CN116951867A - Control method for refrigerating and freezing device and refrigerating and freezing device - Google Patents
Control method for refrigerating and freezing device and refrigerating and freezing device Download PDFInfo
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- CN116951867A CN116951867A CN202310793433.6A CN202310793433A CN116951867A CN 116951867 A CN116951867 A CN 116951867A CN 202310793433 A CN202310793433 A CN 202310793433A CN 116951867 A CN116951867 A CN 116951867A
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- 238000007710 freezing Methods 0.000 title claims abstract description 59
- 230000008014 freezing Effects 0.000 title claims abstract description 52
- 238000000034 method Methods 0.000 title claims abstract description 34
- 238000005057 refrigeration Methods 0.000 claims abstract description 175
- 238000001816 cooling Methods 0.000 claims abstract description 96
- 230000006835 compression Effects 0.000 claims abstract description 72
- 238000007906 compression Methods 0.000 claims abstract description 72
- 238000001514 detection method Methods 0.000 claims description 20
- 239000004973 liquid crystal related substance Substances 0.000 claims 2
- 238000005265 energy consumption Methods 0.000 abstract description 4
- 230000002035 prolonged effect Effects 0.000 abstract description 3
- 238000004781 supercooling Methods 0.000 description 22
- 238000003860 storage Methods 0.000 description 11
- 239000003570 air Substances 0.000 description 7
- 230000000875 corresponding effect Effects 0.000 description 6
- 235000013305 food Nutrition 0.000 description 6
- 238000004321 preservation Methods 0.000 description 6
- 230000001276 controlling effect Effects 0.000 description 5
- 239000000463 material Substances 0.000 description 5
- 238000009826 distribution Methods 0.000 description 4
- 239000002699 waste material Substances 0.000 description 4
- 230000002596 correlated effect Effects 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 239000012080 ambient air Substances 0.000 description 2
- 238000004590 computer program Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000005485 electric heating Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 230000007246 mechanism Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 238000010257 thawing Methods 0.000 description 2
- 238000012546 transfer Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 230000009477 glass transition Effects 0.000 description 1
- 230000036541 health Effects 0.000 description 1
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- 238000011160 research Methods 0.000 description 1
- 239000004065 semiconductor Substances 0.000 description 1
- 238000004017 vitrification Methods 0.000 description 1
Classifications
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B25/00—Machines, plants or systems, using a combination of modes of operation covered by two or more of the groups F25B1/00 - F25B23/00
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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
- F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
- F25D17/04—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection
- F25D17/06—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation
- F25D17/062—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation in household refrigerators
- F25D17/065—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating air, e.g. by convection by forced circulation in household refrigerators with compartments at different temperatures
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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
- F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
- F25D19/04—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors with more than one refrigeration unit
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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
- F25D29/00—Arrangement or mounting of control or safety devices
-
- 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
- F25D2600/00—Control issues
- F25D2600/06—Controlling according to a predetermined profile
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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
-
- 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
- F25D2700/14—Sensors measuring the temperature outside the refrigerator or freezer
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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
- Y02B40/00—Technologies aiming at improving the efficiency of home appliances, e.g. induction cooking or efficient technologies for refrigerators, freezers or dish washers
Abstract
The application provides a control method for a refrigeration and freezing device and the refrigeration and freezing device. A refrigeration and freezer includes a cabinet defining a cryogenic compartment, a vapor compression refrigeration system for cooling the cryogenic compartment, and a stirling refrigeration system. The control method comprises the following steps: when the room temperature of the cryogenic room is greater than or equal to a set cryogenic temperature, judging whether the room temperature is greater than or equal to a preset switching temperature; if so, controlling the vapor compression refrigeration system to cool the cryogenic compartment, and stopping cooling the cryogenic compartment by the Stirling refrigeration system; if not, the Stirling refrigerating system is controlled to cool the cryogenic compartment, and the vapor compression refrigerating system stops cooling the cryogenic compartment, so that the refrigerating efficiency of the refrigerating and freezing device to the cryogenic compartment is improved as a whole, the energy consumption of the refrigerating and freezing device is reduced, and the service life of the Stirling refrigerator is prolonged.
Description
The application relates to a control method for a refrigeration and freezing device and a divisional application of the refrigeration and freezing device:
filing date of the original application: 20191227
Application number of the original application: 201911382785.2
The application of the original application creates the name: a control method for a refrigerating and freezing device and a refrigerating and freezing device.
Technical Field
The present application relates to the field of refrigeration, and more particularly, to a control method for a refrigeration and freezing apparatus and a refrigeration and freezing apparatus.
Background
With the importance of people on health, the household reserve of high-end food materials is also increasing. Through researches, the storage temperature of the food material is lower than the vitrification temperature of the food material, the property of the food material is relatively stable, and the quality guarantee period is greatly prolonged. Wherein the glass transition temperature of the food material is mostly concentrated at-80 ℃ to-30 ℃.
The existing domestic refrigerators are refrigerated by adopting a vapor compression mode, and refrigerators adopting semiconductor, magnetic refrigeration and other modes are developed in recent years, but the temperature in the refrigerator is difficult to reach below-30 ℃ due to the limitation of refrigeration efficiency. The Stirling refrigerating system is adopted for refrigerating in the fields of aerospace, medical treatment and the like, and the refrigerating temperature of the Stirling refrigerating system can be lower than minus 200 ℃.
Disclosure of Invention
It is an object of the first aspect of the present application to provide a control method for a refrigeration and freezing apparatus, which can improve the overall refrigeration efficiency of the refrigeration and freezing apparatus.
A further object of the first aspect of the application is to avoid undesirable waste of energy.
It is a further object of the first aspect of the present application to avoid frequent switching between vapor compression refrigeration systems and stirling refrigeration systems.
An object of the second aspect of the present application is to provide a refrigerating and freezing apparatus.
