CN211625831U - Refrigerating and freezing device - Google Patents

Abstract

The utility model provides a cold-stored refrigeration device. The refrigerating and freezing device comprises a box body, a vapor compression refrigerating system and a Stirling refrigerating system. The box body is limited with a plurality of storage compartments, wherein one storage compartment is a deep cooling compartment. At least a portion of the vapor compression refrigeration system is disposed within or passes to the cryogenic compartment to provide cooling to the cryogenic compartment. At least one part of the Stirling refrigerating system is arranged in the deep cooling chamber or reaches the deep cooling chamber to supply cold to the deep cooling chamber. The utility model discloses a cold-stored refrigerating plant is selectively simultaneously for cryrogenic interventricular refrigeration through making vapor compression refrigerating system and stirling refrigerating system, and not only refrigeration efficiency is high, still can realize the broad width alternating temperature of cryrogenic interventricular, satisfies different users' user demand in a flexible way, and the suitability is high.

Description

Refrigerating and freezing device

Technical Field

The utility model relates to a refrigeration field especially relates to an adopt cryogenic cold-stored refrigerating plant of stirling refrigerating system and vapor compression refrigerating system.

Background

With the health emphasis of people, the household stock of high-end food materials is also increasing. According to the research, the storage temperature of the food material is lower than the glass transition temperature, 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 household refrigerator adopts a vapor compression method for refrigeration, and in recent years, refrigerators adopting semiconductor, magnetic refrigeration and other methods are developed, but the temperature in the refrigerator is difficult to reach below minus 30 ℃ due to the limitation of refrigeration efficiency. The Stirling refrigerating system is adopted for refrigeration in the fields of spaceflight, medical treatment and the like, and the refrigerating temperature of the system can be below 200 ℃ below zero.

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to overcome at least one technical defect of prior art, provide an adopt cryogenic cold-stored refrigerating plant of stirling refrigerating system and vapor compression refrigerating system.

The utility model discloses a further purpose is to avoid vapor compression refrigerating system's refrigerant to gather in the evaporating pipe for cryrogenic compartment cooling.

The utility model discloses another further purpose improves for the efficiency of cryrogenic compartment cooling.

Particularly, the utility model provides a cold-stored refrigeration device, its characterized in that includes:

the refrigerator comprises a box body, a door body and a refrigerator, wherein a plurality of storage compartments are defined, and one storage compartment is a deep cooling compartment;

a vapor compression refrigeration system, at least a portion of which is disposed within or passes into said cryogenic compartment to provide cooling thereto; and

stirling refrigerating system, at least some set up in the cryrogenic compartment or reach in the cryrogenic compartment is indoor, in order to the cryrogenic compartment cooling.

Optionally, the vapor compression refrigeration system comprises:

the compressor, the condenser pipe and the throttling element;

a plurality of evaporating pipes, one of said evaporating pipes is disposed in said deep cooling chamber, and the other of said evaporating pipes and the evaporating pipe in said deep cooling chamber are connected in parallel between said condensing pipe and said compressor or at least partially connected in series downstream of the evaporating pipe in said deep cooling chamber; and

and the valve is set to at least switch on and off the refrigerant flow path from the condensation pipe to the evaporation pipe in the deep cooling chamber.

Optionally, the vapor compression refrigeration system further comprises:

and the check valve is connected between the outlet of the evaporation pipe in the deep cooling chamber and the compressor in series and is configured to prohibit the evaporation pipe from receiving the refrigerants in other evaporation pipes.

Alternatively, in the normal cooling mode,

the vapor compression refrigeration system is configured to supply cold to the cryogenic compartment when the compartment temperature of the cryogenic compartment is greater than or equal to a preset switching temperature; and is

The Stirling refrigerating system is located to work as the room temperature of cryrogenic compartment more than or equal to sets for cryrogenic temperature and is less than when predetermineeing the switching temperature do the cryrogenic compartment cooling.

Alternatively, in the quick-freeze mode,

the vapor compression refrigeration system is configured to supply cold to the cryogenic compartment when the compartment temperature of the cryogenic compartment is greater than or equal to a preset switching temperature; and is

The Stirling refrigerating system is arranged to supply cold for the cryogenic chamber when the temperature of the cryogenic chamber is greater than or equal to the set cryogenic temperature.

Alternatively, in the normal cooling mode,

the vapor compression refrigeration system is configured to supply cold to the cryogenic compartment within a preset time when the compartment temperature of the cryogenic compartment is greater than or equal to a set cryogenic temperature; and is

The Stirling refrigerating system is configured to supply cold to the deep cold chamber after the preset time and when the temperature of the deep cold chamber is greater than or equal to the set deep cold temperature.

Alternatively, in the normal cooling mode,

the vapor compression refrigeration system and the Stirling refrigeration system are configured to alternately supply cold to the cryogenic chamber when the temperature of the cryogenic chamber is greater than or equal to a set cryogenic temperature; wherein

In each refrigerating period of the alternate refrigeration, the Stirling refrigerating system firstly supplies cold for the deep cooling chamber.

Alternatively, in the quick-freeze mode,

the vapor compression refrigeration system is configured to supply cold to the cryogenic compartment within a preset time when the compartment temperature of the cryogenic compartment is greater than or equal to a set cryogenic temperature; and is

The Stirling refrigerating system is configured to supply cold to the cryogenic compartment when the compartment temperature of the cryogenic compartment is greater than or equal to a set cryogenic temperature.

Optionally, the refrigeration and freezing apparatus further comprises:

the refrigerating fan is arranged in the deep cooling chamber and used for circulating air in the deep cooling chamber; and is

The refrigeration fan is configured to operate when at least one of the vapor compression refrigeration system and the stirling refrigeration system is providing cooling to the cryogenic compartment.

