CN111059799A - Heat exchanger and refrigerating and freezing device with same - Google Patents

Abstract

The invention provides a heat exchanger and a refrigerating and freezing device with the same. The heat exchanger includes a first cold conductive plate and a second cold conductive plate. The first cold guide plate is provided with a refrigerant pipe connecting structure. The second cold conducting plate is arranged to be in thermal connection with the first cold conducting plate and is provided with a heat pipe connecting structure. The refrigerating and freezing device comprises a box body which limits a deep cooling chamber, a vapor compression refrigerating system, a Stirling refrigerating system and the heat exchanger. The first cold guide plate of the heat exchanger is arranged in the deep cooling chamber, and the evaporation tube of the vapor compression refrigeration system and the cold guide heat tube of the Stirling refrigeration system are respectively in thermal connection with the heat exchanger through a refrigerant tube connection structure and a heat tube connection structure. The cold storage and refrigeration device of the invention thermally connects the refrigerant pipe of the vapor compression refrigeration system and the cold conduction heat pipe of the Stirling refrigeration system with the heat exchanger, thereby not only having high refrigeration efficiency, but also realizing wide temperature change of the cryogenic compartment and flexibly meeting the use requirements of different users.

Description

Heat exchanger and refrigerating and freezing device with same

Technical Field

The present invention relates to the field of refrigeration, and more particularly, to a heat exchanger and a refrigerating and freezing apparatus having the same.

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, the system can realize the refrigerating temperature below 200 ℃ below zero, but the cold end area of the Stirling refrigerator is small, and the refrigerating efficiency is low.

Disclosure of Invention

It is an object of the first aspect of the present invention to provide a heat exchanger capable of receiving heat (or cold) from a refrigerant pipe and a heat pipe.

A further object of the first aspect of the invention is to make the heat exchanger compact.

It is an object of the second aspect of the present invention to provide a refrigerating and freezing apparatus having the heat exchanger.

It is a further object of the second aspect of the present invention to facilitate the assembly of the cold conduction heat pipe with the heat exchanger.

According to a first aspect of the present invention, there is provided a heat exchanger, characterized by comprising:

the first cold conducting plate is provided with a refrigerant pipe connecting structure and is used for being thermally connected with a refrigerant pipe; and

the second cold conducting plate is arranged to be in thermal connection with the first cold conducting plate, and is provided with a heat pipe connecting structure for being in thermal connection with a heat pipe.

Optionally, the heat exchanger further comprises:

the back plate is arranged on one side of the first cold conduction plate close to the second cold conduction plate; wherein

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

The back plate is provided with at least one refrigerant pipe groove, and the refrigerant pipe groove and the at least one refrigerant pipe groove of the first cold guide plate are spliced along the longitudinal direction of the refrigerant pipe and clamp the refrigerant pipe therebetween.

Optionally, the second cold conduction plate is arranged to be integrally manufactured with the first cold conduction plate or directly thermally connected with the first cold conduction plate; and is

The backboard is provided with an avoiding hole, and the second cold guide plate is arranged to penetrate through the avoiding hole and enable the heat pipe connecting structure to be located on one side of the backboard, which is far away from the first cold guide plate.

Optionally, the backing plate is configured to thermally couple to the first cold conductive plate; and is

The second cold conducting plate is arranged on one side, far away from the first cold conducting plate, of the back plate and is in thermal connection with the back plate.

Optionally, the heat exchanger further comprises:

the locking piece is arranged on one side of the second cold conduction plate, which is far away from the first cold conduction plate; wherein

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

The locking piece is provided with at least one heat pipe groove, and the heat pipe groove and the at least one heat pipe groove of the second cold conduction plate are spliced along the longitudinal direction of the heat pipe and clamp the heat pipe therebetween.

Optionally, the first cold guide plate comprises:

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

the fins are arranged at intervals and extend from the base plate to the direction far away from the second cold conducting plate; wherein

The base plate is provided with at least one heating groove with an opening back to the second cold conduction plate, and the heating groove is used for being thermally connected with the electric heating pipe.

According to a second aspect of the present invention, there is provided a refrigeration and freezing apparatus, comprising:

a tank defining a cryogenic compartment;

the vapor compression refrigeration system comprises a refrigerant pipe arranged in the deep cooling chamber;

the Stirling refrigeration system comprises a Stirling refrigerator and at least one cold guide heat pipe thermally connected with the cold end of the Stirling refrigerator; and

according to the heat exchanger, the first cold guide plate is arranged in the deep cooling chamber, the refrigerant pipe is arranged to be in thermal connection with the first cold guide plate through the refrigerant pipe connecting structure, and the at least one cold guide heat pipe is arranged to be in thermal connection with the second cold guide plate through the heat pipe connecting structure; wherein the one refrigerant pipe is an evaporation pipe.

