the flow resistance at its controllable throttling point 20 or 21 .
- the speed is reduced by ⁇ U (S 7 ), and in the event of a reduction it is increased by ⁇ U (S 8 ).
- the value of ⁇ U may differ, depending on the throttling point 20 or 21 at which the change to the flow resistance took place.
- controllable throttling points 18 ′, 19 ′ may be expansion valves of the same type as the ones at the throttling points 20 , 21 , but they may also—as shown in FIG. 3 —be a parallel circuit comprising a capillary 33 and a shutoff valve 34 .
- the pressure in the evaporator 8 may be brought into line with that of the condenser 11 , with the result that refrigerant in the evaporator 8 condenses instead of evaporating, and the temperature zone 3 is heated by the heat this releases.
- the regulators 28 , 29 continue to operate by the method described in conjunction with FIG. 2 in order to distribute the available cooling power to the temperature zones 1 , 2 as required.
- FIG. 4 shows a diagram analogous to FIG. 1 , of a refrigeration appliance according to a further embodiment of the invention.
- Identical reference numerals in both figures designate components that have already been described in conjunction with FIG. 1 ; statements made in relation to these components in the description of FIG. 1 also apply here and need not be repeated.
- An additional temperature sensor 35 is mounted adjacent to the infeed point for the evaporator 6 in order to detect the evaporating temperature thereof reliably even if the extent to which it is filled with liquid refrigerant is not sufficient to keep it at the evaporating temperature over its entire extent.
- the temperature sensor 35 may also serve to control a defrosting heater for the purpose of defrosting the evaporator 6 .
- a further temperature sensor 36 is also mounted at an outlet of the evaporator 6 or at the low-pressure portion 23 , in order to detect the temperature of the refrigerant vapor flowing back to the compressor 10 .
- a further regulator 37 is connected to both temperature sensors 35 , 36 in order to monitor the difference between the temperatures and to use this difference to control the flow resistance of an expansion valve that is inserted as a controllable throttling point 18 ′ between the condenser 11 and the evaporator 8 . Too small a difference is an indication of a high filling level of the evaporator 6 and the possibility that liquid refrigerant is reaching the low-pressure portion 23 as a result of overfilling.
- the regulator 37 increases the flow resistance of the throttling point 18 ′, such that more liquid refrigerant builds up upstream of the throttling point 18 ′ and in response the quantity of refrigerant in the evaporator 6 falls. If by contrast there is too great a difference—that is to say if the temperature measured by the sensor 35 , of the refrigerant vapor that is removed by suction, is only a little lower than the compartment temperature of the temperature zone 1 , then this is an indication of insufficient filling of the evaporator 6 , and the flow resistance of the throttling point 18 ′ is reduced to allow more liquid refrigerant to penetrate through the evaporators 8 , 7 and into the evaporator 6 .
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Abstract
Description
- The present invention relates to a refrigeration appliance, in particular a household refrigeration appliance, having a plurality of temperature zones, and a method for operating a refrigeration appliance of this kind.
- DE 10 2013 226 341 A1 discloses a refrigeration appliance having a first and a second temperature zone, in which a refrigerant circuit includes a compressor, a first evaporator for cooling the first temperature zone and, connected in series with the first evaporator, a second evaporator for cooling the second temperature zone, and in which a controllable expansion valve is connected upstream of each evaporator in the refrigerant circuit.
- In this known refrigeration appliance, if there is an unmet need for cooling in a temperature zone, throttling at the controllable expansion valve lying upstream of the evaporator for this temperature zone is increased, with the result that the evaporating temperature in the relevant evaporator falls. In order to prevent this measure from also having an effect on other evaporators downstream in the refrigerant circuit, throttling in an expansion valve downstream of the relevant evaporator is reduced as a counter-measure, with the result that throttling of the expansion valves connected in series remains unchanged: in this way, the mass flow of refrigerant in the refrigerant circuit also remains unchanged overall, with the result that cooling power that is additionally available in this way in the relevant temperature zone has to be withheld from the other temperature zones. If an unmet need for cooling then arises in another temperature zone, then the available cooling power is redistributed again, which results in undesired fluctuations in temperature. As a result of redistributing the cooling power, it is not possible to take account of the changing need for cooling in all the temperature zones which in practice unavoidably arises as a result of changes in temperature in the area surrounding the refrigeration appliance.