Optionally, the refrigerating and freezing device is a cross side by side refrigerator, and the deep cooling chamber is a lower storage chamber of the refrigerator body; and is

And the Stirling refrigerating machine of the Stirling refrigerating system is arranged at the rear side of the deep cooling chamber.

The utility model discloses a cold-stored refrigerating plant is selectively simultaneously for cryrogenic interventricular refrigeration through making vapor compression refrigerating system and stirling refrigerating system, and not only refrigeration efficiency is high, still can realize the broad width alternating temperature of cryrogenic interventricular, satisfies different users' user demand in a flexible way, and the suitability is high.

Further, the utility model discloses set up the check valve between the export of the evaporating pipe of room between cryrogenic and the compressor to configure the check valve into forbidding the refrigerant in this evaporating pipe receives other evaporating pipes, can be less than the temperature of ordinary cold room between cryrogenic and the compressor stop operation, avoid the refrigerant in other evaporating pipes constantly to gather in the evaporating pipe of room between cryrogenic under the effect of pressure differential, the normal refrigeration of room between the influence is ordinary cold.

Further, the utility model discloses a vapor compression refrigerating system and stirling refrigerating system work in turn or continue under ordinary cold mode, have not only improved refrigeration refrigerating plant on the whole to the refrigeration efficiency of cryrogenic compartment, have still reduced refrigeration refrigerating plant's energy consumption, have prolonged stirling refrigerator's life.

The above and other objects, advantages and features of the present invention will become more apparent to those skilled in the art from the following detailed description of specific embodiments thereof, taken in conjunction with the accompanying drawings.

Drawings

Some specific embodiments of the present invention will be described in detail hereinafter, by way of illustration and not by way of limitation, with reference to the accompanying drawings. The same reference numbers in the drawings identify the same or similar elements or components. Those skilled in the art will appreciate that the drawings are not necessarily drawn to scale. In the drawings:

figure 1 is a schematic cross-sectional view of a refrigeration and freezing apparatus according to an embodiment of the present invention;

fig. 2 is a schematic block diagram of a vapor compression refrigeration system according to an embodiment of the present invention;

FIG. 3 is a schematic side view of the case of FIG. 1;

FIG. 4 is a schematic partial rear elevational view of the refrigeration freezer of FIG. 1;

FIG. 5 is a schematic rear elevational view of the refrigeration freezer of FIG. 4 with the device chamber cover plate removed;

FIG. 6 is a schematic rear view of the refrigeration freezer of FIG. 5 with one of the half shells, one of the resilient feet, and the heat retention cover removed;

FIG. 7 is a schematic partial enlarged view of region A in FIG. 6;

FIG. 8 is a schematic side view of the heat exchanger of FIG. 1;

fig. 9 is a schematic structural diagram of a controller according to an embodiment of the present invention.

Detailed Description

Fig. 1 is a schematic cross-sectional view of a refrigeration and freezing apparatus 100 according to an embodiment of the present invention; fig. 2 is a schematic block diagram of a vapor compression refrigeration system according to an embodiment of the present invention; fig. 3 is a schematic side view of the case shown in fig. 1. Referring to fig. 1 to 3, the refrigerating 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, respectively, a stirling refrigerating system for refrigerating the at least one storage compartment, a vapor compression refrigerating system for refrigerating the at least one storage compartment, and a controller 190 for controlling operations of the vapor compression refrigerating system and the stirling refrigerating system. The refrigerating and freezing device 100 may be a refrigerator, a freezer, or the like.

The box body may include an outer box 111, at least one inner container disposed in the outer box 111, and a heat insulation layer 112 disposed between the outer box 111 and the at least one inner container. Wherein, at least one storage compartment is limited by at least one inner container respectively.

In the illustrated embodiment, the tank includes a normal cold bladder 113, a normal cold bladder 114, a normal cold bladder 115, and a cryogenic bladder 116. The vapor compression refrigeration system may be configured to provide cooling to the refrigerated compartment defined by the common cold bladder 113, the common cold compartment defined by the common cold bladder 114 and the common cold bladder 115, and the cryogenic compartment defined by the cryogenic bladder 116, and the stirling refrigeration system may be configured to provide cooling only to the cryogenic compartment defined by the cryogenic bladder 116.

Illustratively, the storage temperature of the cold storage compartment may be from 0 to +8 ℃; the preservation temperature of the common cold chamber can be-14 to-24 ℃; the preservation temperature of the deep cooling chamber can cover the preservation temperature of the common cooling chamber and can be-14-80 ℃.

Specifically, the vapor compression refrigeration system may include a compressor 131, a condenser tube 132, at least one throttling element, and a plurality of evaporator tubes. Wherein, the evaporation pipe 133a, the evaporation pipe 133b and the evaporation pipe 133c can be respectively arranged in the normal-cooling liner 113, the normal-cooling liner 114 and the deep-cooling liner 116. The normal cold inner container 115 can be communicated with the normal cold inner container 114 through an air duct.

The evaporation pipe 133a may be connected in parallel with the evaporation pipe 133c between the condensation duct 132 and the compressor 131. The evaporation tube 133b may be connected in parallel with the evaporation tube 133a and the evaporation tube 133c between the condensation tube 132 and the compressor 131, or connected in series downstream of the evaporation tube 133a and the evaporation tube 133c, or connected in parallel partially with the evaporation tube 133a and the evaporation tube 133c and connected in series partially downstream of the evaporation tube 133a and the evaporation tube 133 c.