Optionally, the box includes:

the deep cooling inner container is limited with the deep cooling chamber and is provided with a plurality of clamping jaws; wherein

The refrigerant pipe is clamped and fixed on the plurality of clamping jaws and enables the second cold conducting plate to be in thermal connection with the at least one cold conducting pipe; or

The second cold guide plate is fixed on the deep cooling inner container, and the refrigerant pipe is clamped on the plurality of clamping jaws and enables the back plate to be thermally connected with the second cold guide plate.

Optionally, the box includes:

an outer box;

the deep cooling inner container is limited with the deep cooling chamber and is provided with an installation opening; and

the heat insulation layer is arranged between the outer box and the deep cooling inner container; wherein

The part of the at least one cold conduction heat pipe close to the second cold conduction plate and the locking piece are preset in the heat insulation layer; and is

The second cold conduction plate is arranged to penetrate through the mounting opening and is in thermal connection with the at least one cold conduction heat pipe.

Optionally, the refrigeration and freezing apparatus further comprises:

and the cover cap is arranged on the outer side of the copious cooling inner container and covers the part, close to the second cold guide plate, of the at least one cold guide pipe and the locking piece.

The first cold guide plate and the second cold guide plate of the heat exchanger are respectively provided with the refrigerant pipe connecting structure and the heat pipe connecting 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 is improved, and a compartment provided with the heat exchanger has a larger temperature adjusting range.

Furthermore, the refrigerant pipe is clamped between the first cold conduction plate and the back plate, and the first cold conduction plate is provided with at least one heating pipe groove with an opening back to the second cold conduction plate to be thermally connected with the electric heating pipe, so that the long-term frosting of the heat exchanger is avoided, the refrigeration efficiency is reduced, the heat exchanger is compact in structure and convenient to assemble, and the production cost is reduced.

Furthermore, the cold storage and refrigeration device of the invention thermally connects the refrigerant pipe of the vapor compression refrigeration system and the cold conduction heat pipe of the Stirling refrigeration system with the heat exchanger, thereby not only having high refrigeration efficiency, but also realizing wide temperature change of the cryogenic compartment at +8 to-80 ℃, flexibly meeting the use requirements of different users and having high applicability.

Furthermore, the part of the cold guide heat pipe close to the second cold guide plate and the locking piece are preset in the foaming layer, the plurality of clamping claws are arranged in the deep cooling liner, and the refrigerant pipe is clamped and fixed on the clamping claws, so that the second cold guide plate is in thermal connection with the cold guide heat pipe or the back plate is in thermal connection with the cold guide heat pipe, the installation and the connection are reliable, the assembly is simple and convenient, the production efficiency is improved, and the production cost is reduced.

Furthermore, the cold guide heat pipe is arranged to comprise a plurality of bending parts, and the bending angle of at least one bending part is larger than or equal to 90 degrees and smaller than 180 degrees, so that the vibration transmitted to the heat exchanger by the Stirling refrigerator is effectively reduced, the problem of echo amplification noise generated when the vibration is transmitted to the deep cooling chamber is solved, the connection reliability of the heat exchanger and the cold guide heat pipe is improved, and the user experience is improved.

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 invention will be described in detail hereinafter, by way of illustration and not 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:

FIG. 1 is a schematic side view of a heat exchanger according to one embodiment of the present 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 region A in FIG. 3;

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

figure 6 is a schematic cross-sectional view of a refrigeration freezer apparatus 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 refrigeration chiller employing the heat exchanger of FIG. 5;

FIG. 9 is a schematic partial rear elevational view of the refrigeration freezer shown in FIG. 6;

fig. 10 is a schematic rear view of the refrigeration chiller of fig. 9 with the appliance compartment first cold conduction plate removed;

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

FIG. 12 is a schematic partial enlarged view of region C of 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 cold conduction heat pipe according to embodiment 1 of the present invention;

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

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

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

FIG. 18 is a stress test chart of example 2, in which 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 cold-conducting heat pipe of 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 footpad of fig. 12.

Detailed Description

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

The first cold conducting plate 120 may be provided with a refrigerant pipe connection structure for thermally connecting with a refrigerant pipe to receive cold or heat of the refrigerant pipe. The refrigerant pipe may 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 conductive plate 130 may be configured to be thermally connected to the first cold conductive plate 120, and may be configured with a heat pipe connection structure for thermally connecting to a 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 or hot source, such as a cold or hot side of the stirling cooler 220, a cold or hot side of the semiconductor cooler.