According to a first aspect of the present application there is provided a control method for a refrigeration chiller including a cabinet defining a cryogenic compartment, a vapour compression refrigeration system for cooling the cryogenic compartment and a stirling refrigeration system, the control method comprising:
when the room temperature of the cryogenic room is greater than or equal to a set cryogenic temperature, judging whether the room temperature is greater than or equal to a preset switching temperature;
if yes, controlling the vapor compression refrigeration system to cool the cryogenic compartment, and stopping cooling the cryogenic compartment by the Stirling refrigeration system;
and if not, controlling the Stirling refrigerating system to cool the cryogenic compartment, and stopping cooling the cryogenic compartment by the vapor compression refrigerating system.
Optionally, the tank further defines a common cooling compartment, and the vapor compression refrigeration system is further configured to cool the common cooling compartment; the control method is characterized by further comprising the following steps:
and determining the working rotation speed of a compressor of the vapor compression refrigeration system according to the set cryogenic temperature, the set common cooling temperature and the ambient temperature around the refrigeration and freezing device.
Optionally, under the condition that the set cryogenic temperature, the set common cooling temperature and the ambient temperature are the same, the working rotation speed of the compressor when the Stirling refrigerating system supplies cold for the cryogenic compartment and the vapor compression refrigerating system supplies cold for the common cooling compartment is less than or equal to the working rotation speed of the compressor when the vapor compression refrigerating system supplies cold for the cryogenic compartment.
Optionally, when the set normal cooling temperature and the ambient temperature are the same, and the vapor compression refrigeration system supplies cold for the cryogenic compartment, the working rotation speed of the compressor when the set cryogenic temperature is greater than or equal to the preset cryogenic temperature is greater than or equal to the working rotation speed when the set cryogenic temperature is less than the preset cryogenic temperature.
Optionally, a refrigerating fan is arranged in the cryogenic room, which is characterized in that,
and when the vapor compression refrigeration system supplies cold for the cryogenic compartment, the duty ratio of the refrigeration fan is determined according to the set cryogenic temperature, and the duty ratio is smaller than 100%.
Optionally, the control method further includes:
and determining the working power of the Stirling refrigerator of the Stirling refrigerating system according to the difference between the chamber temperature and the set cryogenic temperature and the ambient temperature around the refrigerating and freezing device.
Optionally, a refrigerating fan is arranged in the cryogenic room, which is characterized in that,
when the Stirling refrigerating system is used for cooling the cryogenic compartment, the duty ratio of the refrigerating fan is 100%.
Optionally, the control method further includes:
judging whether the room temperature is smaller than a set cryogenic temperature or not;
if yes, controlling the vapor compression refrigeration system and the Stirling refrigeration system to stop cooling the cryogenic compartment;
and if not, controlling the vapor compression refrigeration system or the Stirling refrigeration system to continuously cool the cryogenic compartment.
Optionally, the refrigerating and freezing device further comprises a detecting device for detecting the temperature of the compartment, and is characterized in that,
when judging whether the room temperature is larger than or equal to a set cryogenic temperature, the room temperature is the difference value of the detected temperature detected by the detection device minus a preset temperature fluctuation value; and/or
When judging whether the compartment temperature is smaller than the set cryogenic temperature, the compartment temperature is the sum of the detected temperature detected by the detection device and a preset temperature fluctuation value; and/or
Judging whether the compartment temperature is larger than or equal to a preset switching temperature under the condition that the vapor compression refrigeration system supplies cold for the cryogenic compartment, wherein the compartment temperature is the difference value of the detected temperature detected by the detection device minus a preset temperature fluctuation value; and/or
And under the condition that the Stirling refrigerating system supplies cold for the cryogenic compartment, judging whether the compartment temperature is larger than or equal to a preset switching temperature, wherein the compartment temperature is the sum of the detection temperature detected by the detection device and a preset temperature fluctuation value.
According to a second aspect of the present application, there is provided a refrigeration and freezing apparatus comprising:
a box defining a cryogenic compartment;
a vapor compression refrigeration system and a Stirling refrigeration system for cooling the cryogenic compartment; and
a controller configured to perform any of the control methods described above.
The application makes the vapor compression refrigeration system supply cold to the cryogenic compartment when the compartment temperature is more than or equal to the preset switching temperature in the normal mode, and switches to the Stirling refrigeration system to supply cold to the cryogenic compartment when the compartment temperature is less than the preset switching temperature, thereby not only improving the refrigeration efficiency of the refrigeration and freezing device to the cryogenic compartment as a whole, but also reducing the energy consumption of the refrigeration and freezing device and prolonging the service life of the Stirling refrigerator.
Further, the working speed of the compressor of the vapor compression refrigeration system is determined according to the set cryogenic temperature, the set normal cooling temperature and the ambient temperature around the refrigeration and freezing device, and the working power of the Stirling refrigerator of the Stirling refrigeration system is determined according to the difference between the room temperature of the cryogenic room and the set cryogenic temperature and the ambient temperature around the refrigeration and freezing device, so that the efficiency of refrigerating the normal cooling room is not reduced, the high-efficiency refrigeration of the cryogenic room is realized, the power of the refrigeration and freezing device is reasonably distributed, the unexpected energy waste is avoided, and the user experience is improved.
Furthermore, the temperature value detected by the detection device is corrected by setting the temperature fluctuation value, so that frequent switching between the vapor compression refrigeration system and the Stirling refrigeration system is avoided, frequent switching on and off of a part of the vapor compression refrigeration system for cooling the cryogenic compartment or frequent switching on and off of the Stirling refrigeration system are avoided, and the service lives of the vapor compression refrigeration system and the Stirling refrigeration system are further prolonged.