- It is the object of the invention to develop a refrigeration appliance of the type known from DE 10 2013 226 341 A1, and to provide a method for operation of a refrigeration appliance, which enable simple and stable temperature control of the different temperature zones.
- The object is achieved, in a first aspect, in that in a refrigeration appliance having at least a first and a second temperature zone and a refrigerant circuit that includes a compressor, a first evaporator for cooling the first temperature zone and a second evaporator for cooling the second temperature zone, wherein the first evaporator is connected in series with the second evaporator, downstream thereof in the refrigerant circuit, and a first controllable throttling point is connected in the refrigerant circuit upstream of the first evaporator and downstream of the second evaporator, a first regulator controls the degree of opening of the first controllable throttling point, independently of the temperature of the first temperature zone, by way of the temperature of the second temperature zone.
- The basic concept here is that the mass flow in the refrigerant circuit is determined by the intake conditions (pressure and temperature) that prevail at a suction connector of the compressor and an outlet of the first evaporator leading to this suction connector. If the degree of opening of the first controllable throttling point is changed, it takes considerable time before this results in a change in the intake conditions (superheated gas at evaporation pressure) in the first evaporator, which lies between the first throttling point and the suction connector. As long as the intake conditions remain the same, adjustment of the degree of opening has no effect on the mass flow but does have an effect on the cooling power of the second evaporator, which lies upstream of the first controllable throttling point.
- Only once there is a change to the intake conditions is there also a change in the cooling power of the first evaporator lying downstream of the first controllable throttling point. In order to counter this change, advantageously a compressor regulator, which controls adaptation of the compressor speed by way of the temperature of the first temperature zone, is provided. It is only this change in speed which also results in a change in the mass flow. Depending on the mass flow, the cooling power that can be distributed to the different temperature zones also changes, with the result that the change to the cooling power affecting the second evaporator need not be compensated, or at least not in its entirety, by a countering change in power at the first evaporator. Thus, it is possible to decouple regulation of the individual temperature zones in a simple manner. Because of inertia in the system, it is immaterial when a change to the total cooling power as a result of a briefly unmet need for cooling in an individual compartment occurs.
- Independence of the temperature in the first temperature zone simplifies control of the first throttling point, since there is no need for two influencing variables to be taken into account at the same time.
- The first regulator should be set up to increase the degree of opening of the first controllable throttling point when a setpoint temperature in the second temperature zone is exceeded, and to reduce the degree of opening of the first controllable throttling point when the temperature falls below a setpoint temperature in the second temperature zone. If for example the first regulator increases the degree of opening of the first controllable throttling point, then the pressure in the second evaporator falls, and the temperature thereof then also falls, with the result that the second temperature zone is cooled to a greater extent, as desired; conversely, the pressure and temperature of the second evaporator rise when the degree of opening of the first controllable throttling point is increased.
- In order to enable rapid adaptation of the degree of opening to a change in conditions, the first regulator should be a proportional regulator, preferably a PI controller—that is to say the change in the degree of opening caused by the first regulator should include a term that is proportional to the deviation between the actual and the setpoint temperature, and preferably also a term that is proportional to the duration of the deviation.
- The second temperature zone should have a temperature sensor that is connected to an input to the first regulator. Further measurement variables are not required to control the first controllable throttling point—that is to say that this input may be the only input to the first regulator to receive a measurement variable.
- Typically, there is no controllable throttling point connected downstream of the first evaporator. So that it is also possible to influence the temperature of this, it is possible, as mentioned above, to provide a compressor regulator that controls the speed of the compressor by way of the temperature and/or an unmet need for cooling of the temperature zone that comes last, as seen in the direction of flow.
