CN111059832B

CN111059832B - Refrigeration and freezing equipment

Info

Publication number: CN111059832B
Application number: CN201911380009.9A
Authority: CN
Inventors: 李靖; 野田俊典; 刘会; 刘煜森; 万新明; 俞国新; 房雯雯; 陶瑞涛; 孙永升
Original assignee: Qingdao Haier Refrigerator Co Ltd; Qingdao Haier Smart Technology R&D Co Ltd; Haier Smart Home Co Ltd
Current assignee: Qingdao Haier Refrigerator Co Ltd; Qingdao Haier Smart Technology R&D Co Ltd; Haier Smart Home Co Ltd
Priority date: 2019-12-27
Filing date: 2019-12-27
Publication date: 2024-09-13
Anticipated expiration: 2039-12-27
Also published as: CN111059832A

Abstract

The present invention provides a refrigeration and freezing device. The refrigeration and freezing device includes a housing, a heat exchanger, a vapor compression refrigeration system and a Stirling refrigeration system. The housing defines a deep freezing chamber. The heat exchanger is at least partially disposed in the deep freezing chamber. The vapor compression refrigeration system includes an evaporator tube disposed in the deep freezing chamber, and the evaporator tube is configured to be thermally connected to the heat exchanger. The Stirling refrigeration system includes a Stirling refrigerator, and the cold end of the Stirling refrigerator is configured to be thermally connected to the heat exchanger. The refrigeration and freezing device of the present invention thermally connects the refrigerant pipe of the vapor compression refrigeration system and the cold and heat conducting pipe of the Stirling refrigeration system to the heat exchanger, which not only has high refrigeration efficiency, but also can realize a wide range of temperature change in the deep freezing chamber, flexibly meets the use requirements of different users, and has high applicability.

Description

Refrigerating and freezing device

Technical Field

The invention relates to the field of refrigeration, in particular to a refrigeration and freezing device adopting a Stirling refrigeration system and a vapor compression refrigeration system for refrigeration.

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 refrigeration in the fields of aerospace, medical treatment and the like, the refrigerating temperature of the Stirling refrigerating system can be lower than minus 200 ℃, but the cold end area of the Stirling refrigerator is smaller, and the refrigerating efficiency is lower.

Disclosure of Invention

It is an object of the present invention to overcome at least one of the technical drawbacks of the prior art by providing a refrigeration chiller employing a stirling refrigeration system and a vapor compression refrigeration system for refrigeration.

It is a further object of the present invention to facilitate the assembly of Stirling and vapor compression refrigeration systems with heat exchangers.

It is a further object of the present invention to avoid accumulation of refrigerant in the vapor compression refrigeration system in the evaporator tubes that cool the cryogenic compartments.

In particular, the present invention provides a refrigerating and freezing apparatus characterized by comprising:

a box defining a cryogenic compartment;

A heat exchanger at least partially disposed within the cryogenic compartment;

A vapor compression refrigeration system comprising an evaporator tube disposed within said cryogenic compartment and said evaporator tube being configured to be thermally coupled to said heat exchanger; and

A stirling cooler system comprising a stirling cooler and the cold end of the stirling cooler being arranged in thermal communication with the heat exchanger.

Optionally, the stirling cooler system further comprises a cold guide means, and the cold guide means comprises:

At least one cold-conducting and heat-conducting tube arranged in thermal connection with the cold end; and the heat exchanger comprises:

The first cold guide plate is provided with a refrigerant pipe connecting structure and is thermally connected with the evaporation pipe; and

The second cold guide plate is provided with a heat pipe connecting structure and is in thermal connection with the at least one cold guide heat pipe; wherein the method comprises the steps of

The second cold guide plate is integrally formed with the first cold guide plate or is directly thermally connected with the first cold guide plate.

Optionally, the refrigeration and freezing device further comprises:

the locking piece is arranged on one side, far away from the first cold guide plate, of the second cold guide plate; wherein the method comprises the steps of

The heat pipe connection structure comprises at least one heat pipe groove; and is also provided with

The locking piece is provided with at least one heat pipe groove which is combined with the at least one heat pipe groove of the second heat conduction plate along the longitudinal direction of the heat conduction pipe and is used for clamping the heat conduction pipe therebetween.

Optionally, the case includes:

An outer case;

the cryogenic inner container is limited with the cryogenic chamber, is provided with a plurality of clamping claws and is provided with an installation opening; and

The heat insulation layer is arranged between the outer box and the cryogenic liner; wherein the method comprises the steps of

The part of the at least one cold and heat conducting pipe, which is close to the second cold conducting plate, and the locking piece are preset in the heat insulation layer; and is also provided with

The evaporation pipe is clamped and fixed on the clamping claws and enables the second cold guide plate to penetrate through the mounting opening to be in thermal connection with the at least one cold guide pipe.