The first cold conduction plate 120 and the second cold conduction plate 130 of the heat exchanger 100 of the invention are respectively provided with a refrigerant pipe connection structure and a heat pipe connection structure, and can selectively exchange heat with a refrigerant pipe and/or a heat pipe, so that the flexibility of the refrigeration and heating modes of the heat exchanger 100 is improved, and the compartment provided with the heat exchanger 100 has a larger temperature regulation range.

In some embodiments, the second cold conductive plate 130 may be disposed in thermal communication with a central region of the first cold conductive plate 120 to improve temperature uniformity of the first cold conductive plate 120.

In some embodiments, the heat exchanger 100 may further include a backing plate 110 disposed on a side of the first cold conductive plate 120 proximate to the second cold conductive plate 130.

Fig. 4 is a schematic enlarged view of the region 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 formed with at least one refrigerant pipe groove 115. The at least one refrigerant pipe groove 115 of the first cold conducting plate 120 and the at least one refrigerant pipe groove 115 of the back plate 110 may be configured to be spliced along a longitudinal direction of the refrigerant pipe (i.e., a length direction and an axial direction of the refrigerant pipe), and the refrigerant pipe clamp is disposed therebetween to fix the refrigerant pipe and receive cold or heat of the refrigerant pipe.

The projection of the at least one refrigerant tube slot 115 to the direction close to the second cold conducting plate 130 may be located outside 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 be provided with an avoiding hole 111 in a projection range of the heat pipe connection structure, so as to save cost and further improve the cooling and heating efficiency of the heat exchanger 100 as a whole.

The first cold conducting plate 120 may include a base plate 121 having at least one refrigerant pipe slot 115 and a plurality of cold conducting fins 122 disposed at intervals and extending from the base plate 121 to a direction away from the second cold conducting plate 130, so as to increase a heat exchanging area of the first cold conducting plate 120, and further improve a cooling and heating efficiency of the heat exchanger 100.

The first cold conduction plate 120 may further be formed with at least one heating groove 113 with an opening facing away from the second cold conduction plate 130 for thermal connection with the electric heating pipe 280, so as to prevent the heat exchanger 100 from frosting for a long time and reducing the cooling efficiency. That is, the electric heating tube 280 may be partially embedded in the base plate 121 and partially located in the space between the plurality of cooling guide fins 122.

The heat exchanger 100 may further include a retaining member 140 disposed on a side of the second cold conductive plate 130 remote from the first cold conductive plate 120.

The heat pipe connection structure may include at least one heat pipe groove 135. The locker 140 may be correspondingly formed with at least one heat pipe groove 135. The at least one heat pipe groove 135 of the locker 140 and the at least one heat pipe groove 135 of the second cold conductive plate 130 may be configured to be engaged in a longitudinal direction of the heat pipe (i.e., a length direction, an axial direction of the heat pipe) and sandwich the heat pipe therebetween to fix the heat pipe and receive the cold or heat of the heat pipe.

Heat conductive silicone grease may be disposed in the cooling medium pipe groove 115 and/or the heat pipe groove 135 to improve heat exchange efficiency between the cooling medium pipe and/or the heat pipe and the heat exchanger 100.

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

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

In this embodiment, the second cold conductive plate 130 may be disposed through the escape aperture 111 and have the heat pipe connection structure located on a side of the back plate 110 away from the first cold conductive plate 120.

The invention also provides a refrigerating and freezing device 200 based on the heat exchanger 100 of any one of the above embodiments. Fig. 6 is a schematic cross-sectional view of a refrigerated freezer 200 according to one embodiment of the invention; FIG. 7 is a schematic enlarged view of region B in FIG. 6; fig. 9 is a schematic partial rear view of the refrigeration freezer 200 shown in 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, 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 for controlling operations of the vapor compression refrigerating system and the stirling refrigerating system. The refrigerating and freezing device 200 may be a refrigerator, a freezer, or the like.

The box body may include an outer box 211, at least one inner container disposed in the outer box 211, and a heat insulation layer 212 disposed between the outer box 211 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 213, a normal cold bladder 214, a normal cold bladder 215, and a cryogenic bladder 216. The vapor compression refrigeration system may be configured to provide refrigeration to the common cold chamber defined by common cold bladder 213, common cold bladder 214, and common cold bladder 215, and the cryogenic chamber defined by cryogenic bladder 216, and the stirling refrigeration system may be configured to provide refrigeration only to the cryogenic chamber defined by cryogenic bladder 216.