- The compressor regulator should be set up to increase the speed of the compressor when a setpoint temperature in the last temperature zone, as seen in the direction of flow, is exceeded, and to reduce the speed of the compressor when the temperature falls below a setpoint temperature in the last temperature zone, as seen in the direction of flow. Similarly to the manner in which the degree of opening the first controllable throttling point is increased, as explained above, increasing the speed brings about not only a reduction in the pressure and temperature in the first evaporator but at the same time also an increase in the mass flow of refrigerant, with the result that an additional cooling power that is required is provided in one of the temperature zones. Among other things, this favors rapid reinstatement of an energy-efficient steady operating state of the refrigeration appliance if the need for cooling has changed in all the temperature zones after a change in the ambient temperature.
- The compressor regulator may be coupled to the first regulator and be set up to increase the speed when the degree of opening of the first controllable throttling point is increased and to reduce it when the degree of opening of the first controllable throttling point is reduced. In this way, a proactive adaptation of the compressor speed is already possible at a point in time before a change in the degree of opening of the first controllable throttling point has had any effect on the cooling power of the first evaporator.
- The compressor regulator may also be a proportional or PI controller.
- The principle of the invention may be extended to an indefinite number of evaporators connected in series, for example by connecting a third evaporator, which is for controlling the temperature of a third temperature zone, upstream of the second evaporator in the refrigerant circuit by way of a second controllable throttling point, and by providing a second regulator in order to control the degree of opening of the second controllable throttling point by way of the temperature of the third temperature zone independently of the temperature of the second temperature zone.
- It goes without saying that the compressor regulator may in that case also be coupled to the second regulator in order to take account of a change to the degree of opening of the second controllable throttling point when the compressor speed is established.
- The second regulator for controlling the second throttling point may operate entirely independently of the first regulator. In practice, in fact, both regulators may be implemented in the form of software on the same processor; the fact that they are mutually independent is seen in the fact that the two do not have access to the same temperature sensors, nor does one of the regulators use output data from the other as input data.
- Between a pressure-side connector of the compressor and the evaporators there may be provided an upstream controllable throttling point. In order to control the distribution of refrigerant between the evaporators and a high-pressure portion of the refrigerant circuit, the degree of opening of this throttling point may be controlled by way of a drop in temperature at the first evaporator. A distribution regulator that is used for this purpose may in turn be independent, in the sense specified above, of the first, second and any further regulators.
- For an efficient heat transfer between the evaporator and the associated temperature zone, there may be associated with at least one of the evaporators a ventilator for driving air current that streams over a surface of the evaporator.
- In order to control the air humidity in the temperature zone, this ventilator may be capable of being switched between at least two operating modes of different speeds. One of these modes may be operation at high speed, which keeps the difference in temperature between the temperature zone and the evaporator small and accordingly has only a small dehumidifying effect on the circulated air at the evaporator. Although the evaporator temperature, relatively high in this mode, enables efficient generation of refrigeration, because of the high ventilator output it does not achieve an ideal level of efficiency. In a second mode, the ventilator can be switched off or operated at low speed, with the result that the evaporator reaches low temperatures which, although they are typically not of ideal energy efficiency either, have a pronounced air dehumidifying effect. In a further mode, the ventilator can be operated at medium speed in order to optimize the energy efficiency of the appliance.
- The object is further achieved by a method for operating a refrigeration appliance having at least a first and a second temperature zone and a refrigerant circuit that includes a compressor, a first evaporator for cooling the first temperature zone and a second evaporator for cooling the second temperature zone, wherein the first evaporator is connected in series with the second evaporator, downstream thereof in the refrigerant circuit, and a first controllable throttling point is connected in the refrigerant circuit upstream of the first evaporator and downstream of the second evaporator, in which the temperature of the second temperature zone is measured and the degree of opening of the first controllable throttling point, independently of the temperature of the first temperature zone, is controlled by way of the temperature of the second temperature zone.
- A variable speed of the compressor can be controlled by way of the measured temperature of the first temperature zone.