Optionally, the cold-conducting device further includes a cold-end adapter, the number of the cold-conducting heat pipes is plural and the cold-end adapter includes:

the two mounting pieces are arranged in mirror symmetry with respect to a longitudinal central plane of the cold end and are clamped between the two mounting pieces, and at least one pipe groove is respectively formed in the two mounting pieces; and

And the locking piece is provided with a plurality of pipe grooves which are combined with the pipe grooves of the two mounting pieces along the longitudinal direction of the heat conduction pipe and clamp the heat conduction pipe between the heat conduction pipe and the two mounting pieces.

Optionally, the refrigeration and freezing device further comprises:

The backboard is arranged on one side of the first cold guide plate, which is close to the second cold guide plate; wherein the method comprises the steps of

The refrigerant pipe connecting structure comprises at least one refrigerant pipe groove; and is also provided with

The back plate is provided with at least one refrigerant pipe groove which is combined with the at least one refrigerant pipe groove of the first cold guide plate along the longitudinal direction of the evaporation pipe and is used for clamping the evaporation pipe therebetween.

Optionally, the first cold guide plate includes:

the base plate is provided with the refrigerant pipe connecting structure; and

The fins are arranged at intervals and extend from the base plate in a direction away from the second cold guide plate.

Optionally, the refrigeration and freezing device further comprises:

And a refrigeration fan disposed within the cryogenic compartment and configured to operate when at least one of the vapor compression refrigeration system and the Stirling refrigeration system is cooling the cryogenic compartment.

Optionally, the refrigeration fan is arranged downstream of the heat exchanger; and/or

The refrigerating and freezing device further comprises an air duct cover plate which forms a compartment air duct together with the rear wall of the cryogenic compartment, the refrigerating fan and at least part of the heat exchanger are arranged in the compartment air duct, and the air duct cover plate is provided with at least one air supply opening and an air return opening arranged below the at least one air supply opening.

Optionally, the box body further defines a common cooling chamber; and the vapor compression refrigeration system further comprises:

a compressor, a condenser tube and a throttling element;

The other evaporating pipe is arranged in the common cooling room and connected with the condensing pipe and the compressor in parallel or at least partially connected in series at the downstream of the evaporating pipe;

The valve is arranged to at least switch on and off a refrigerant flow path from the condensation pipe to the evaporation pipe; and

The one-way valve is connected in series between the outlet of the one evaporation tube and the compressor and is configured to inhibit the one evaporation tube from receiving the refrigerant in the other evaporation tube.

The refrigerating and freezing device of the invention has high refrigerating efficiency, can realize wide temperature variation of the cryogenic chamber, flexibly meets the use requirements of different users and has high applicability by thermally connecting the refrigerant pipe of the vapor compression refrigerating system and the cold and heat conducting pipe of the Stirling refrigerating system with the heat exchanger.

Furthermore, the part of the cold and heat conducting pipe close to the second cold and heat conducting plate and the locking piece are preset in the foaming layer, the plurality of clamping jaws are arranged on the cryogenic inner container, the refrigerant pipe is clamped and fixed on the clamping jaws, and meanwhile the second cold and heat conducting plate is in thermal connection with the cold and heat conducting pipe.

Further, the one-way valve is arranged between the outlet of the evaporation tube of the cryogenic compartment and the compressor, and the one-way valve is configured to inhibit the evaporation tube from receiving the refrigerant in other evaporation tubes, so that the refrigerant in other evaporation tubes is prevented from continuously accumulating in the evaporation tube of the cryogenic compartment under the action of pressure difference when the temperature of the cryogenic compartment is lower than that of the cryogenic compartment and the compressor stops running, and the normal refrigeration of the cryogenic compartment is influenced.

Furthermore, the heat conduction pipe comprises a plurality of bending parts, and the bending angle of at least one bending part is more than or equal to 90 degrees and less than 180 degrees, so that the vibration transmitted to the heat exchanger by the Stirling refrigerator is effectively reduced, the problem that echo amplification noise is generated when the vibration is transmitted to the cryogenic compartment is avoided, the connection reliability of the heat exchanger and the heat conduction pipe is improved, and the user experience is improved.

The above, as well as additional objectives, advantages, and features of the present invention will become apparent to those skilled in the art from the following detailed description of a specific embodiment of the present invention when read in conjunction with the accompanying drawings.

Drawings

Some specific embodiments of the invention 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 side view of a heat exchanger according to one embodiment of the invention;

FIG. 2 is a schematic side view of the heat exchanger of FIG. 1 from another angle;

FIG. 3 is a schematic exploded view of the heat exchanger shown in FIG. 2;

Fig. 4 is a schematic enlarged view of the area a in fig. 3;

FIG. 5 is a schematic side view of a first cold guide plate and a second cold guide plate integrally formed in accordance with another embodiment of the present invention;

FIG. 6 is a schematic cross-sectional view of a refrigerated freezer according to one embodiment of the invention;

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

FIG. 8 is a schematic partial view of a refrigerated freezer employing the heat exchanger of FIG. 5;

FIG. 9 is a schematic partial rear view of the refrigeration and freezer of FIG. 6;

FIG. 10 is a schematic rear view of the refrigeration and freezer of FIG. 9 with the device chamber first cold guide plate removed;