Specifically, the vapor compression refrigeration system may include a compressor 231, a condenser tube 232, at least one throttling element, and a plurality of evaporator tubes 233. Wherein, a plurality of evaporation tubes 233 can be respectively arranged in the normal cold inner container 213, the normal cold inner container 214 and the deep cold inner container 216. The normal cold liner 215 can be communicated with the normal cold liner 214 through an air duct.

The stirling refrigeration system may include at least one stirling cooler 220, at least one cold conduction device 250 thermally coupled to the cold end of the at least one stirling cooler 220, respectively, and at least one heat sink 260 thermally coupled to the hot end of the at least one stirling cooler 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 that drives the piston in motion. The housing may be composed of a main body 221 and a cylindrical portion 222. The driving mechanism may be disposed within the main body 221. The piston may be arranged to reciprocate within the cylindrical portion 222 to form a cold end and a hot end.

The cold-directing device 250 may include a cold-end adapter thermally coupled to the cold end of the stirling cooler 220 and at least one cold-directing heat pipe 252 thermally coupled to the cold-end adapter.

One evaporation tube 233 may be configured to be thermally coupled to the first cold conduction plate 120 via a refrigerant tube coupling structure. At least one cold conduction heat pipe 252 may be disposed in thermal communication with the second cold conduction plate 130 through a heat pipe connection structure. The first cold conducting plate 120 can be arranged in the deep cooling inner container 216 to improve the efficiency of the evaporation tube 233 and the cold conducting heat tube 252 for refrigerating the deep cooling compartment, so that the wide temperature change of the deep cooling compartment at +8 to-80 ℃ is realized, and the use requirements of different users are flexibly met.

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

Cryogenic inner bladder 216 may be provided with a plurality of dogs 282. The evaporation pipe 233 may be fastened to the plurality of claws 282 to fix the heat exchanger 100.

The portion of the at least one cold conduction heat pipe 252 close to the second cold conduction plate 130 and the locking member 140 may be disposed in the insulation layer 212. Cryogenic inner tank 216 may be provided with mounting openings. The second cold conduction plate 130 may be disposed through the mounting opening and thermally coupled to the cold conduction heat pipe 252.

In an embodiment where the first cold conductive plate 120 and the second cold conductive plate 130 are independent from each other, the second cold conductive plate 130 may be disposed to be fixedly connected to the periphery of the installation opening and thermally connected to the cold conductive heat pipe 252. That is, the locking member 140 and the cold conducting heat pipe 252 may be assembled with the second cold conducting plate 130 first, and then foamed between the deep cooling inner container 216 and the outer container 211 to form the heat insulating layer 212, so as to simplify the production process and improve the production efficiency.

The back plate 110 can be thermally connected to the second cold conduction plate 130 when the evaporation tubes 233 are fastened to the plurality of claws 282, so that the installation and connection are reliable, and the production efficiency is further improved.

Fig. 8 is a schematic partial view of a refrigeration freezer 200 employing the heat exchanger 100 shown in fig. 5. Referring to fig. 8, in the embodiment where the first cold conductive plate 120 and the second cold conductive plate 130 are integrally formed or directly thermally connected, the assembly may be completed by a similar component to the second cold conductive plate 130 of the previous embodiment, the locking member 140 and the cold conductive pipe 252, and then the insulation layer 212 may be formed by foaming between the cryogenic inner container 216 and the outer container 211. And the part is removed after foaming is complete.

The second cold conduction plate 130 can be thermally connected to the cold conduction heat pipe 252 when the evaporation tube 233 is fastened to the plurality of claws 282, so as to reduce thermal resistance, ensure reliable installation and connection, and further improve production efficiency.

The refrigeration freezer 200 may also include a cover 284 disposed outside the cryogenic inner container 216. The cover 284 may cover a portion of the at least one cold conducting pipe 252 close to the second cold conducting plate 130 and the locking member 140 therein, so as to make the foaming more uniform and improve the heat insulation performance of the insulation layer 212.

The cover 284 may be provided with at least one through hole. Retaining member 140 may be fixedly attached to second cold conductive plate 130 or a similar component of second cold conductive plate 130, and cover 284 may be provided with retaining member 140 and fixedly attached to cryogenic inner bladder 216. At least one cold-conducting heat pipe 252 may be inserted into the heat pipe connection structure via at least one through hole of the cover 284.

The refrigeration chiller 200 may also include an electrical heating tube 280 for defrosting the heat exchanger 100. The number of the heating pipe grooves 113 may be plural, and the electric heating pipe 280 may be disposed in a serpentine shape between the plurality of cooling guide fins 122 and thermally connected to the first cooling guide plate 120 to increase a heat exchange area of the electric heating pipe 280.