The above, as well as additional objectives, advantages, and features of the present application will become apparent to those skilled in the art from the following detailed description of a specific embodiment of the present application when read in conjunction with the accompanying drawings.
Drawings
Some specific embodiments of the application will be described in detail hereinafter by way of example and not by way of limitation with reference to the accompanying drawings. The same reference numbers will be used throughout the drawings to refer to the same or like parts or portions. It will be appreciated by those skilled in the art that the drawings are not necessarily drawn to scale. In the accompanying drawings:
FIG. 1 is a schematic cross-sectional view of a refrigerated freezer according to one embodiment of the application;
FIG. 2 is a schematic partial rear view of the refrigeration and freezer of FIG. 1;
FIG. 3 is a schematic rear view of the refrigeration and freezer of FIG. 2 with the device chamber cover plate removed;
FIG. 4 is a schematic rear view of the refrigeration and freezer of FIG. 3 with one of the half shells, one of the resilient feet, and the insulating cover removed;
FIG. 5 is a schematic partial enlarged view of region A of FIG. 4;
FIG. 6 is a schematic side view of the heat exchanger of FIG. 1;
FIG. 7 is a schematic block diagram of a controller of one embodiment of the present application;
FIG. 8 is a flow chart of a control method for a refrigeration and chiller according to one embodiment of the present application;
fig. 9 is a detailed flowchart of a control method for a refrigerating and freezing apparatus according to the present application.
Detailed Description
Fig. 1 is a schematic cross-sectional view of a refrigerated chiller 100 according to one embodiment of the present application; fig. 2 is a schematic partial rear view of the refrigeration and freezer 100 of fig. 1; fig. 3 is a schematic rear view of the refrigeration and freezer 100 of fig. 2 with the cover 118 of the device chamber 117 removed. Referring to fig. 1 through 3, a refrigeration and freezing apparatus 100 may include a cabinet defining at least one storage compartment, at least one door for opening and closing the at least one storage compartment, a stirling refrigeration system for refrigerating the at least one storage compartment and a vapor compression refrigeration system for refrigerating the at least one storage compartment, respectively, and a controller 190 for controlling operation of the vapor compression refrigeration system and the stirling refrigeration system. The refrigerating and freezing apparatus 100 may be a refrigerator, a freezer, or the like.
The case may include an outer case 111, at least one inner container disposed in the outer case 111, and a heat insulation layer 112 disposed between the outer case 111 and the at least one inner container. Wherein, at least one inner container is limited with at least one storing compartment respectively.
In the illustrated embodiment, the cabinet includes a supercooled liner 113, a supercooled liner 114, a supercooled liner 115, and a supercooled liner 116. The vapor compression refrigeration system may be configured to provide cooling to the refrigerated compartment defined by the super-cooled liner 113, the super-cooled compartment defined by the super-cooled liner 114 and the super-cooled liner 115, and the super-cooled compartment defined by the super-cooled liner 116, and the stirling refrigeration system may be configured to provide cooling only to the super-cooled compartment defined by the super-cooled liner 116.
Illustratively, the storage temperature of the refrigerated compartment may be from 0 to +8 ℃; the preservation temperature of the common cooling chamber can be-14 to-24 ℃; the preservation temperature of the cryogenic compartment can cover the preservation temperature of the common cooling compartment and can be between-14 and 80 ℃.
Specifically, the vapor compression refrigeration system may include a compressor 131, a condenser tube, at least one throttling element, and a plurality of evaporator tubes 133. The plurality of evaporating pipes 133 may be disposed in the common cooling liner 113, the common cooling liner 114, and the cryogenic liner 116, respectively. The common cooling liner 115 may be in communication with the common cooling liner 114 via an air duct.
The Stirling refrigeration system may include at least one Stirling refrigerator 120, at least one cold guide 150 thermally coupled to a cold side of the at least one Stirling refrigerator 120, respectively, and at least one heat sink 160 thermally coupled to a hot side of the at least one Stirling refrigerator 120, respectively. In the illustrated embodiment, the number of Stirling coolers 120 is one.
Specifically, each Stirling cooler 120 may include a housing, a cylinder, a piston, and a drive mechanism to drive the movement of the piston. Wherein the housing may be composed of a body 121 and a cylindrical portion 122. The drive mechanism may be disposed within the body 121. The piston may be configured to reciprocate within barrel 122 to form a cold end and a hot end.
The rear bottom of the outer box 111 may also define a device chamber 117. In particular, the Stirling refrigerator 120 may be disposed within the device chamber 117 to facilitate installation and maintenance of the Stirling refrigerator 120 and to improve stability of the Stirling refrigerator 120, and to prevent resonance problems caused by vibrations generated by the Stirling refrigerator 120 being transmitted to the case to some extent.
In some embodiments, the refrigerator-freezer 100 can further include a bottom steel fixedly attached to the outer box 111. A bottom steel may be provided at the bottom of the device chamber 117 for supporting the stirling cooler 120.
In some embodiments, the cold end of Stirling cooler 120 may be disposed above the hot end thereof to facilitate transfer of cold generated at the cold end to the cryogenic compartment.
In some embodiments, the compressor 131 and the condenser 132 may also be disposed in the device chamber 117, so that the structure is compact, the box has a larger storage space, and installation, maintenance and circuit layout of the compressor 131, the condenser 132 and the Stirling refrigerator 120 are facilitated, and production cost is reduced.
In some embodiments, the refrigeration and freezer 100 can also include a thermal cover 175. The heat preservation cover 175 may be configured to separate the cold end and the hot end of the stirling cooler 120 from the inside and the outside thereof, so as to avoid the heat interference of the hot end and the cold end, and make most or all of the cold energy generated by the cold end be transmitted to the cryogenic compartment, thereby improving the refrigeration efficiency of the stirling cooler 120.