The vapor compression refrigeration system may further include a valve 137 provided to open and close at least a refrigerant flow path from the condensation duct 132 to the evaporation duct 133c, and a check valve 138 connected in series between an outlet of the evaporation duct 133c and the compressor 131. The check valve 138 may be configured to prohibit the evaporation tube 133c from receiving the refrigerant in the evaporation tubes 133a and 133b, so as to prevent the refrigerant in the evaporation tubes 133a and 133b from continuously accumulating in the evaporation tube 133c under the action of the pressure difference and affecting the normal refrigeration of the normal cooling chamber when the temperature of the deep cooling chamber is lower than the temperature of the normal cooling chamber and the compressor 131 stops operating (especially when the valve 137 blocks the refrigerant flow path from the condensation tube 132 to the evaporation tube 133 c).

The number of the throttling elements may be plural, and specifically may include the throttling element 136a, the throttling element 136b, and the throttling element 136 c. The throttling element 136a, the throttling element 136b, and the throttling element 136c may be connected in series between the condensation duct 132 and the evaporation duct 133a, the evaporation duct 133b, and the evaporation duct 133c, respectively. The valve 137 may be configured to open and close a refrigerant flow path between the condensation duct 132 and the throttling element 136a and 136 b.

The vapor compression refrigeration system may also include other components such as a filter-drier and a reservoir.

The stirling refrigeration system may include at least one stirling cooler 120, at least one cold conduction device 150 thermally coupled to the cold end of the at least one stirling cooler 120, respectively, and at least one heat sink 160 thermally coupled to the hot end of the at least one stirling cooler 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 that drives the piston in motion. The housing may be composed of a main body 121 and a cylindrical portion 122. The driving mechanism may be disposed within the body 121. The piston may be arranged to reciprocate within the cylinder portion 122 to form a cold end and a hot end.

In some embodiments, the refrigeration and freezing apparatus 100 may be a cross-door refrigerator, and the cryogenic compartment may be a lower storage compartment of the cabinet, such as a lower left or lower right storage compartment, or a partial partition thereof. The stirling cooler 120 may be disposed at the rear side of the cryogenic compartment to facilitate cooling.

In some embodiments, the refrigeration and freezing apparatus 100 may be a multi-door refrigerator, and the deep cooling compartment may be a separate storage compartment of the cabinet, or a partial partition thereof.

In some embodiments, the refrigeration and freezing apparatus 100 may be a three-door refrigerator, and the cryogenic compartment may be a separate storage compartment (preferably a middle compartment) of the cabinet, or a partial partition thereof.

In some embodiments, the refrigeration and freezing apparatus 100 may be a double door refrigerator, and the cryogenic compartment may be an upper or lower storage compartment of the cabinet, or a partial partition thereof.

In some embodiments, the refrigeration and freezing apparatus 100 may be a side-by-side refrigerator, and the cryogenic compartment may be a left or right storage compartment of the cabinet, or a partial partition thereof.

In some embodiments, the refrigerating and freezing device 100 may be a wine chest or a vertical freezer or a horizontal freezer, and the cryogenic compartment may be the only storage compartment thereof, or a partial partition thereof.

In some embodiments, the refrigeration and freezing apparatus 100 may be any of the storage compartments of other various shaped refrigeration and freezing apparatuses, or a partial partition thereof.

In some embodiments, in a refrigeration and freezing apparatus not limited to any of the above forms, a plurality of cryogenic compartments may also be provided as required.

Fig. 4 is a schematic partial rear view of the refrigeration freezer 100 of fig. 1; fig. 5 is a schematic rear view of the refrigeration freezer 100 shown in fig. 4 with the cover 118 of the appliance compartment 117 removed. Referring to fig. 4 and 5, the rear bottom of the outer case 111 may further define a device chamber 117. In particular, the stirling cooler 120 may be disposed within the device chamber 117 to facilitate installation and maintenance of the stirling cooler 120 and to improve stability of the stirling cooler 120, to some extent preventing vibrations generated by the stirling cooler 120 from being transmitted to the cabinet to cause resonance problems.

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 the stirling cooler 120 may be disposed above the hot end thereof to facilitate transfer of cold produced by 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 device chamber is compact, the box body has a large storage space, and installation, maintenance and circuit layout of the compressor 131, the condenser 132 and the stirling cooler 120 are facilitated, thereby reducing production cost.

In some embodiments, the refrigerated freezer 100 can further include a heat retention cover 175. The heat retaining cover 175 may be configured to separate the cold end and the hot end of the stirling cooler 120 between the inner side and the outer side thereof, so as to avoid thermal interference of the heated end of the cold end, and to enable most or even all of the cold energy generated by the cold end to be transmitted to the cryogenic compartment, thereby improving the cooling efficiency of the stirling cooler 120.

In some embodiments, the refrigerating and freezing device 100 may further include a cover 170 disposed outside the body 121 of the stirling cooler 120 to prevent heat generated by the compressor 131 from affecting the operating efficiency of the stirling cooler 120, and to shield vibration noise generated by the stirling cooler 120, thereby reducing noise transmitted to the surrounding environment and improving user experience.

Fig. 6 is a schematic rear view of the refrigeration freezer 100 of fig. 5 with one of the half shells, one of the resilient feet, and the heat retention cover 175 removed; fig. 7 is a schematic partial enlarged view of region a in fig. 6. Referring to fig. 6 and 7, the enclosure 170 may be comprised of two half-shells that are mirror-symmetric about a longitudinal central symmetry plane of the stirling cooler 120. That is, the two half-shells of the casing 170 may be mirror symmetric about a plane coplanar with the direction of piston movement of the Stirling cooler 120 to facilitate assembly of the Stirling cooler 120 with the casing 170 and extraction of the cold and hot ends of the Stirling cooler 120.

The cold guide device 150 may include a cold end adapter thermally connected to the cold end of the stirling cooler 120 and a plurality of cold guide heat pipes thermally connected to the cold end adapter.