- Further, if the degree of opening of the first (or the second, if present) controllable throttling point is increased the speed of the compressor may be increased, and if the degree of opening of the same controllable throttling point is reduced the speed of the compressor may be reduced.
- Further features and advantages of the invention become apparent from the description of exemplary embodiments, given with reference to the attached figures, in which:
-
FIG. 1 shows a schematic illustration of the refrigeration appliance according to the invention, according to a first embodiment; -
FIG. 2 shows a flow chart of an operating method of a regulator of the refrigeration appliance; -
FIG. 3 shows a modified detail of the refrigeration appliance; -
FIG. 4 shows an illustration analogous toFIG. 1 , according to a second embodiment; and -
FIG. 5 shows a flow chart of an operating method of a compressor regulator. -
FIG. 1 shows schematically a refrigeration appliance according to a first embodiment of the invention. The refrigeration appliance is a combination appliance, and includes a plurality oftemperature zones housing 5, which are each closable by a door and are separated from one another by heat-insulating walls. - Each
temperature zone evaporator compressor 10 and acondenser 11. At least two evaporators, in this case theevaporators evaporator 9. - Each
evaporator condenser 11 are combined with arespective ventilator 25 for increasing the heat transfer output. - The
temperature zones evaporator ventilator 25 drives the air exchange between the storage compartment and the evaporator chamber. - The temperature difference that must prevail between an evaporator and the storage compartment cooled thereby in order to be able to keep the storage compartment at its setpoint temperature depends on the extent of the air exchange between the storage compartment and the evaporator chamber. If this is small, then the evaporator temperature must be low, and since maintaining a low evaporator temperature requires a high output from the
compressor 11 the energy efficiency of the appliance is limited. Because of the low evaporator temperature, almost all the water vapor reaching the evaporator chamber from the storage compartment is precipitated at the evaporator, so the air humidity in the storage compartment is low. Conversely, the temperature difference between the evaporator and the storage compartment can be kept small if theventilator 25 provides a high exchange of air. In that case, the output requirements made of thecompressor 10 are reduced, but in exchange more energy is consumed for operation of thefan 25. Because of the small difference in temperature, condensation on the evaporator is also small, and a high air humidity can be maintained in the storage compartment. Between these two extreme cases there is an optimum-efficiency operating mode in which the output of both thecompressor 10 and theventilator 25 is small but not minimal, and the sum of their outputs is at a minimum. It may be provided for the user to be able to select one of these operating modes for eachtemperature zone - A high-pressure portion 15 of the refrigerant line 12 extends from a pressure-
side connector 16 of thecompressor 10, through thecondenser 11 and, in this case, a branchingpoint 17, to anupstream throttling point upstream throttling point evaporator - Connected in series downstream of the
evaporator 8 there are acontrollable throttling point 20, theevaporator 7, a furthercontrollable throttling point 21 and theevaporator 6. Since the pressure in the refrigerant line 12 falls after eachthrottling point zone 3 is the warmest of thetemperature zones zone 1 is the coldest. In this way, thezone 3 may for example form a normal refrigerator compartment, thezone 2 may form a crisper compartment and thezone 1 may form a freezer compartment. - Downstream of the
evaporator 6, the branches 13, 14 meet again at amerge point 22, and a low-pressure portion 23 of the refrigerant line 12 leads to asuction connector 24 of thecompressor 10. - A plurality of
regulators microprocessor 26. Theregulators microprocessor 26 but do not access common data. Eachregulator particular temperature sensor -