In some embodiments, the refrigerating and freezing apparatus 100 may further include a cover 170 covering the outside of the main body 121 of the stirling cooler 120 to prevent the heat generated by the compressor 131 from affecting the working efficiency of the stirling cooler 120 and to shield the vibration noise generated by the stirling cooler 120, thereby reducing the noise transferred to the surrounding environment and improving the user experience.
FIG. 4 is a schematic rear view of the refrigeration and freezer 100 of FIG. 3 with one half shell, one resilient pad, and the thermal cover 175 removed; fig. 5 is a schematic partial enlarged view of the area a in fig. 4. Referring to fig. 4 and 5, the enclosure 170 may be comprised of two half-shells that are mirror symmetrical about a longitudinal central plane of symmetry of the stirling cooler 120. I.e., the two halves of the housing 170 may be mirror symmetric about a plane coplanar with the direction of piston motion of the Stirling cooler 120 to facilitate assembly of the Stirling cooler 120 with the housing 170 and extraction of the cold and hot ends of the Stirling cooler 120.
The cold guide 150 may include a cold end adapter thermally coupled to the cold end of the Stirling refrigerator 120 and a plurality of cold guide tubes thermally coupled to the cold end adapter.
The cold end adapter may be provided with a plurality of tube holes. One end of each heat pipe can be arranged in each pipe hole and is thermally connected with the cold end adapter so as to receive cold energy of the cold end and guide out the cold energy.
Fig. 6 is a schematic side view of the heat exchanger 140 of fig. 1. Referring to fig. 6, the heat exchanger 140 may include a cold guide plate 142 and a refrigerating end adapter 141 thermally connected to the cold guide plate 142.
The cold guide plate 142 may be provided with a plurality of refrigerant holes, and the evaporation tube 133 may extend in a serpentine shape and pass through the plurality of refrigerant holes, so as to increase the contact area between the evaporation tube 133 and the cold guide plate 142.
The cold side adapter 141 may be provided with a plurality of heat pipe holes. The other ends of the plurality of heat pipes may be disposed in the plurality of heat pipe holes and thermally connected to the cooling end adapter 141, respectively, to transfer the received cooling power to the cooling plate 142.
In some embodiments, the refrigeration and freezer 100 can also include at least one electric heating tube 180. Each of the electric heating pipes 180 may be provided to be partially embedded in the cold guide plate 142 to defrost the heat exchanger 140.
In some embodiments, the refrigeration and chiller 100 may further include a cooling fan 134 disposed in the sub-ambient air space to provide more efficient heat exchange between the hot air and the cold air in the sub-ambient air space.
Fig. 7 is a schematic block diagram of a controller 190 according to an embodiment of the present application. Referring to fig. 7, the controller 190 may include a processing unit 191 and a storage unit 192. The storage unit 192 stores therein a computer program 193 for implementing the control method of the embodiment of the present application when the computer program 193 is executed by the processing unit 191.
In particular, the refrigeration and freezer 100 is provided with a normal mode. In the normal mode, the controller 190 may be configured to control the vapor compression refrigeration system to cool the cryogenic compartment and to control the stirling refrigeration system to stop cooling the cryogenic compartment when the compartment temperature of the cryogenic compartment is greater than or equal to the preset switching temperature and greater than or equal to the set cryogenic temperature; when the temperature of the cryogenic chamber is smaller than the preset switching temperature and larger than or equal to the set cryogenic temperature, the Stirling refrigerating system is controlled to cool the cryogenic chamber, and the vapor compression refrigerating system is controlled to stop cooling the cryogenic chamber.
In the present application, the set cryogenic temperature is a user input or a default set storage temperature for the cryogenic compartment. The preset switching temperature may be greater than the minimum refrigeration temperature of the vapor compression refrigeration system, e.g., the minimum refrigeration temperature of the vapor compression refrigeration system is 40 ℃, and the switching temperature may be-25 ℃.
The refrigeration and freezing device 100 of the application can cool the vapor compression refrigeration system to the cryogenic compartment when the compartment temperature is larger than or equal to the preset switching temperature in the normal mode, and can cool the Stirling refrigeration system to the cryogenic compartment when the compartment temperature is smaller than the preset switching temperature, thereby not only improving the refrigeration efficiency of the refrigeration and freezing device 100 to the cryogenic compartment as a whole, but also reducing the energy consumption of the refrigeration and freezing device 100 and prolonging the service life of the Stirling refrigerator 120.
In some embodiments, the controller 190 may be configured to determine the operating power of the Stirling cooler 120 based on the difference between the compartment temperature of the cryogenic compartment and the set cryogenic temperature and the ambient temperature surrounding the refrigerated freezer 100. That is, during the cooling process, the operating power of the Stirling refrigerator 120 is re-determined in real time according to the change of the temperature difference, so that energy is saved while the cooling efficiency is ensured.
In the case of the same ambient temperature, the operating power of Stirling refrigerator 120 may be approximately directly related to the difference between the compartment temperature of the cryogenic compartment and the set cryogenic temperature, i.e., the difference between the compartment temperature of the cryogenic compartment minus the set cryogenic temperature.
In the case where the difference between the compartment temperature of the cryogenic compartment and the set cryogenic temperature is the same, the operating power of the Stirling refrigerator 120 may be approximately positively correlated with the ambient temperature.
Table 1 shows the difference between the room temperature minus the set cryogenic temperature of the various cryogenic rooms, and the operating power of the stirling cooler 120 corresponding to the ambient temperature around the various refrigeration chiller 100, in watts (W), temperature difference and ambient temperature in degrees celsius (°c), in accordance with an exemplary embodiment of the present application.
TABLE 1
The controller 190 may regulate the operating power of the Stirling cooler 120 by regulating the input voltage to the Stirling cooler 120.