The cold end adapter may be provided with a plurality of tube holes. One end of each cold conduction heat pipe can be arranged in each pipe hole and is in thermal connection with the cold end adapter, so that cold energy of the cold end is received, and the cold energy is led out.

Fig. 8 is a schematic side view of the heat exchanger 140 of fig. 1. Referring to fig. 8, the heat exchanger 140 may include a cold conducting plate 142 and a cooling end adapter 141 thermally connected to the cold conducting plate 142.

The cold conducting plate 142 may be formed with a plurality of refrigerant tube holes, and the evaporation tube 133c may extend in a serpentine shape and pass through the plurality of refrigerant tube holes to increase a contact area between the evaporation tube 133c and the cold conducting plate 142.

Refrigeration end adapter 141 may be provided with a plurality of heat pipe apertures. The other ends of the plurality of cold conduction heat pipes can be respectively arranged in the plurality of heat pipe holes and thermally connected with the refrigeration end adapter 141 so as to transmit the received cold energy to the cold conduction plate 142.

In some embodiments, the refrigerator-freezer 100 may further include at least one electric heating tube 180. Each of the electric heating pipes 180 may be disposed to be partially embedded in the cold conducting plate 142 to defrost the heat exchanger 140.

In some embodiments, the refrigeration and freezing apparatus 100 may further include a cooling fan 134 disposed in the cryogenic compartment for circulating air in the cryogenic compartment to more fully exchange heat between the hot air and the cold air in the cryogenic compartment.

The refrigeration fan 134 may be configured to operate when at least one of the vapor compression refrigeration system and the stirling refrigeration system is providing cooling to the cryogenic compartment.

Fig. 9 is a schematic block diagram of the controller 190 according to an embodiment of the present invention. Referring to fig. 9, the controller 190 may include a processing unit 191 and a storage unit 192. The storage unit 192 stores therein a computer program 193, and the computer program 193 is used to implement the control method according to the embodiment of the present invention when being executed by the processing unit 191.

In the first embodiment, the refrigerating and freezing apparatus 100 is provided with the normal mode. In the normal mode, the controller 190 may be configured to control the vapor compression refrigeration system to supply cold to the cryogenic compartment and control the stirling refrigeration system to stop supplying cold to 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; and when the temperature of the compartment of the cryogenic compartment is less than the preset switching temperature and is greater than or equal to the set cryogenic temperature, controlling the Stirling refrigeration system to supply cold to the cryogenic compartment, and controlling the vapor compression refrigeration system to stop supplying cold to the cryogenic compartment.

The utility model discloses in, set for the cryogenic temperature for user input or the temperature is preserved in setting for of the system acquiescence room. The preset switching temperature may be greater than the minimum refrigeration temperature of the vapor compression refrigeration system, for example, the minimum refrigeration temperature of the vapor compression refrigeration system is 40 ℃ and the switching temperature may be-25 ℃.

The utility model discloses a cold-stored refrigerating plant 100 makes vapor compression refrigerating system to cryrogenic room cooling between room temperature more than or equal to predetermine when switching the temperature under the common mode, and room temperature is less than to predetermine when switching the temperature and switches into stirling refrigerating system again and to cryrogenic room cooling between room, has not only improved cold-stored refrigerating plant 100 on the whole to the cryogenic refrigeration efficiency of room between, has still reduced cold-stored refrigerating plant 100's energy consumption, has prolonged stirling refrigerator 120's life.

Further, 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 around the refrigeration chiller 100. That is, the operating power of the stirling cooler 120 is re-determined in real time according to the change in the temperature difference during cooling to save energy while ensuring cooling efficiency.

In the case where the ambient temperature is the same, the operating power of the stirling cooler 120 may be approximately in positive correlation with 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 and 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 cooler 120 may be approximately in positive correlation with the ambient temperature.

Table 1 shows the operating power of the stirling cooler 120 corresponding to the difference between the room temperature of different cryogenic rooms minus the set cryogenic temperature and the ambient temperature around different refrigeration and freezing apparatuses 100 according to an exemplary embodiment of the present invention, where the operating power of the stirling cooler 120 is given in watts (W) and the unit of the temperature difference and the ambient temperature is given in degrees celsius (c).

TABLE 1

The controller 190 may regulate the operating power of the Stirling cryocooler 120 by regulating the input voltage to the Stirling cryocooler 120.

Further, the controller 190 may be further configured to determine the operating speed of the compressor 131 according to the set cryogenic temperature, the set normal temperature, and the ambient temperature around the refrigerating and freezing device 100, so as to make the power distribution of the refrigerating and freezing device 100 more reasonable and achieve efficient refrigeration of the cryogenic compartment without reducing the efficiency of cooling the normal compartment.

The utility model discloses in, set for ordinary cold temperature and preserve the temperature for the setting of user input or the ordinary cold room of system acquiescence.

In the case where the set cryogenic temperature and the ambient temperature are the same, the operating speed of the compressor 131 may be approximately inversely related to the set normal cooling temperature.

In the case where the set deep cooling temperature and the set normal cooling temperature are the same, the operating speed of the compressor 131 may be substantially positively correlated with the ambient temperature.

Further, under the condition that the set normal cooling temperature and the set environment temperature are the same and the vapor compression refrigeration system supplies cooling for the deep cooling chamber, the working rotating speed of the compressor when the set deep cooling temperature is greater than or equal to the preset deep cooling temperature can be greater than or equal to the working rotating speed when the set deep cooling temperature is less than the preset deep cooling temperature, so that the efficiency of supplying cooling for the deep cooling chamber is improved.