FIG. 11 is a schematic rear view of the refrigeration and freezer of FIG. 10 with one of the half shells, one of the resilient feet, and the insulating cover removed;

FIG. 12 is a schematic partial enlarged view of region C in FIG. 11;

FIG. 13 is a schematic exploded view of the cold guide of FIG. 12;

FIG. 14 is a schematic side view of a heat pipe according to embodiment 1 of the present invention;

FIG. 15 is a stress test chart of example 1, wherein the abscissa is frequency and the ordinate is maximum stress;

fig. 16 is an acceleration test chart of embodiment 1, in which the abscissa is frequency and the ordinate is acceleration;

FIG. 17 is a schematic side view of a cold and hot conducting pipe according to embodiment 2 of the present invention;

FIG. 18 is a stress test chart of example 2, wherein the abscissa is frequency and the ordinate is maximum stress;

fig. 19 is an acceleration test chart of example 2, in which the abscissa is frequency and the ordinate is acceleration;

FIG. 20 is a schematic side view of a heat pipe for conducting cold according to comparative example 1 of the present invention;

FIG. 21 is a stress test chart of comparative example 1, in which the abscissa is frequency and the ordinate is maximum stress;

FIG. 22 is a schematic cross-sectional view of the resilient pad of FIG. 12;

fig. 23 is a schematic block diagram of a vapor compression refrigeration system of one embodiment of the present invention.

Detailed Description

FIG. 1 is a schematic side view of a heat exchanger 100 according to one embodiment of the invention; FIG. 2 is a schematic side view of the heat exchanger 100 of FIG. 1 from another angle; fig. 3 is a schematic exploded view of the heat exchanger 100 shown in fig. 2. Referring to fig. 1 to 3, the heat exchanger 100 may include a first cold guide plate 120 and a second cold guide plate 130.

The first cold guide plate 120 may be provided with a refrigerant pipe connection structure for being thermally connected with the refrigerant pipe to receive cooling capacity or heat of the refrigerant pipe. The refrigerant pipe can be an evaporation pipe (absorbing heat) or a condensation pipe (releasing heat) of the vapor compression refrigeration system. In the present invention, at least one is one, two or more than two.

The second cold guide plate 130 may be provided to be thermally connected with the first cold guide plate 120, and provided with a heat pipe connection structure for being thermally connected with the heat pipe to receive the cold or heat of the heat pipe. Wherein the heat pipe may be configured to be thermally coupled to a cold, hot side of, for example, the stirling cooler 220, a cold, hot side of the semiconductor cooler, or a heat source.

The first cold guide plate 120 and the second cold guide plate 130 of the heat exchanger 100 are respectively provided with a refrigerant pipe connection structure and a heat pipe connection structure, and can selectively exchange heat with the refrigerant pipe and/or the heat pipe, so that the flexibility of a refrigerating and heating mode of the heat exchanger 100 is improved, and a chamber provided with the heat exchanger 100 has a larger temperature adjustment range.

In some embodiments, the second cold guide plate 130 may be disposed to be thermally connected with the middle region of the first cold guide plate 120 to improve temperature uniformity of the first cold guide plate 120.

In some embodiments, the heat exchanger 100 may further include a back plate 110 disposed at a side of the first cold guide plate 120 adjacent to the second cold guide plate 130.

Fig. 4 is a schematic enlarged view of the area a in fig. 3. Referring to fig. 3 and 4, the refrigerant pipe connection structure may include at least one refrigerant pipe groove 115. The back plate 110 may be correspondingly provided with at least one refrigerant pipe groove 115. The at least one refrigerant pipe groove 115 of the first cold guide plate 120 and the at least one refrigerant pipe groove 115 of the back plate 110 may be disposed to be split along a longitudinal direction of the refrigerant pipe (i.e., a length direction, an axial direction of the refrigerant pipe) and to sandwich the refrigerant pipe therebetween to fix the refrigerant pipe and receive cold or heat of the refrigerant pipe.

The projection of the at least one refrigerant pipe groove 115 to a direction approaching the second cold guide plate 130 may be located at an outer side of the heat pipe connection structure to improve the cooling and heating efficiency of the heat exchanger 100 as a whole.

The back plate 110 may have a relief hole 111 formed at a portion thereof within a projection range of the heat pipe connection structure to save costs and further improve cooling and heating efficiency of the heat exchanger 100 as a whole.

The first cold guide plate 120 may include a base plate 121 provided with at least one refrigerant pipe groove 115 and a plurality of cold guide fins 122 disposed at intervals and extending from the base plate 121 in a direction away from the second cold guide plate 130, so as to increase a heat exchange area of the first cold guide plate 120, thereby improving the cooling and heating efficiency of the heat exchanger 100.

The first cold guide plate 120 may further be provided with at least one heating tube slot 113 having an opening facing away from the second cold guide plate 130 for being thermally connected with the electric heating tube 280, so as to prevent the heat exchanger 100 from being frosted for a long time to reduce the refrigerating efficiency.

The heat exchanger 100 may further include a locking member 140 disposed at a side of the second cold guide plate 130 remote from the first cold guide plate 120.