In some embodiments, the controller 190 may be further configured to determine the operating speed of the compressor 131 based on the set cryogenic temperature, the set chilling temperature, and the ambient temperature surrounding the refrigeration chiller 100 to make the power distribution of the refrigeration chiller 100 more rational, while achieving efficient cooling of the cryogenic compartment without reducing the efficiency of cooling the cryogenic compartment.
In the application, the set cooling temperature is set preservation temperature of the cooling chamber by user input or default of the system.
The operating speed of the compressor 131 may be approximately inversely related to the set sub-ambient temperature, with both the set sub-ambient temperature and the set sub-ambient temperature being the same.
In the case where the set sub-ambient temperature and the set sub-ambient temperature are the same, the operating speed of the compressor 131 may be approximately positively correlated with the ambient temperature.
In some further embodiments, when the set supercooling temperature and the ambient temperature are the same and the vapor compression refrigeration system supplies cold to the supercooling compartment, the operating speed of the compressor may be greater than or equal to the operating speed when the set supercooling temperature is greater than or equal to the preset supercooling temperature and less than the preset supercooling temperature, so as to increase the efficiency of supplying cold to the supercooling compartment.
For example, the preset switching temperature is-25℃and the preset cryogenic temperature is-21 ℃. The working speed of the compressor can be more than or equal to the working speed of the compressor at the set temperature of more than or equal to minus 25 ℃ and less than minus 21 ℃ under the condition that other conditions are the same.
Specifically, table 2 shows the operating speeds of the compressors 131 corresponding to different set supercooling temperatures and different ambient temperatures around the refrigerating and freezing apparatus 100 when the compressor 131 cools the supercooling compartment and the set supercooling temperature is equal to or higher than the preset supercooling temperature in the normal mode according to an exemplary embodiment of the present application, wherein the operating speed of the compressors 131 is expressed in revolutions per minute (rpm), and the set supercooling temperature and the ambient temperature are expressed in degrees celsius (°c).
TABLE 2
Table 3 shows the operating speeds of the compressors 131 corresponding to different set supercooling temperatures and different ambient temperatures around the refrigerating and freezing apparatus 100 when the compressor 131 cools the supercooling compartment and the set supercooling temperature is less than the preset supercooling temperature in the normal mode according to an exemplary embodiment of the present application, wherein the operating speed of the compressor 131 is expressed in revolutions per minute (rpm), and the set supercooling temperature and the ambient temperature are expressed in degrees celsius (°c).
TABLE 3 Table 3
In some further embodiments, where the set sub-ambient temperature, and the ambient temperature are all the same, the operating speed of the compressor 131 when the Stirling refrigeration system is cooling the sub-ambient and the vapor compression refrigeration system is cooling the sub-ambient may be less than or equal to the operating speed of the compressor 131 when the vapor compression refrigeration system is cooling the sub-ambient. That is, the operating speed of the compressor 131 when cooling only the sub-cooling compartment or simultaneously cooling at least one of the sub-cooling compartment and the other compartments (the refrigerating compartment and the general cooling compartment) is equal to or greater than the operating speed when stopping cooling the sub-cooling compartment and cooling at least one of the other compartments, so that the distribution of power is more reasonable.
Table 4 shows the operating speeds of the compressors 131 corresponding to different cooling temperatures and different ambient temperatures around the refrigeration and freezer 100 when the compressors 131 are only used for cooling at least one other storage compartment in the normal mode according to an exemplary embodiment of the present application, wherein the operating speeds of the compressors 131 are expressed in revolutions per minute (rpm) and the cooling temperatures and the ambient temperatures are set in degrees celsius (°c).
TABLE 4 Table 4
In some embodiments, in the normal mode, the controller 190 may be configured to determine the duty cycle (ratio of the operating speed to the rated speed) of the refrigeration fan 134 based on the set cryogenic temperature when the vapor compression refrigeration system is providing cooling to the cryogenic compartment, in which case the duty cycle may be less than 100% to allow the hot air in the cryogenic compartment to exchange heat with the cold air more fully, to increase refrigeration efficiency, to avoid undesirable energy waste, and to extend the service life of the refrigeration fan. Wherein the duty cycle of the refrigeration fan 134 may be inversely proportional to the set cryogenic temperature.
Specifically, table 5 shows the duty ratios of the cooling fans 134 corresponding to different set cryogenic temperatures when the compressor 131 supplies cold to the cryogenic compartment in the normal mode according to an exemplary embodiment of the present application, wherein the set cryogenic temperatures are set in degrees celsius (°c).
TABLE 5
In some further embodiments, in the normal mode, the controller 190 may be configured to control the refrigeration fan 134 to operate at 100% duty cycle when the Stirling refrigeration system is providing cold to the cryogenic compartment to further increase the refrigeration efficiency and avoid over-concentration of cold thereby reducing the useful life of the refrigeration fan 134.
In some embodiments, the refrigerator-freezer 100 may also be provided with a quick-freeze mode. The quick freezing mode may be operated when a quick freezing mode start instruction input by a user is received, or operated when the refrigerating and freezing apparatus 100 is first powered on (i.e., the temperature of the compartment from the first time the refrigerating and freezing apparatus 100 is powered on to the temperature of the cryogenic compartment is less than a set cryogenic temperature) even when the previous two times of power on, or operated immediately after defrosting of the cryogenic compartment is completed, so as to improve the preservation quality of foods in the cryogenic compartment.
In the quick-freeze mode, the controller 190 may be configured to control the vapor compression refrigeration system and the stirling refrigeration system to cool the cryogenic compartment when the compartment temperature of the cryogenic compartment is greater than or equal to a preset switching temperature and greater than or equal to a set cryogenic temperature; when the temperature of the cryogenic chamber is smaller than the preset switching temperature and is larger than or equal to the set cryogenic temperature, the Stirling refrigerating system is controlled to cool the cryogenic chamber, and the vapor compression refrigerating system is controlled to stop cooling the cryogenic chamber, so that the cooling efficiency of the cryogenic chamber is further improved.