FIG. 2 shows an operating method for theregulator 27. In step S1, a measurement value of the temperature is read off from the associatedsensor 30. In step S2, the measurement value is compared with a setpoint temperature for thetemperature zone 6 that is predetermined by the user. If the measurement value is within a tolerance range around the setpoint temperature, the method moves on to step S3, in which a time span Δt is allowed to elapse before the program returns to step S1 in order to repeat the method at regular intervals. - If it is determined in step S2 that the measured temperature is above the tolerance range, then there is clearly a need for greater cooling power in the
temperature zone 8. In this case, theregulator 27 actuates thethrottling point 20 in step S4 in order to reduce the flow resistance thereof by a fixed value OR. The extent of the reduction may be fixedly predetermined or be proportional to the discrepancy between the measured temperature and the setpoint temperature. - As a result of reducing the flow resistance, the evaporating temperature in the
evaporator 8 falls, and cooling of thetemperature zone 3 becomes more intense. At the same time, more liquid refrigerant arrives in theevaporator 7 although more refrigerant does not flow away therefrom, with the result that over time the pressure there rises and the cooling power falls. - If, after the waiting time Δt, step S2 is repeated and the measured temperature continues to be above the tolerance range, then the flow resistance of the
throttling point 20 is reduced again. In this way, the flow resistance is varied in a manner proportional to the time integral of the standard deviation until the cooling requirement in thetemperature zone 3 is sufficient and the temperature measured by thesensor 30 is within the tolerance range. - If, by contrast, the measured temperature in step S2 is below the tolerance range, then in step S5 the regulator increases the flow resistance of the
throttling point 20 by the value OR such that the temperature of theevaporator 8 rises. Increasing the flow resistance may, again, be repeated in successive iterations of the method. - In the context of the method, there is no need to take into account the operating mode of the
ventilator 25 that has been selected for thetemperature zone 3; if the user changes the operating mode, this results initially in a change in the temperature measured by thesensor 30 and then, in the course of one or more iterations of the method described above, in an adjustment of the flow resistance, as a result of which thetemperature zone 3 reaches its setpoint temperature again. - The operating method of the
regulator 28 comprises the same steps as those illustrated inFIG. 2 . In step S1, the temperature of thetemperature zone 2 or itsevaporator 7 is read off from thesensor 31; in step S2, it is compared with the setpoint value established for this temperature zone and, depending on the result, the flow resistance of thethrottling point 21 is maintained unchanged, reduced (step S4) or increased (S5). The extent OR of the change may but need not be identical to that used in theregulator 27. The reduction results in a fall in the pressure and temperature in theevaporator 7 and, to a lesser extent, in theevaporator 8, such that a greater cooling power is available in bothevaporators - Where a reduction has become necessary because, as a result of the increased need for cooling of the
temperature zone 3, theregulator 27 has reduced the flow resistance of thethrottling point 20 and so the temperature in theevaporator 7 has risen, the reduction of the flow resistance of thethrottling point 21 contributes to meeting the need for cooling of thetemperature zone 3 quickly. - Accordingly, where there is an increase in the flow resistance of the
throttling point 21, the pressure in theevaporator 7 and, to a lesser extent, in theevaporator 8 rises. - If the temperature measured by the
sensor 32 in thetemperature zone 1 differs from the setpoint temperature, there is no throttling point downstream of theevaporator 6 which could be used to influence the evaporating temperature. For this reason, theregulator 29 performs a slightly modified method, in which, if the setpoint temperature is exceeded, the speed of thecompressor 10 is increased in step S4 and, if the temperature falls below the setpoint temperature, it is reduced in step S5. As in the case of theregulators evaporator 6 but at the same time an increase in the mass flow, so that overall more cooling power to be distributed to the different evaporators is available. Conversely, S5 raises the evaporating temperature while at the same time throttling the mass flow. - In this way, a change in the cooling requirement is propagated through the refrigeration appliance step by step: in the case of an increased need for cooling in the