For example, the preset switching temperature is-25 ℃ and the preset cryogenic temperature is-21 ℃. Under the same other conditions, the working speed of the compressor can be greater than or equal to the working speed of the compressor when the set cryogenic temperature is greater than or equal to-21 ℃ and the set temperature is greater than or equal to-25 ℃ and less than-21 ℃.

Specifically, table 2 shows the operating speeds of the compressor 131 corresponding to the different set normal cooling temperatures and the different ambient temperatures around the refrigeration and freezing device 100 when the compressor 131 supplies cooling to the deep cooling compartment and sets the deep cooling temperature to be greater than or equal to the preset deep cooling temperature in the normal mode according to an exemplary embodiment of the present invention, where the unit of the operating speed of the compressor 131 is revolutions per minute (rpm), and the unit of the set normal cooling temperature and the ambient temperature is degrees celsius (deg.c).

TABLE 2

Table 3 shows the operating speeds of the compressor 131 corresponding to the different set normal cooling temperatures when the compressor 131 supplies cooling to the deep cooling compartment and the set deep cooling temperature is lower than the preset deep cooling temperature and the ambient temperatures around the different refrigeration devices 100 in the normal mode according to an exemplary embodiment of the present invention, where the unit of the operating speed of the compressor 131 is revolutions per minute (rpm), and the unit of the set normal cooling temperature and the ambient temperature is degrees celsius (° c).

TABLE 3

Further, under the condition that the set cryogenic temperature, the set normal cooling temperature, and the ambient temperature are the same, the operating speed of the compressor 131 when the stirling refrigeration system supplies cold to the cryogenic compartment and the vapor compression refrigeration system supplies cold to the normal cooling compartment may be less than or equal to the operating speed of the compressor 131 when the vapor compression refrigeration system supplies cold to the cryogenic compartment. That is, the operating speed of the compressor 131 when cooling only the cryogenic compartment or both the cryogenic compartment and at least one of the other compartments (the cold storage compartment and the normal cooling compartment) is equal to or higher than the operating speed thereof when cooling of the cryogenic compartment is stopped and cooling of at least one of the other compartments is performed, so that the power distribution is more reasonable.

Table 4 shows the operating speeds of the compressor 131 corresponding to different set normal cooling temperatures and different ambient temperatures around the refrigerator-freezer 100 when the compressor 131 only supplies cold to at least one other storage compartment in the normal mode according to an exemplary embodiment of the present invention, where the unit of the operating speed of the compressor 131 is revolutions per minute (rpm), and the unit of the set normal cooling temperature and the ambient temperature is degrees celsius (° c).

TABLE 4

Further, in the normal mode, the controller 190 may be configured to determine a duty ratio (a ratio of the operating rotational speed to the rated rotational speed) of the cooling fan 134 according to a set cryogenic temperature when the vapor compression refrigeration system supplies cold to the cryogenic compartment, in which case the duty ratio may be less than 100%, so that heat exchange between hot air and cold air in the cryogenic compartment is more sufficient, the refrigeration efficiency is improved, undesirable energy waste is avoided, and the service life of the cooling fan is prolonged. Wherein, the duty ratio of the refrigeration fan 134 may be inversely proportional to the set cryogenic temperature.

Specifically, table 5 shows duty ratios of the refrigeration 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 invention, where the unit of the set normal cold temperature is celsius (deg.c).

TABLE 5

Further, in the normal mode, the controller 190 may be configured to control the refrigeration fan 134 to operate at a duty ratio of 100% when the stirling refrigeration system supplies cold to the cryogenic compartment, so as to further improve the refrigeration efficiency and avoid the reduction in the service life of the refrigeration fan 134 due to too concentrated cold.

Further, the refrigerating and freezing apparatus 100 may be provided with a quick-freezing mode. The quick-freezing mode can be operated when a quick-freezing mode opening instruction input by a user is received, or operated when the refrigerating and freezing device 100 is powered on for the first time (namely the temperature of the compartment between the first time of starting power on of the refrigerating and freezing device 100 and the deep-freezing compartment is lower than the set deep-freezing temperature) or even powered on for the first two times, or operated immediately after the deep-freezing compartment is defrosted, so that the preservation quality of food in the deep-freezing compartment is improved.

In the quick-freezing mode, the controller 190 may be configured to control the vapor compression refrigeration system and the stirling refrigeration system to supply cold to 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; and when the temperature of the compartment of the cryogenic compartment is less than the preset switching temperature and is more than or equal to the set cryogenic temperature, controlling the Stirling refrigeration system to supply cold to the cryogenic compartment, and controlling the vapor compression refrigeration system to stop supplying cold to the cryogenic compartment, so as to further improve the efficiency of supplying cold to the cryogenic compartment.

Further, under the condition that the set normal cooling temperature and the set ambient temperature are the same, the working speed of the compressor 131 in the quick-freezing mode for cooling the deep-cooling compartment may be greater than or equal to the working speed of the compressor 131 in the normal mode for cooling the deep-cooling compartment, so that the energy is saved and the cooling efficiency is further improved.

Table 6 shows the operating speeds of the compressor 131 corresponding to different set normal cooling temperatures when the compressor 131 supplies cold to the deep cooling compartment and different ambient temperatures around the refrigeration and freezing device 100 in the quick-freezing mode according to an exemplary embodiment of the present invention, where the unit of the operating speed of the compressor 131 is revolutions per minute (rpm), and the unit of the set normal cooling temperature and the ambient temperature is degrees celsius (° c).

TABLE 6

Further, in the quick-freeze mode, the controller 190 may be configured to control the refrigeration fan 134 to operate at a duty ratio of 100% to further improve the refrigeration efficiency and prevent the refrigeration capacity from being too concentrated to reduce the service life of the refrigeration fan 134.