The heat pipe connection structure may include at least one heat pipe slot 135. The locking member 140 may be correspondingly provided with at least one heat pipe slot 135. The at least one heat pipe groove 135 of the locking member 140 and the at least one heat pipe groove 135 of the second cold guide plate 130 may be disposed to be split along a longitudinal direction of the heat pipe (i.e., a length direction of the heat pipe, an axial direction of the heat pipe) and sandwich the heat pipe therebetween to fix the heat pipe and receive cold or heat of the heat pipe.

Heat conductive silicone grease may be disposed within the refrigerant tube slots 115 and/or within the heat pipe slots 135 to increase the heat exchange efficiency of the refrigerant tubes and/or heat pipes with the heat exchanger 100.

In some embodiments, the first cold guide plate 120 and the second cold guide plate 130 may be independent from each other. Specifically, the back plate 110 may be disposed to be thermally connected with the first cold guide plate 120. The second cold guide plate 130 may be disposed on a side of the back plate 110 away from the first cold guide plate 120 and thermally connected to the back plate 110, so as to simplify the assembly process.

Fig. 5 is a schematic side view of a first cold guide plate and a second cold guide plate integrally formed according to another embodiment of the present invention. Referring to fig. 5, in other embodiments, the second cold guide plate 130 may be provided to be integrally formed with the first cold guide plate 120 or directly thermally connected with the first cold guide plate 120 to reduce thermal resistance.

In this embodiment, the second cold guide plate 130 may be disposed to pass through the escape hole 111 such that the heat pipe connection structure is located at a side of the back plate 110 remote from the first cold guide plate 120.

Based on the heat exchanger 100 of any of the above embodiments, the present invention also provides a refrigeration and freezer 200. Fig. 6 is a schematic cross-sectional view of a refrigerated chiller 200 according to one embodiment of the present invention; FIG. 7 is a schematic enlarged view of region B in FIG. 6; FIG. 8 is a schematic partial view of a refrigerated freezer employing the heat exchanger of FIG. 5; fig. 9 is a schematic partial rear view of the refrigeration and freezer 200 of fig. 6. Referring to fig. 6 to 9, the refrigerating and freezing apparatus 200 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 refrigerating system for refrigerating the at least one storage compartment and a vapor compression refrigerating system for refrigerating the at least one storage compartment, respectively, and a controller for controlling operations of the vapor compression refrigerating system and the stirling refrigerating system. The refrigerating and freezing apparatus 200 may be a refrigerator, a freezer, etc.

The case may include an outer case 211, at least one inner container disposed within the outer case 211, and a heat insulation layer 212 disposed between the outer case 211 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 box includes a supercooled liner 213, a supercooled liner 214, a supercooled liner 215, and a supercooled liner 216. The vapor compression refrigeration system may be configured to provide cooling to the common cold compartments defined by the common cold liner 213, the common cold liner 214, and the common cold liner 215, and the sub-cold compartments defined by the sub-cold liner 216, and the stirling refrigeration system may be configured to provide cooling only to the sub-cold compartments defined by the sub-cold liner 216.

Fig. 23 is a schematic block diagram of a vapor compression refrigeration system of one embodiment of the present invention. Referring to fig. 23, in particular, a vapor compression refrigeration system can include a compressor 231, a condenser tube 232, at least one throttling element, and a plurality of evaporator tubes. The evaporation tube 233a, the evaporation tube 233b, and the evaporation tube 233c may be disposed in the common cooling liner 213, the common cooling liner 214, and the cryogenic liner 216, respectively. The common cooling liner 215 may be in communication with the common cooling liner 214 via an air duct.

The evaporation tube 233a may be connected in parallel with the evaporation tube 233c between the condensation tube 232 and the compressor 231. The evaporation tube 233b may be connected in parallel with the evaporation tube 233a and the evaporation tube 233c between the condensation tube 232 and the compressor 231, or connected in series downstream of the evaporation tube 233a and the evaporation tube 233c, or connected in parallel with the evaporation tube 233a and the evaporation tube 233c in part and connected in series downstream of the evaporation tube 233a and the evaporation tube 233c in part.

The vapor compression refrigeration system may further include a valve 237 configured to open and close at least the refrigerant flow path from the condenser tube 232 to the evaporator tube 233c, and a one-way valve 238 connected in series between the outlet of the evaporator tube 233c and the compressor 231. The check valve 238 may be configured to prohibit the refrigerant in the evaporator tube 233a and the evaporator tube 233b from being received by the evaporator tube 233c, so as to prevent the refrigerant in the evaporator tube 233a and the evaporator tube 233b from continuously accumulating in the evaporator tube 233c under the pressure difference when the temperature of the sub-cooling compartment is lower than the temperature of the sub-cooling compartment and the compressor 231 stops operating (particularly when the valve 237 blocks the refrigerant flow path from the condenser tube 232 to the evaporator tube 233 c).