temperature zone 3, meeting the need by opening thethrottling point 20 has the result, with some delay, that the need for cooling in thetemperature zone 2 is no longer entirely met, and a correction in this respect of the degree of opening of thethrottling point 21 results in heating thetemperature zone 1 and a subsequent correction of the compressor speed. - In order to make convergence of the regulation faster, it may be provided for the
compressor regulator 29 to be coupled to theregulators compressor 10 that corresponds to the change before the change in the flow resistance has taken effect as a change to the temperature in thetemperature zone 1. A coupling of this kind may for example comprise, whenever one of theregulators compressor regulator 29 reduce or raise the speed of thecompressor 10 by a corresponding increment AU.FIG. 5 shows an operating method of thecompressor regulator 29 that implements a coupling of this kind. Steps S1 to S5 correspond to those inFIG. 2 , apart from the fact that if, in step S2, the measured temperature is above the setpoint value for thetemperature zone 1, then the speed is increased by a fixed value ΔU′ in step S4, or if it is below the setpoint value it is reduced by the value ΔU′ in step S5. In each iteration of the method, a check is carried out in step S6 of whether, since the preceding iteration, at least one of theregulators controllable throttling point throttling point - In a modified embodiment, the capillaries at the throttling points 18, 19 in
FIG. 1 are replaced by controllable throttling points 18′, 19′. These controllable throttling points 18′, 19′ may be expansion valves of the same type as the ones at the throttling points 20, 21, but they may also—as shown inFIG. 3 —be a parallel circuit comprising a capillary 33 and ashutoff valve 34. By making the flow resistance of thethrottling point 18′ negligibly small, for example by opening theshutoff valve 34, the pressure in theevaporator 8 may be brought into line with that of thecondenser 11, with the result that refrigerant in theevaporator 8 condenses instead of evaporating, and thetemperature zone 3 is heated by the heat this releases. - In this case too, the
regulators FIG. 2 in order to distribute the available cooling power to thetemperature zones -
FIG. 4 shows a diagram analogous toFIG. 1 , of a refrigeration appliance according to a further embodiment of the invention. Identical reference numerals in both figures designate components that have already been described in conjunction withFIG. 1 ; statements made in relation to these components in the description ofFIG. 1 also apply here and need not be repeated. Anadditional temperature sensor 35 is mounted adjacent to the infeed point for theevaporator 6 in order to detect the evaporating temperature thereof reliably even if the extent to which it is filled with liquid refrigerant is not sufficient to keep it at the evaporating temperature over its entire extent. Thetemperature sensor 35 may also serve to control a defrosting heater for the purpose of defrosting theevaporator 6. Afurther temperature sensor 36 is also mounted at an outlet of theevaporator 6 or at the low-pressure portion 23, in order to detect the temperature of the refrigerant vapor flowing back to thecompressor 10. Afurther regulator 37 is connected to bothtemperature sensors controllable throttling point 18′ between thecondenser 11 and theevaporator 8. Too small a difference is an indication of a high filling level of theevaporator 6 and the possibility that liquid refrigerant is reaching the low-pressure portion 23 as a result of overfilling. If this is the case, theregulator 37 increases the flow resistance of thethrottling point 18′, such that more liquid refrigerant builds up upstream of thethrottling point 18′ and in response the quantity of refrigerant in theevaporator 6 falls. If by contrast there is too great a difference—that is to say if the temperature measured by thesensor 35, of the refrigerant vapor that is removed by suction, is only a little lower than the compartment temperature of thetemperature zone 1, then this is an indication of insufficient filling of theevaporator 6, and the flow resistance of thethrottling point 18′ is reduced to allow more liquid refrigerant to penetrate through theevaporators evaporator 6. -