Further, 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 stop cooling the cryogenic compartment when the compartment temperature is less than the set cryogenic temperature.

Further, the refrigerating and freezing apparatus 100 may 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 a difference between the detected temperature detected by the detection device and a preset temperature fluctuation value as the compartment temperature of the deep-freezing compartment when determining whether the compartment temperature is greater than or equal to the set deep-freezing temperature; and when judging whether the compartment temperature is lower than the set cryogenic temperature, taking the sum of the detected temperature detected by the detection device and a preset temperature fluctuation value as the compartment temperature of the cryogenic compartment so as to avoid frequent on-off of the part of the vapor compression refrigeration system supplying cold to the cryogenic compartment or frequent on-off of the Stirling refrigeration system.

The utility model discloses in, the temperature fluctuation value can be any value in 1 ~ 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 greater than or equal to a preset switching temperature when the vapor compression refrigeration system supplies cold to the deep-freezing compartment, and use a difference value obtained by subtracting a preset temperature fluctuation value from the detection temperature detected by the detection device as the compartment temperature of the deep-freezing compartment; when the Stirling refrigeration system supplies cold for the cryogenic chamber, whether the temperature of the chamber is lower than a preset switching temperature is judged, the sum of the detection temperature detected by the detection device and a preset temperature fluctuation value is used as the temperature of the cryogenic chamber, and therefore frequent switching between the vapor compression refrigeration system and the Stirling refrigeration system is avoided.

In the second embodiment, it is different from the first embodiment in that, in the normal mode, the controller 190 may be configured to control the vapor compression refrigeration system to supply cold to the cryogenic chamber for a preset time when the temperature of the cryogenic chamber is greater than or equal to the set cryogenic temperature, and the stirling refrigeration system stops supplying cold to the cryogenic chamber; after the preset time, if the temperature of the compartment is still greater than or equal to the set cryogenic temperature, the Stirling refrigeration system is controlled to supply cold to the cryogenic compartment, and the vapor compression refrigeration system stops supplying cold to the cryogenic compartment.

The utility model discloses a refrigerating and freezing device 100 switches refrigerating system through the time, makes two refrigerating system all be in best operating condition, has not only improved refrigerating and freezing device 100 on the whole to the refrigeration efficiency of cryrogenic compartment, has still prolonged compressor 131 and stirling refrigerator 120's life.

Further, the controller 190 may be configured to control the vapor compression refrigeration system to supply the cryogenic compartment with the cold for the preset time in each refrigeration cycle when the set cryogenic temperature is greater than or equal to the preset switching temperature, and restart the stirling refrigeration system if the temperature of the cryogenic compartment is still greater than or equal to the set cryogenic temperature; when the set cryogenic temperature is lower than the preset switching temperature, the vapor compression refrigeration system is controlled to supply cold for the cryogenic chamber for the preset time only in the first refrigeration cycle, and the Stirling refrigeration system is restarted if the temperature of the cryogenic chamber is still greater than or equal to the set cryogenic temperature, so that the refrigeration efficiency is improved, and meanwhile, the use requirements of users are met.

The utility model discloses in, the refrigeration cycle means from vapor compression refrigerating system and/or stirling refrigerating system for cryrogenic interventricular cooling to vapor compression refrigerating system and stirling refrigerating system stop for the cycle of cryrogenic interventricular cooling, from the cycle of completing cryogenic to cryrogenic interventricular cooling promptly. The first refrigeration cycle when the set cryogenic temperature is lower than the preset switching temperature means that the set cryogenic temperature is adjusted from being higher than or equal to the preset switching temperature to being lower than the preset switching temperature.

Controller 190 may be configured to control vapor compression refrigeration system to stop supplying cold for the cryogenic compartment and stirling refrigeration system to supply cold for the cryogenic compartment in other refrigeration cycles except the first refrigeration cycle under the condition that the set cryogenic temperature is less than the preset switching temperature, so that the temperature of the cryogenic compartment is rapidly decreased to the set cryogenic temperature.

Further, the controller 190 may be further configured to determine the aforementioned preset time (i.e., the operating time of the compressor 131) according to the set cryogenic temperature and the ambient temperature around the refrigerating and freezing device 100 to avoid undesirable waste of energy.

Under the condition that the set cryogenic temperature is the same, the preset time can be positively correlated with the ambient temperature.

The predetermined time may be inversely related to the set cryogenic temperature for the same ambient temperature. That is, the lower the set cryogenic temperature, the longer the preset time.

Table 7 shows the working time of the compressor 131 corresponding to the different set cryogenic temperatures and the different ambient temperatures around the refrigeration and freezing device 100 when the compressor 131 provides cold for the cryogenic compartment and the set cryogenic temperature is greater than or equal to the preset switching temperature in the normal mode according to an exemplary embodiment of the present invention, where the unit of the working time of the compressor 131 is minute (min), and the unit of the set normal cold temperature and the ambient temperature is celsius (deg.c).

TABLE 7

Further, in the case where both the set cryogenic temperature and the ambient temperature are the same, the preset time when the set cryogenic temperature is less than the preset switching temperature may be greater than or equal to the preset time when the set cryogenic temperature is greater than or equal to the preset switching temperature, so as to prolong the service life of the stirling cooler 120.

When the set cryogenic temperature is greater than or equal to the set cryogenic temperature, the preset time of the first refrigeration cycle may be greater than the preset time of the other refrigeration cycles to avoid undesirable energy waste and prolong the service life of the compressor 131.