The number of throttling elements may be plural and may specifically include a throttling element 236a, a throttling element 236b, and a throttling element 236c. The throttling element 236a, the throttling element 236b, and the throttling element 236c may be connected in series between the condensing duct 232 and the evaporating duct 233a, the evaporating duct 233b, and the evaporating duct 233c, respectively. The valve 237 may also be configured to open and close the refrigerant flow path between the condenser tube 232 and the throttling element 236a and the throttling element 236 b.

The vapor compression refrigeration system may also include other components such as a dry filter and a liquid storage bag.

The Stirling refrigeration system may include at least one Stirling refrigerator 220, at least one cold guide 250 thermally coupled to a cold side of the at least one Stirling refrigerator 220, respectively, and at least one heat sink 260 thermally coupled to a hot side of the at least one Stirling refrigerator 220, respectively. In the illustrated embodiment, the number of Stirling coolers 220 is one.

Specifically, each Stirling cooler 220 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 main body 221 and a cylindrical portion 222. The drive mechanism may be disposed within the body 221. The piston may be configured to reciprocate within the barrel portion 222 to form a cold end and a hot end.

The cold guide 250 may include a cold end adapter thermally coupled to the cold end of the Stirling refrigerator 220 and at least one cold guide tube 252 thermally coupled to the cold end adapter.

The evaporation tube 233c may be disposed to be thermally connected with the first cold guide plate 120 through a refrigerant tube connection structure. At least one cold-conducting pipe 252 may be provided to be thermally connected with the second cold-conducting plate 130 through a heat pipe connection structure. The first cold guide plate 120 can be disposed in the cryogenic liner 216, so as to improve the refrigerating efficiency of the evaporating pipe 233c and the cold guide heat pipe 252 to the cryogenic compartment, realize wide temperature variation of +8 to-80 ℃ in the cryogenic compartment, and flexibly meet the use requirements of different users.

The number of the refrigerant pipe grooves 115 of the first cold guide plate 120 may be plural. The evaporation tube 233c may extend in a serpentine shape and be partially disposed in the plurality of refrigerant tube grooves 115 of the first cold guide plate 120 to increase the contact area between the evaporation tube 233c and the first cold guide plate 120.

The cryogenically cooled liner 216 may be provided with a plurality of jaws 282. The evaporation tube 233c may be fastened to the plurality of jaws 282 to fix the heat exchanger 100.

The portion of the at least one heat pipe 252 adjacent to the second cold guide plate 130 and the locking member 140 may be preset in the heat insulation layer 212. The cryogenic liner 216 may be provided with a mounting opening. The second cold guide plate 130 may be disposed through the mounting opening and thermally connected with the cold guide heat pipe 252.

In the embodiment in which the first cold guide plate 120 and the second cold guide plate 130 are independent of each other, the second cold guide plate 130 may be disposed to be fixedly connected to the periphery of the mounting opening and thermally connected to the cold and heat guide pipe 252. That is, the locking member 140 and the cold/hot pipe 252 can be assembled with the second cold guide plate 130, and then foamed between the cryogenic liner 216 and the outer box 211 to form the heat insulation layer 212, so as to simplify the production process and improve the production efficiency.

The back plate 110 may be thermally connected to the second cold guide plate 130 when the evaporation tube 233c is fastened to the plurality of jaws 282, so that the installation connection is reliable and the production efficiency is further improved.

Referring to fig. 8, in the embodiment in which the first cold guide plate 120 and the second cold guide plate 130 are integrally formed or directly thermally connected, the assembly of the locking member 140 and the heat guide pipe 252 may be completed by a similar part to the second cold guide plate 130 of the previous embodiment, and then the heat insulation layer 212 may be formed by foaming between the deep cooling liner 216 and the outer case 211. And the part is removed after foaming is completed.

The second cold guide plate 130 may be thermally connected to the cold guide pipe 252 when the evaporation pipe 233c is fastened to the plurality of jaws 282, so as to reduce thermal resistance, make the installation connection reliable, and further improve production efficiency.

The refrigeration and chiller 200 may also include a cover 284 disposed outside of the cryogenically cooled liner 216. The cover 284 may cover the portion of the at least one cold-conducting tube 252 adjacent to the second cold-conducting plate 130 and the locking member 140 therein to make foaming more uniform and to improve the heat insulation performance of the heat insulation layer 212.

The cap 284 may be provided with at least one through hole. The locking member 140 may be fixedly connected to the second cold guide plate 130 or a similar part of the second cold guide plate 130, and the cover 284 covers the locking member 140 and is fixedly connected to the cryogenic liner 216. The at least one heat pipe 252 may be inserted into the heat pipe connection structure through the at least one through hole of the cover 284.

The refrigeration chiller 200 may also include an electric heating tube 280 for defrosting the heat exchanger 100. The number of the heating tube slots 113 may be plural, and the electric heating tube 280 may be serpentine-shaped between the plurality of cold guide fins 122 and thermally connected with the first cold guide plate 120 to increase the heat exchanging area of the electric heating tube 280.

Referring to fig. 6, in some embodiments, the refrigeration chiller 200 also includes a refrigeration fan 234 disposed in the cryogenic compartment. The refrigeration fan 234 may be configured to operate when at least one of the vapor compression refrigeration system and the Stirling refrigeration system is cooling the cryogenic compartment to circulate air within the cryogenic compartment to increase refrigeration efficiency.