In some further embodiments, when the set normal cooling temperature and the ambient temperature are the same, the working speed of the compressor 131 for cooling the cryogenic compartment in the quick freezing mode may be equal to or higher than the working speed for cooling the cryogenic compartment in the normal mode, so as to further improve the refrigeration efficiency while saving energy.
Table 6 shows the operating speeds of the compressors 131 corresponding to different set cooling temperatures and different ambient temperatures around the refrigerating and freezing apparatus 100 when the compressors 131 are used for cooling the deep-freezing compartment in the quick-freezing mode according to an exemplary embodiment of the present application, wherein the operating speeds of the compressors 131 are expressed in revolutions per minute (rpm), and the set cooling temperatures and the ambient temperatures are expressed in degrees celsius (deg.c).
TABLE 6
In some embodiments, in the quick-freeze mode, the controller 190 may be configured to control the refrigeration blower 134 to operate at a 100% duty cycle to further increase refrigeration efficiency, avoiding too concentrated cooling to reduce the useful life of the refrigeration blower 134.
In some embodiments, in the normal mode and the quick-freeze mode, the controller 190 may be configured to control the vapor compression refrigeration system and the Stirling refrigeration system to cease cooling the cryogenic compartment when the compartment temperature is less than the set cryogenic temperature.
In some embodiments, the refrigeration and freezer 100 can further include a detection device for detecting the compartment temperature of the cryogenic compartment.
In the normal mode and the quick-freezing mode, the controller 190 may be configured to determine whether the compartment temperature is equal to or higher than a set cryogenic temperature, as the compartment temperature of the cryogenic compartment, a difference of the detected temperature detected by the detecting means minus a preset temperature fluctuation value; when judging whether the room temperature is smaller than the set cryogenic temperature, taking the sum of the detected temperature detected by the detection device and the preset temperature fluctuation value as the room temperature of the cryogenic room, so as to avoid frequent on-off of the part of the vapor compression refrigeration system for cooling the cryogenic room or frequent on-off of the Stirling refrigeration system.
In the present application, the temperature fluctuation value may be any value of 1 to 3 ℃, for example, 1 ℃, 2 ℃, or 3 ℃.
In the normal mode and the quick-freezing mode, the controller 190 may be further configured to determine whether the compartment temperature is equal to or higher than a preset switching temperature in the case where the vapor compression refrigeration system supplies cold to the cryogenic compartment, and to use a difference obtained by subtracting a preset temperature fluctuation value from the detected temperature detected by the detection device as the compartment temperature of the cryogenic compartment; when the Stirling refrigerating system supplies cold for the cryogenic compartment, judging whether the compartment temperature is smaller than the preset switching temperature or not, taking the sum of the detected temperature detected by the detecting device and the preset temperature fluctuation value as the compartment temperature of the cryogenic compartment so as to avoid frequent switching between the vapor compression refrigerating system and the Stirling refrigerating system.
Fig. 8 is a flowchart of a control method for the refrigerating and freezing apparatus 100 according to an embodiment of the present application. Referring to fig. 8 (in the present application, "Y" in the drawings indicates "yes" and "N" indicates "no"), the control method for the refrigerating and freezing apparatus 100, which is performed by the controller 190 of any of the above-described embodiments, of the present application may include the steps of:
step S802: when the room temperature of the cryogenic room is greater than or equal to the set cryogenic temperature, judging whether the room temperature of the cryogenic room is greater than or equal to the preset switching temperature. If yes, go to step S804; if not, go to step S806.
Step S804: the vapor compression refrigeration system is controlled to cool the cryogenic compartment, and the Stirling refrigeration system stops cooling the cryogenic compartment.
Step S806: the Stirling refrigerating system is controlled to cool the cryogenic compartment, and the vapor compression refrigerating system stops cooling the cryogenic compartment.
The control method of the application enables the vapor compression refrigeration system to supply cold to the cryogenic compartment when the compartment temperature is more than or equal to the preset switching temperature in the normal mode, and then switches to the Stirling refrigeration system to supply cold to the cryogenic compartment when the compartment temperature is less than the preset switching temperature, thereby not only improving the refrigeration efficiency of the refrigeration and freezing device 100 to the cryogenic compartment as a whole, but also reducing the energy consumption of the refrigeration and freezing device 100 and prolonging the service life of the Stirling refrigerator 120.
In some embodiments, the operating speed of the compressor 131 may be determined according to the set cryogenic temperature, the set common cooling temperature, and the ambient temperature surrounding the refrigeration chiller 100 to make the power distribution of the refrigeration chiller 100 more reasonable, and to achieve efficient cooling of the cryogenic compartment without reducing the efficiency of cooling the common compartment.
The operating speed of the compressor 131 may be approximately inversely related to the set sub-ambient temperature, with both the set sub-ambient temperature and the set sub-ambient temperature being the same.
In the case where the set sub-ambient temperature and the set sub-ambient temperature are the same, the operating speed of the compressor 131 may be approximately positively correlated with the ambient temperature.
In some further embodiments, when the set supercooling temperature and the ambient temperature are the same and the vapor compression refrigeration system supplies cold to the supercooling compartment, the operating speed of the compressor may be greater than or equal to the operating speed when the set supercooling temperature is greater than or equal to the preset supercooling temperature and less than the preset supercooling temperature, so as to increase the efficiency of supplying cold to the supercooling compartment.
In some further embodiments, where the set sub-ambient temperature, and the ambient temperature are all the same, the operating speed of the compressor 131 when the Stirling refrigeration system is cooling the sub-ambient and the vapor compression refrigeration system is cooling the sub-ambient may be less than or equal to the operating speed of the compressor 131 when the vapor compression refrigeration system is cooling the sub-ambient to make the distribution of power more reasonable.