Further, in the quick-freezing mode, the controller 190 may be configured to control the vapor compression refrigeration system and the stirling refrigeration system to provide cooling capacity for the cryogenic compartment during each refrigeration cycle when the set cryogenic temperature is greater than or equal to the preset switching temperature; when the set cryogenic temperature is lower than the preset switching temperature, the vapor compression refrigeration system and the Stirling refrigeration system are controlled to supply cold to the cryogenic chamber for the preset time only in the first refrigeration cycle, if the temperature of the cryogenic chamber is still greater than or equal to the set cryogenic temperature after the preset time, the Stirling refrigeration system is controlled to supply cold to the cryogenic chamber, and the vapor compression refrigeration system stops supplying cold to the cryogenic chamber, so that the efficiency of supplying cold to the cryogenic chamber is further improved.

The controller 190 may be configured to control the stirling refrigeration system to supply cooling to the cryogenic compartment and the vapor compression refrigeration system to stop supplying cooling to the cryogenic compartment during the other refrigeration cycles except the first refrigeration cycle when the set cryogenic temperature is less than the preset switching temperature.

In the quick-freezing mode, the preset time when the set cryogenic temperature is less than the preset switching temperature may be greater than or equal to the preset time when the set cryogenic temperature is greater than or equal to the preset switching temperature in the quick-freezing mode. In the quick-freezing mode, the preset time when the set cryogenic temperature is greater than or equal to the preset switching temperature may be greater than or equal to the preset time when the set cryogenic temperature is less than the preset switching temperature in the normal mode.

In the third embodiment, it is different from the second embodiment in that, in the normal mode, the controller 190 may be configured to control the vapor compression refrigeration system and the stirling refrigeration system to alternately supply cooling to the cryogenic compartment when the compartment temperature of the cryogenic compartment is equal to or greater than the set cryogenic temperature. In each alternate refrigeration cycle, the stirling refrigeration system can firstly supply cold to the deep cooling chamber, so that the refrigeration efficiency of the refrigeration and freezing device 100 to the deep cooling chamber is improved on the whole while the two systems are in the optimal working state, and the energy consumption is reduced.

Further, the controller 190 may be configured to control the vapor compression refrigeration system and the stirling refrigeration system to alternately refrigerate in each refrigeration cycle when the set cryogenic temperature is greater than or equal to the preset switching temperature; when the set cryogenic temperature is lower than the preset switching temperature, the vapor compression refrigeration system and the Stirling refrigeration system are controlled to alternately refrigerate only in the first refrigeration cycle, so that the refrigeration efficiency is improved, and meanwhile, the use requirements of users are met.

Further, the controller 190 may be configured to determine the cool down time for each time the stirling refrigeration system is to cool the cryogenic compartment and the cool down time for each time the vapor compression refrigeration system is to cool the cryogenic compartment in each alternating refrigeration cycle based on the set cryogenic temperature and the ambient temperature surrounding the refrigeration chiller 100 to avoid undesirable energy waste. The cooling time for each time the stirling refrigeration system supplies cold to the cryogenic compartment and the cooling time for each time the vapor compression refrigeration system supplies cold to the cryogenic compartment may be determined according to a table similar to table 7.

The cooling time for each stirling refrigeration system to provide cooling to the cryogenic compartment and the cooling time for each vapor compression refrigeration system to provide cooling to the cryogenic compartment in each alternating refrigeration cycle may be approximately inversely proportional to the set cryogenic temperature for the same ambient temperature.

In the case where the set cryogenic temperature is the same, the cooling time for each stirling refrigeration system to supply cold to the cryogenic compartment and the cooling time for each vapor compression refrigeration system to supply cold to the cryogenic compartment in each alternating refrigeration cycle may be approximately proportional to the ambient temperature.

Furthermore, in each alternate refrigeration cycle, the cooling time of the refrigeration system supplying cooling to the back deep cooling chamber can be more than or equal to that of the refrigeration system supplying cooling to the front deep cooling chamber, so that the two systems are prevented from being frequently switched while the performance of the two refrigeration systems is ensured.

For the refrigerator with the lowest refrigerating temperature of the vapor compression refrigerating system being lower than the lowest refrigerating temperature of the Stirling refrigerating system, the cold supply time of the two refrigerating systems can be set to enable the temperature of the compartment of the Stirling refrigerating system, which is cooled to the deep cooling compartment, to be lower than the set deep cooling temperature when the set deep cooling temperature is lower than the lowest refrigerating temperature of the vapor compression refrigerating system.

In particular, the controller 190 may be configured to start the vapor compression refrigeration system and supply cold within a preset time when it is determined that a condition that the vapor compression refrigeration system and the stirling refrigeration system are simultaneously switched from the off state to the on state is satisfied, and after the preset time, start the stirling refrigeration system to supply cold together with the vapor compression refrigeration system, so as to reduce vibration noise of the compressor 131 and the stirling refrigerator 120, reduce the maximum power of the whole machine, improve the refrigeration efficiency as a whole, reduce the initial load of the stirling refrigerator 120, further reduce the vibration noise, and prolong the service life of the stirling refrigerator 120. In this embodiment, the predetermined time may be 20-40 min.

The condition for simultaneously switching the vapor compression refrigeration system and the stirling refrigeration system from the off state to the on state may be a condition for supplying the cold storage refrigeration apparatus 100 with electricity for the first time, a condition for operating the quick-freeze mode in a case where the vapor compression refrigeration system stops supplying the cold to the cold storage compartment and the normal cold compartment, and a condition for supplying the vapor compression refrigeration system to the normal cold compartment and the stirling refrigeration system to the cold storage compartment.

When the vapor compression refrigeration system is turned on (including determining that a condition that the vapor compression refrigeration system and the stirling refrigeration system are simultaneously switched from the off state to the on state is satisfied, and during operation of the stirling refrigerator 120), the controller 190 may be configured to control the compressor 131 to increase from the preset initial rotational speed to the target rotational speed at a preset rotational speed step length every preset first time interval, so as to further reduce vibration noise. The target rotation speed is a target operation rotation speed of the compressor 131, and may be determined by any one of the methods for determining the operation rotation speed of the compressor 131 in the foregoing embodiments.