The cooling fan 234 may be disposed downstream of the heat exchanger 100 to reduce wind resistance and further improve cooling and heating efficiency.

The refrigeration and freezer 200 may also include an air duct cover 235 disposed within the cryogenically cooled liner 216 and forming a compartment air duct with the cryogenically cooled compartment, i.e., the rear wall of the cryogenically cooled liner 216. The cooling fan 234 and at least a portion of the heat exchanger 100 may be disposed in the compartment air duct, and the air duct cover 235 may be provided with at least one air supply opening 2351 and a return air opening 2352 disposed below the at least one air supply opening 2351 to improve temperature uniformity of the cryogenic compartment.

Fig. 10 is a schematic rear view of the refrigeration and freezer 200 of fig. 9 with the device chamber first cold plate 218 removed. Referring to fig. 10, the rear bottom of the outer box 211 may further define a device chamber 217. In particular, the Stirling refrigerator 220 may be disposed within the device chamber 217 to facilitate installation and maintenance of the Stirling refrigerator 220 and to improve stability of the Stirling refrigerator 220, and to prevent resonance problems caused by transmission of vibrations generated by the Stirling refrigerator 220 to the case to some extent.

In some embodiments, the refrigerator-freezer 200 can also include a bottom steel fixedly attached to the outer box 211. A bottom steel may be provided at the bottom of the device chamber 217 for supporting the stirling cooler 220.

In some embodiments, the cold end of Stirling cooler 220 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 231 and condenser tube may also be disposed within the device chamber 217 to provide a compact structure, a larger storage space for the tank, and facilitate installation and maintenance and layout of the compressor 231, condenser tube, and Stirling refrigerator 220, reducing production costs.

A heat dissipation blower may also be disposed within the device chamber 217. The heat rejection fan may be configured to induce airflow from the condenser tube through the compressor 231 to the main body 221 of the Stirling refrigerator 220 to improve the heat rejection efficiency of the Stirling refrigeration system and the vapor compression refrigeration system as a whole, further reducing energy consumption, improving refrigeration efficiency, and avoiding the problem of potential safety hazards due to overheating.

The heat dissipation fan can be arranged between the condensing tube and the compressor 231 to reduce wind resistance, improve air quantity and further improve heat dissipation efficiency.

The controller may also be disposed within the device chamber 217 downstream of the body 221 of the Stirling cooler 220 to facilitate electrical connection of the controller to the Stirling cooler 220 and the compressor 231.

Fig. 11 is a schematic rear view of the refrigeration and freezer 200 of fig. 10, with one of the half shells 271, one of the resilient feet 290, and the insulating cover 240 removed; fig. 12 is a schematic partial enlarged view of the region C in fig. 11. Referring to fig. 10 to 12, the refrigerating and freezing apparatus 200 may further include a heat-retaining cover 240. The heat preservation cover 240 may be configured to separate the cold end and the hot end of the stirling cooler 220 from the inner side and the outer side thereof, so as to avoid the heat interference of the hot end and the cold end, and most or all of the cold energy generated by the cold end is transmitted to the cryogenic compartment, thereby improving the refrigeration efficiency of the stirling cooler 220.

In some embodiments, the refrigeration and freezing apparatus 200 may further include a housing 270, which is disposed on the outer side of the main body 221 of the stirling cooler 220, to prevent the heat generated by the compressor 231 from affecting the working efficiency of the stirling cooler 220, and to shield the vibration noise generated by the stirling cooler 220, thereby reducing the noise transferred to the surrounding environment and improving the user experience.

The enclosure 270 may be comprised of two half shells 271 that are mirror symmetrical about a longitudinal central plane of symmetry of the Stirling cooler 220. I.e., the two halves 271 of the enclosure 270 may be mirror symmetric about a plane coplanar with the direction of piston movement of the Stirling cooler 220 to facilitate assembly of the Stirling cooler 220 with the enclosure 270 and extraction of the cold and hot ends of the Stirling cooler 220.

The refrigeration and freezer 200 can also include a plurality of spring suspensions 272 uniformly distributed in the circumferential direction of the Stirling cooler 220. Each spring hanger 272 may be fixedly coupled with the housing 270 and the stirling cooler 220 to suspend the stirling cooler 220 within the housing 270 to reduce or even eliminate vibration of the stirling cooler 220 in various directions while stabilizing the installation of the stirling cooler 220, thereby preventing the vibration generated by the stirling cooler 220 from being amplified through the cold and heat conductive tube 252.

Each spring suspension 272 may include a first mounting plate fixedly connected to the housing of the stirling cooler 220, a second mounting plate fixedly connected to the casing 270, and two tension springs having both ends fixedly connected to the first and second mounting plates, respectively, and extending lines of the tension directions intersecting at a side of the first mounting plate remote from the second mounting plate.