In some embodiments, the operating power of the Stirling cooler 120 may be determined based on the difference between the compartment temperature of the cryogenic compartment and the set cryogenic temperature and the ambient temperature surrounding the refrigeration chiller 100 to conserve energy while maintaining refrigeration efficiency.
In some embodiments, in the normal mode, when the vapor compression refrigeration system is cooling the cryogenic compartment, the duty cycle of the refrigeration fan 134 may be determined according to the set cryogenic temperature, in which case the duty cycle may be less than 100% to allow the hot air in the cryogenic compartment to exchange heat with the cold air more fully, improve refrigeration efficiency, avoid undesirable energy waste, and extend the service life of the refrigeration fan.
In some embodiments, in the normal mode, when the Stirling refrigeration system is cooling the cryogenic compartment, the duty cycle of the refrigeration fan 134 may be 100% to further increase the refrigeration efficiency, avoiding too concentrated cooling to reduce the service life of the refrigeration fan 134.
Fig. 9 is a detailed flowchart of a control method for the refrigerating and freezing apparatus 100 according to the present application. Referring to fig. 9, the control method for the refrigerating and freezing apparatus 100 of the present application may specifically include the steps of:
step S902: whether a quick-freezing mode starting instruction is received or whether the refrigerating and freezing device 100 is electrified for the first time or whether defrosting of the deep-cooling compartment is finished is judged. If yes, executing step S904, and starting to run a quick-freezing mode; if not, it is determined that the normal mode start command is received, step S912 is executed, and the normal mode starts to be operated.
Step S904: and judging whether the room temperature of the cryogenic room is greater than or equal to the set cryogenic temperature. If yes, go to step S906; if not, go to step S920. In some embodiments, in each quick-freezing mode operation period, when step S904 is performed for the first time, in order to determine whether the cryogenic compartment needs to be refrigerated, the temperature of the cryogenic compartment may be the difference obtained by subtracting the preset temperature fluctuation value from the detected temperature detected by the detecting device; and when the step S904 is operated again, in order to judge whether the chamber temperature of the cryogenic chamber is smaller than the set cryogenic temperature, namely, judge whether the refrigeration of the cryogenic chamber is finished, at this moment, the temperature of the cryogenic chamber can be the sum of the detected temperature detected by the detection device and a preset temperature fluctuation value, so as to avoid frequent on-off of a part of the vapor compression refrigeration system for supplying cold to the cryogenic chamber or frequent on-off of the Stirling refrigeration system.
Step S906: judging whether the room temperature of the cryogenic room is more than or equal to a preset switching temperature. If yes, go to step S908; if not, go to step S910. In some embodiments, during each quick-freeze mode operation cycle, the first time step S906 is operated, the temperature of the cryogenic compartment may be the detected temperature detected by the detection device at that time.
Step S908: the vapor compression refrigeration system and the Stirling refrigeration system are controlled to provide cooling for the cryogenic compartment. And returns to step S902. In some embodiments, when step S906 is performed after step S908, the sub-zero compartment temperature may be the difference between the detected temperature detected by the detection device minus a preset temperature fluctuation value to avoid frequent switching between the vapor compression refrigeration system and the stirling refrigeration system.
Step S910: the Stirling refrigerating system is controlled to cool the cryogenic compartment, and the vapor compression refrigerating system stops cooling the cryogenic compartment. And returns to step S902. In some embodiments, when step S906 is performed after step S910, the sub-zero compartment temperature may be the sum of the detected temperature detected by the detection device and a preset temperature fluctuation value to avoid frequent switching between the vapor compression refrigeration system and the stirling refrigeration system.
Step S912: and judging whether the room temperature of the cryogenic room is greater than or equal to the set cryogenic temperature. If yes, go to step S914; if not, go to step S920. In some embodiments, in each normal mode operation period, when step S912 is performed for the first time, in order to determine whether the cryogenic compartment needs to be refrigerated, the temperature of the cryogenic compartment may be the difference obtained by subtracting the preset temperature fluctuation value from the detected temperature detected by the detecting device; when the step S912 is performed again, in order to determine whether the chamber temperature of the cryogenic chamber is less than the set cryogenic temperature, that is, whether the refrigeration of the cryogenic chamber is completed, the temperature of the cryogenic chamber may be the sum of the detected temperature detected by the detecting device and the preset temperature fluctuation value, so as to avoid frequent on-off of the portion of the vapor compression refrigeration system supplying the cold to the cryogenic chamber or frequent on-off of the stirling refrigeration system.
Step S914: judging whether the room temperature of the cryogenic room is more than or equal to a preset switching temperature. If yes, go to step S916; if not, go to step S918. In some embodiments, during each normal mode operation period, the first time step S914 is performed, the temperature of the cryogenic compartment may be the detected temperature detected by the detection means at that time.
Step S916: the vapor compression refrigeration system is controlled to cool the cryogenic compartment, and the Stirling refrigeration system stops cooling the cryogenic compartment. And returns to step S902. In some embodiments, when step S914 is performed after step S916, the sub-zero chamber temperature may be the difference between the detected temperature detected by the detection device minus a preset temperature fluctuation value to avoid frequent switching between the vapor compression refrigeration system and the stirling refrigeration system.
Step S918: the Stirling refrigerating system is controlled to cool the cryogenic compartment, and the vapor compression refrigerating system stops cooling the cryogenic compartment. And returns to step S902.
Step S920: the vapor compression refrigeration system and the Stirling refrigeration system are controlled to stop cooling the cryogenic compartment. And returns to step S902.
Further, the controller 190 may be configured to step up the input voltage to the Stirling refrigerator 120 each time the Stirling refrigerator 120 is started at full power to avoid cylinder collision of the Stirling refrigerator 120. For example, the Stirling refrigerator 120 is turned on and then increased from 0 volts (V) to a rated voltage in preset steps every preset time interval.