In some exemplary embodiments, the predetermined initial rotation speed may be 1000 to 1500rpm, the first time interval may be 2 to 5min, and the predetermined rotation speed step may be 300 to 600 rpm.

When the stirling refrigeration system is turned on (including determining that a condition that the vapor compression refrigeration system and the stirling refrigeration system are simultaneously switched from the off state to the on state is satisfied, and during operation of the compressor 131), the controller 190 may be configured to control the stirling refrigerator 120 to increase from the preset initial power to the target power at the preset cooling step length at every preset second time interval, so as to further reduce vibration noise. The target power is the target operating power of the stirling cooler 120, and may be determined by any of the methods for determining the operating power of the stirling cooler 120 described in any of the embodiments above.

In some exemplary embodiments, the predetermined initial power may be 5-10W, the second time interval may be 2-5 min, and the predetermined power step may be 4-6W.

Thus, it should be appreciated by those skilled in the art that while a number of exemplary embodiments of the invention have been shown and described in detail herein, many other variations and modifications can be made, consistent with the principles of the invention, which are directly determined or derived from the disclosure herein, without departing from the spirit and scope of the invention. Accordingly, the scope of the present invention should be understood and interpreted to cover all such other variations or modifications.

Claims (10)

1. A refrigeration freezer apparatus, comprising:

the refrigerator comprises a box body, a door body and a refrigerator, wherein a plurality of storage compartments are defined, and one storage compartment is a deep cooling compartment;

a vapor compression refrigeration system, at least a portion of which is disposed within or passes into said cryogenic compartment to provide cooling thereto; and

stirling refrigerating system, at least some set up in the cryrogenic compartment or reach in the cryrogenic compartment is indoor, in order to the cryrogenic compartment cooling.

2. A refrigerator-freezer as claimed in claim 1, wherein the vapour compression refrigeration system comprises:

the compressor, the condenser pipe and the throttling element;

a plurality of evaporating pipes, one of said evaporating pipes is disposed in said deep cooling chamber, and the other of said evaporating pipes and the evaporating pipe in said deep cooling chamber are connected in parallel between said condensing pipe and said compressor or at least partially connected in series downstream of the evaporating pipe in said deep cooling chamber; and

and the valve is set to at least switch on and off the refrigerant flow path from the condensation pipe to the evaporation pipe in the deep cooling chamber.

3. A refrigeration chiller as claimed in claim 2, wherein the vapor compression refrigeration system further comprises:

and the check valve is connected between the outlet of the evaporation pipe in the deep cooling chamber and the compressor in series and is configured to prohibit the evaporation pipe from receiving the refrigerants in other evaporation pipes.

4. A refrigerator-freezer according to claim 1, wherein, in the normal cooling mode,

the vapor compression refrigeration system is configured to supply cold to the cryogenic compartment when the compartment temperature of the cryogenic compartment is greater than or equal to a preset switching temperature; and is

The Stirling refrigerating system is located to work as the room temperature of cryrogenic compartment more than or equal to sets for cryrogenic temperature and is less than when predetermineeing the switching temperature do the cryrogenic compartment cooling.

5. A refrigerator-freezer according to claim 1, wherein, in the quick-freeze mode,

the vapor compression refrigeration system is configured to supply cold to the cryogenic compartment when the compartment temperature of the cryogenic compartment is greater than or equal to a preset switching temperature; and is

The Stirling refrigerating system is arranged to supply cold for the cryogenic chamber when the temperature of the cryogenic chamber is greater than or equal to the set cryogenic temperature.

6. A refrigerator-freezer according to claim 1, wherein, in the normal cooling mode,

the vapor compression refrigeration system is configured to supply cold to the cryogenic compartment within a preset time when the compartment temperature of the cryogenic compartment is greater than or equal to a set cryogenic temperature; and is

The Stirling refrigerating system is configured to supply cold to the deep cold chamber after the preset time and when the temperature of the deep cold chamber is greater than or equal to the set deep cold temperature.

7. A refrigerator-freezer according to claim 1, wherein, in the normal cooling mode,

the vapor compression refrigeration system and the Stirling refrigeration system are configured to alternately supply cold to the cryogenic chamber when the temperature of the cryogenic chamber is greater than or equal to a set cryogenic temperature; wherein

In each refrigerating period of the alternate refrigeration, the Stirling refrigerating system firstly supplies cold for the deep cooling chamber.

8. A refrigerator-freezer according to claim 1, wherein, in the quick-freeze mode,

the vapor compression refrigeration system is configured to supply cold to the cryogenic compartment within a preset time when the compartment temperature of the cryogenic compartment is greater than or equal to a set cryogenic temperature; and is

The Stirling refrigerating system is configured to supply cold to the cryogenic compartment when the compartment temperature of the cryogenic compartment is greater than or equal to a set cryogenic temperature.

9. A refrigerator-freezer as claimed in claim 1, further comprising:

the refrigerating fan is arranged in the deep cooling chamber and used for circulating air in the deep cooling chamber; and is

The refrigeration fan is configured to operate when at least one of the vapor compression refrigeration system and the stirling refrigeration system is providing cooling to the cryogenic compartment.

10. A refrigerator-freezer according to claim 1,

the refrigerating and freezing device is a cross side-by-side refrigerator, and the deep cooling chamber is a lower storage chamber of the box body; and is

And the Stirling refrigerating machine of the Stirling refrigerating system is arranged at the rear side of the deep cooling chamber.

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