The cover 270 may be provided with a plurality of recesses recessed toward the inside thereof. The plurality of spring suspension devices 272 may be disposed to be fixedly connected with bottom walls of the plurality of recesses, respectively, to improve structural strength of the housing 270, reduce thickness of the housing 270, and save production cost of the housing 270.

Fig. 13 is a schematic exploded view of the cold guide 250 of fig. 12. Referring to fig. 12 and 13, the cold end adapter may be provided with at least one tube aperture. One end of at least one cold-conducting tube 252 may be disposed in at least one tube bore and thermally coupled to the cold-end adapter to receive cold from the cold end and transfer the cold to the heat exchanger 100.

In the embodiment shown in fig. 13, the number of the cold/heat conducting pipes 252 may be plural. The cold end adapter may include two mounts 251a and one lock 251b.

The two mounts 251a may be disposed to be mirror symmetrical about a longitudinal center plane (i.e., an axial center plane) of the cold end with the cold end sandwiched therebetween to be thermally connected with the cold end.

The two mounts 251a may be respectively formed with at least one pipe groove 253. The locking member 251b may be formed with a plurality of pipe grooves 253 and is combined with the pipe grooves 253 of the two mounting members 251a in the longitudinal direction of the cold and heat conductive pipes 252 to form a plurality of pipe holes to be thermally connected with the plurality of cold and heat conductive pipes 252, so as to improve the reliability of the cold end adapter and facilitate the assembly of the cold end adapter with the cold and heat conductive pipes 252.

In some embodiments, each cold-conducting tube 252 may include a plurality of bent portions 254, and the bending angle of at least one bent portion 254 is greater than or equal to 90 ° and less than 180 °, so as to reduce the vibration transmitted from the Stirling refrigerator 220 to the heat exchanger 100, thereby avoiding the problem of echo amplification noise generated when the vibration is transmitted to the cryogenic compartment, and improving the connection reliability of the heat exchanger 100 and the cold-conducting tube 252.

The number of the bent portions 254 of each heat pipe 252 may be 2 to 5, for example, 2, 3,4, or 5, to reduce the difficulty of production while securing the vibration reduction effect.

In some further embodiments, each cold-conducting tube 252 may have at least one bend 254 having a bend angle of 150 ° or more and less than 240 °, for example 150 °, 163 °, 176 °, 191 °, 230 °, or 250 °, to further reduce vibration.

For a further understanding of the present invention, preferred embodiments of the invention are described below in connection with more specific examples, but the invention is not limited to these examples.

Example 1

Fig. 14 is a schematic side view of a heat pipe for cooling according to embodiment 1 of the present invention. Referring to fig. 14, the maximum bending angles of the four heat conductive pipes are 163 °, 176 °, 191 ° and 230 °, respectively.

Example 2

Fig. 17 is a schematic side view of a heat pipe for cooling according to embodiment 2 of the present invention. Referring to fig. 17, the bending angles of the maximum bending portions of the four heat pipes are all 90 °.

Comparative example 1

Fig. 20 is a schematic side view of the heat pipe of comparative example 1 of the present invention. Referring to fig. 20, the bending angles of the maximum bending portions of the four heat pipes are 80 °, 75 °, 70 °, 65 °, respectively.

The diameters of the heat pipes and the relative positions of the both side ends were the same in examples 1-2 and comparative example 1.

Performance tests were performed on examples 1-2 and comparative example 1. Test description: and reserving and fixing the connection structure (namely the cold end adapter, the second cold guide plate and the locking piece) of the heat-conducting pipe, the Stirling refrigerator and the heat exchanger, applying a forced displacement of 10 micrometers (mum) to the connection structure for connecting the heat-conducting pipe with the Stirling refrigerator, and measuring the maximum stress and the maximum acceleration of the heat-conducting pipe under the forced displacement of different frequencies. Wherein, the connection structures used in the test are the same.

FIG. 15 is a stress test chart of example 1, wherein the abscissa is frequency (in Hz) and the ordinate is maximum stress (in MPa); FIG. 18 is a stress test chart of example 2, wherein the abscissa is frequency (in Hz) and the ordinate is maximum stress (in MPa); fig. 21 is a stress test chart of comparative example 1, in which the abscissa is frequency (in Hz) and the ordinate is maximum stress (in MPa). Referring to fig. 15, 18 and 21, in the case where the diameters of the heat pipe and the straight line distances of both side ends are the same, the maximum stresses to which the heat pipes of example 1 and example 2 are subjected at respective frequencies are far smaller than those of the heat pipe of comparative example 3 under the same test conditions. That is, in practical use, the stress applied to the heat exchanger by the heat-conductive pipes of examples 1 and 2 is much smaller than that applied to the heat exchanger by the heat-conductive pipe of comparative example 3, so that the connection of the heat-conductive pipe and the heat exchanger is more reliable.

FIG. 16 is an acceleration test chart of example 1, in which the abscissa is frequency (in Hz) and the ordinate is acceleration (in mm/s ²); FIG. 19 is an acceleration test chart of example 2, in which the abscissa is frequency (in Hz) and the ordinate is acceleration (in mm/s ²). Referring to fig. 16 and 19, in the case where the diameter of the heat pipe and the relative positions of both side ends are the same, the maximum acceleration of the heat pipe of example 1 is slightly smaller than that of example 2 under the same test conditions. That is, the vibration intensity of the heat pipe of example 1 is slightly smaller than that of the heat pipe of example 2, and the vibration noise is small in practical use.