By now it should be appreciated by those skilled in the art that while a number of exemplary embodiments of the application have been shown and described herein in detail, many other variations or modifications of the application consistent with the principles of the application may be directly ascertained or inferred from the present disclosure without departing from the spirit and scope of the application. Accordingly, the scope of the present application should be understood and deemed to cover all such other variations or modifications.
Claims (10)
1. A control method for a refrigeration chiller including a cabinet defining a cryogenic compartment and a common cooling compartment, a stirling refrigeration system for cooling the cryogenic compartment, and a vapor compression refrigeration system for cooling the cryogenic compartment and/or the common cooling compartment, the control method comprising:
when the room temperature of the cryogenic room is more than or equal to a set cryogenic temperature, controlling the Stirling refrigerating system or the vapor compression refrigerating system to cool the cryogenic room; and
determining the working rotation speed of a compressor of the vapor compression refrigeration system according to the set cryogenic temperature, the set common cooling temperature and the ambient temperature around the refrigeration and freezing device; wherein, the liquid crystal display device comprises a liquid crystal display device,
and under the condition that the set normal cooling temperature and the environment temperature are the same, and the vapor compression refrigeration system supplies cold for the cryogenic compartment, the working rotating speed of the compressor when the set cryogenic temperature is more than or equal to the preset cryogenic temperature is more than or equal to the working rotating speed when the set cryogenic temperature is less than the preset cryogenic temperature.
2. The control method according to claim 1, wherein,
and under the condition that the set cryogenic temperature, the set common cooling temperature and the environment temperature are the same, the working rotation speed of the compressor when the Stirling refrigerating system supplies cold for the cryogenic compartment and the vapor compression refrigerating system supplies cold for the common cooling compartment is less than or equal to the working rotation speed of the compressor when the vapor compression refrigerating system supplies cold for the cryogenic compartment.
3. The control method according to claim 1, wherein a refrigerating fan is provided in the sub-zero compartment,
and when the vapor compression refrigeration system supplies cold for the cryogenic compartment, the duty ratio of the refrigeration fan is determined according to the set cryogenic temperature, and the duty ratio is smaller than 100%.
4. The control method according to claim 1, characterized by further comprising:
and determining the working power of the Stirling refrigerator of the Stirling refrigerating system according to the difference between the chamber temperature and the set cryogenic temperature and the ambient temperature around the refrigerating and freezing device.
5. The control method according to claim 1, wherein a refrigerating fan is provided in the sub-zero compartment,
when the Stirling refrigerating system is used for cooling the cryogenic compartment, the duty ratio of the refrigerating fan is 100%.
6. The control method according to claim 1, characterized by further comprising:
judging whether the room temperature is smaller than a set cryogenic temperature or not;
if yes, controlling the vapor compression refrigeration system and the Stirling refrigeration system to stop cooling the cryogenic compartment;
and if not, controlling the vapor compression refrigeration system or the Stirling refrigeration system to continuously cool the cryogenic compartment.
7. The control method according to claim 6, wherein the refrigerating and freezing apparatus further comprises a detecting means for detecting the temperature of the compartment,
when judging whether the room temperature is larger than or equal to a set cryogenic temperature, the room temperature is the difference value of the detected temperature detected by the detection device minus a preset temperature fluctuation value; and/or
And when judging whether the room temperature is smaller than the set cryogenic temperature, the room temperature is the sum of the detected temperature detected by the detection device and a preset temperature fluctuation value.
8. The control method of claim 1, wherein the step of cooling the cryogenic compartment comprises:
judging whether the room temperature is larger than or equal to a preset switching temperature;
if yes, controlling the vapor compression refrigeration system to cool the cryogenic compartment, and stopping cooling the cryogenic compartment by the Stirling refrigeration system;
and if not, controlling the Stirling refrigerating system to cool the cryogenic compartment, and stopping cooling the cryogenic compartment by the vapor compression refrigerating system.
9. The control method according to claim 8, wherein the refrigerating and freezing apparatus further comprises a detecting means for detecting the temperature of the compartment,
judging whether the compartment temperature is larger than or equal to a preset switching temperature under the condition that the vapor compression refrigeration system supplies cold for the cryogenic compartment, wherein the compartment temperature is the difference value of the detected temperature detected by the detection device minus a preset temperature fluctuation value; and/or
And under the condition that the Stirling refrigerating system supplies cold for the cryogenic compartment, judging whether the compartment temperature is larger than or equal to a preset switching temperature, wherein the compartment temperature is the sum of the detection temperature detected by the detection device and a preset temperature fluctuation value.
10. A refrigerated chiller comprising:
a box defining a cryogenic compartment;
a vapor compression refrigeration system and a Stirling refrigeration system for cooling the cryogenic compartment; and
a controller configured to perform the control method of any one of claims 1-9.
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| CN201911382785.2A CN111059842B (en) | 2019-12-27 | 2019-12-27 | Control method for refrigerating and freezing device and refrigerating and freezing device |
| CN202310793433.6A CN116951867A (en) | 2019-12-27 | 2019-12-27 | Control method for refrigerating and freezing device and refrigerating and freezing device |
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| US5715693A (en) * | 1996-07-19 | 1998-02-10 | Sunpower, Inc. | Refrigeration circuit having series evaporators and modulatable compressor |
| JP4169560B2 (en) * | 2002-09-30 | 2008-10-22 | 三洋電機株式会社 | Stirling cold supply system and operation method thereof |
| US8245524B2 (en) * | 2006-12-28 | 2012-08-21 | Whirlpool Corporation | Thermal cascade system for distributed household refrigeration system |
| CN106052258A (en) * | 2016-07-21 | 2016-10-26 | 上海理工大学 | Refrigerator having multiple temperature zones |
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