- 1 Temperature zone
- 2 Temperature zone
- 3 Temperature zone
- 4 Temperature zone
- 5 Housing
- 6 Evaporator
- 7 Evaporator
- 8 Evaporator
- 9 Evaporator
- 10 Compressor
- 11 Condenser
- 12 Refrigerant line
- 13 Branch
- 14 Branch
- 15 High-pressure portion
- 16 Pressure-side connector
- 17 Branching point
- 18 Throttling point
- 19 Throttling point
- 20 Throttling point
- 21 Throttling point
- 22 Merge point
- 23 Low-pressure portion
- 24 Suction connector
- 25 Ventilator
- 26 Microprocessor
- 27 Regulator
- 28 Regulator
- 29 Regulator
- 30 Temperature sensor
- 31 Temperature sensor
- 32 Temperature sensor
- 33 Capillary
- 34 Shutoff valve
- 35 Temperature sensor
- 36 Temperature sensor
- 37 Regulator
Claims (16)
Applications Claiming Priority (3)
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DE102017205426.3 | 2017-03-30 | ||
DE102017205426.3A DE102017205426A1 (en) | 2017-03-30 | 2017-03-30 | Refrigeration appliance and operating method for it |
PCT/EP2018/057009 WO2018177809A1 (en) | 2017-03-30 | 2018-03-20 | Refrigeration appliance and method for the operation thereof |
Publications (1)
Publication Number | Publication Date |
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US20190390882A1 true US20190390882A1 (en) | 2019-12-26 |
Family
ID=61750129
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US16/483,905 Abandoned US20190390882A1 (en) | 2017-03-30 | 2018-03-20 | Refrigeration Appliance And Method For The Operation Thereof |
Country Status (5)
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US (1) | US20190390882A1 (en) |
EP (1) | EP3601902B1 (en) |
CN (1) | CN110462307A (en) |
DE (1) | DE102017205426A1 (en) |
WO (1) | WO2018177809A1 (en) |
Cited By (1)
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US20210239382A1 (en) * | 2020-02-04 | 2021-08-05 | Samsung Electronics Co., Ltd. | Refrigerator |
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Publication number | Priority date | Publication date | Assignee | Title |
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DE102019218352A1 (en) * | 2019-11-27 | 2021-05-27 | BSH Hausgeräte GmbH | Refrigerator with a compartment that can be used in various ways |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
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JPS50150956A (en) * | 1974-05-25 | 1975-12-04 | ||
JPS51137154U (en) * | 1975-04-28 | 1976-11-05 | ||
JP2000356447A (en) * | 1999-06-14 | 2000-12-26 | Matsushita Refrig Co Ltd | Inverter for refrigerating system |
JP2001116423A (en) * | 1999-10-15 | 2001-04-27 | Fuji Electric Co Ltd | Deep freezing air conditioner |
JP2001133112A (en) * | 1999-11-10 | 2001-05-18 | Matsushita Refrig Co Ltd | Refrigerator |
DE102012211270A1 (en) * | 2012-06-29 | 2014-01-02 | BSH Bosch und Siemens Hausgeräte GmbH | Refrigeration device has controller for controlling one valve and another valve depending on one temperature in one frozen food compartment and another temperature in another frozen food compartment |
CN102997610B (en) * | 2012-12-31 | 2015-01-21 | 合肥美的电冰箱有限公司 | Refrigeration plant control method |
DE102013223737A1 (en) * | 2013-11-20 | 2015-05-21 | BSH Hausgeräte GmbH | Single-circuit refrigerating appliance |
DE102013226341A1 (en) | 2013-12-18 | 2015-06-18 | BSH Hausgeräte GmbH | Refrigerating appliance with several cold compartments |
CN105276913B (en) * | 2015-04-13 | 2018-01-30 | Tcl智能科技(合肥)有限公司 | Wind cooling refrigerator rotation speed of fan method of adjustment and wind cooling refrigerator |
DE102015211960A1 (en) * | 2015-06-26 | 2016-12-29 | BSH Hausgeräte GmbH | Refrigeration unit with humidity monitoring |
-
2017
- 2017-03-30 DE DE102017205426.3A patent/DE102017205426A1/en not_active Withdrawn
-
2018
- 2018-03-20 US US16/483,905 patent/US20190390882A1/en not_active Abandoned
- 2018-03-20 CN CN201880023034.9A patent/CN110462307A/en active Pending
- 2018-03-20 WO PCT/EP2018/057009 patent/WO2018177809A1/en unknown
- 2018-03-20 EP EP18712584.4A patent/EP3601902B1/en active Active
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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US20210239382A1 (en) * | 2020-02-04 | 2021-08-05 | Samsung Electronics Co., Ltd. | Refrigerator |
Also Published As
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EP3601902B1 (en) | 2022-05-18 |
DE102017205426A1 (en) | 2018-10-04 |
CN110462307A (en) | 2019-11-15 |
EP3601902A1 (en) | 2020-02-05 |
WO2018177809A1 (en) | 2018-10-04 |
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