In addition, the heat transfer pipes of examples 1 to 2 were subjected to natural frequency test, and the first three-stage natural frequencies of the heat transfer pipes of example 1 were 36HZ, 149HZ and 205HZ, respectively, and the first three-stage natural frequencies of the heat transfer pipes of example 2 were 36HZ, 49HZ and 78HZ, respectively. The cold and hot conducting tube of example 1 is more suitable for a typical 50-90 Hz stirling cooler and has a lower probability of resonating with the typical stirling cooler.

Fig. 22 is a schematic cross-sectional view of the resilient pad 290 of fig. 12. Referring to fig. 12 and 22, in some embodiments, the bottom of the housing 270 may be provided with a plurality of feet 273. The refrigeration and freezer 200 can also include a plurality of resilient pads 290 disposed between the plurality of feet 273 and the mounting surface of the mounting enclosure 270, respectively, to further reduce vibration of the Stirling cooler 220.

In particular, the mounting surface may be provided with a plurality of mounting posts 219 extending upwardly and being annular in cross section. Each of the elastic casters 290 may be provided with a mounting hole 291 penetrating the elastic caster 290 in a vertical direction, and a mounting groove 292 extending in a circumferential direction thereof and opening outward. Wherein, the inner peripheral wall of the mounting column 219 can be used to cooperate with the fastener, the mounting hole 291 can be sleeved on the mounting column 219, and the stand-offs 273 are clamped in the mounting groove 292 to reduce the vibration of the Stirling refrigerator 220 in the vertical direction and reduce the vibration of a certain Stirling refrigerator 220 in the horizontal direction, thereby preventing the vibration generated by the Stirling refrigerator 220 from being amplified by the cold-heat conducting tube 252.

In the embodiment of fig. 12, each half shell 271 is provided with one leg 273, and each leg 273 is configured to snap into the mounting groove 292 of two resilient pads 290.

The outer diameter of the portion of each of the elastic casters 290 located at the lower side of the mounting groove 292 may be larger than the outer diameter of the portion located at the upper side of the mounting groove 292 to save production costs and improve reliability of the elastic casters 290.

Each elastic cushion 290 may further be provided with two buffer grooves 293 which are mutually communicated with the mounting hole 291 and are respectively located at the inner side and the lower side of the mounting groove 292, so that the elasticity of the elastic cushion 290 is improved by using the air chamber formed by the two buffer grooves 293 and the mounting column 219, and further the vibration reduction effect is improved, and the service life of the elastic cushion 290 is prolonged.

The housing 270 may be made of metal to improve the shielding effect of the housing 270. In some embodiments, the housing 270 may be made of steel. The thickness of the cover 270 may be 2 to 5mm, for example, 2mm, 3mm, 4mm, or 5mm, to reduce the size of the mounting groove 292 and thus improve the elasticity of the elastic pad 290.

By now 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 herein in detail, many other variations or modifications of the invention consistent with the principles of the invention may be directly ascertained or inferred from the present disclosure without departing from the spirit and scope of the invention. Accordingly, the scope of the present invention should be understood and deemed to cover all such other variations or modifications.

Claims

1. A refrigeration and freezer comprising:

a box defining a cryogenic compartment;

A heat exchanger at least partially disposed within the cryogenic compartment;

a vapor compression refrigeration system comprising an evaporator tube disposed within said cryogenic compartment and said evaporator tube being configured to be thermally coupled to said heat exchanger;

The Stirling refrigerating system comprises a Stirling refrigerator, and the cold end of the Stirling refrigerator is thermally connected with the heat exchanger; and

The cold-conducting device comprises a cold end adapter and a plurality of cold-conducting heat pipes which are thermally connected with the cold end; wherein,

The heat exchanger includes:

The second cold guide plate is provided with a heat pipe connecting structure and is in thermal connection with the plurality of cold guide heat pipes; wherein the second cold guide plate is integrally formed with the middle region of the first cold guide plate or is directly connected with the first cold guide plate in a thermal manner; and is also provided with

The cold end adapter includes:

2. The refrigeration and freezer of claim 1, further comprising:

3. The refrigeration and freezer of claim 2, wherein the cabinet comprises:

An outer case;

4. The refrigeration and freezer of claim 1, further comprising:

5. The refrigeration and chiller of claim 1, wherein the first cold guide plate comprises:

the base plate is provided with the refrigerant pipe connecting structure; and

6. The refrigeration and freezer of claim 1, further comprising:

7. A refrigerating and freezing apparatus as recited in claim 6, wherein,

The refrigerating fan is arranged at the downstream of the heat exchanger; and/or

8. A refrigerating and freezing apparatus according to claim 1, wherein,

The box body is also limited with a common cooling chamber; and the vapor compression refrigeration system further comprises:

a compressor, a condenser tube and a throttling element;