Fig. 10 is a schematic rear view of the refrigeration freezer 200 of fig. 9 with the device compartment first cold conductive plate 218 removed. Referring to fig. 10, the rear bottom of the outer case 211 may further define a device chamber 217. In particular, the Stirling refrigerator 220 may be disposed in the device chamber 217 to facilitate installation and maintenance of the Stirling refrigerator 220 and to improve stability of the Stirling refrigerator 220, to the extent that vibration generated from the Stirling refrigerator 220 is prevented from being transmitted to the case to cause a resonance problem.

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

In some embodiments, the cold end of the Stirling cooler 220 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 231 and the condenser may also be disposed in the device chamber 217, so that the structure is compact, the box body has a large storage space, installation, maintenance and circuit layout of the compressor 231, the condenser and the stirling cooler 220 are facilitated, and the production cost is reduced.

A heat dissipation fan may also be disposed in the device chamber 217. The heat dissipation fan may be configured to force airflow from the condenser to flow to the body 221 of the stirling cooler 220 via the compressor 231, so as to improve the heat dissipation efficiency of the stirling cooling system and the vapor compression cooling system as a whole, further reduce energy consumption, improve cooling efficiency, and avoid the problem of potential safety hazard due to overheating.

The heat dissipation fan may be disposed between the condenser and the compressor 231 to reduce wind resistance, increase air volume, and further increase heat dissipation efficiency.

The controller may also be disposed within the device chamber 217 and 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-freezing apparatus 200 shown in fig. 10, with one half-shell 271, one resilient foot 290, and the heat-retaining cover 240 removed; fig. 12 is a schematic partial enlarged view of region C in fig. 11. Referring to fig. 10 to 12, the refrigerating and freezing device 200 may further include a heat-retaining cover 240. The heat-insulating cover 240 may be configured to separate the cold end and the hot end of the stirling cooler 220 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 transmit most or even all of the cold energy generated by the cold end to the cryogenic compartment, thereby improving the cooling efficiency of the stirling cooler 220.

In some embodiments, the refrigerating and freezing device 200 may further include a cover 270 covering the outer side of the main body 221 of the stirling cooler 220, so as to prevent heat generated by the compressor 231 from affecting the operating efficiency of the stirling cooler 220, and to shield vibration noise generated by the stirling cooler 220, thereby reducing noise transmitted to the surrounding environment and improving user experience.

The enclosure 270 may be comprised of two half-shells 271 that are mirror-symmetric about a longitudinal central plane of symmetry of the stirling cooler 220. That is, the two half-shells 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 refrigerator-freezer 200 may further include a plurality of spring suspensions 272 uniformly distributed in the circumferential direction of the stirling cooler 220. Each spring suspension 272 may be fixedly connected to the enclosure 270 and the stirling cooler 220 to suspend the stirling cooler 220 within the enclosure 270 to reduce or even eliminate vibration of the stirling cooler 220 in all directions while stabilizing and securing the installation of the stirling cooler 220, thereby preventing the vibration generated by the stirling cooler 220 from being amplified by the cold conducting heat pipe 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 housing 270, and two tension springs having two ends respectively fixedly connected to the first mounting plate and the second mounting plate, and extending lines in the tension direction intersecting with one side of the first mounting plate away 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 hangers 272 may be fixedly connected to the bottom walls of the plurality of recesses, respectively, to improve the structural strength of the housing 270, reduce the thickness of the housing 270, and save the production cost of the housing 270.

Fig. 13 is a schematic exploded view of the cold conductor 250 of fig. 12. Referring to fig. 12 and 13, the cold end adapter may be formed with at least one tube bore. One end of at least one cold-conducting heat pipe 252 may be configured to thermally couple to an adapter of heat exchanger 100 and the other end may be configured to be disposed within at least one bore and thermally couple to a cold-side adapter, respectively, to receive cold from the cold side and transfer the cold to heat exchanger 100.

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

The two mounts 251a may be arranged mirror-symmetrically about a longitudinal central plane (i.e. an axial central plane) of the cold ends and sandwich the cold ends therebetween for thermal connection therewith.

The two mounting members 251a may be respectively formed with at least one tube groove 253. The locking member 251b may be formed with a plurality of pipe grooves 253 and may be spliced with the pipe grooves 253 of the two mounting members 251a to form a plurality of pipe holes along the longitudinal direction of the cold-conducting heat pipe 252 to be thermally connected with the plurality of cold-conducting heat 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-conducting heat pipe 252.

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

The number of the bent portions 254 of each cold conduction heat pipe 252 can be 2-5, for example, 2, 3, 4, or 5, so that the production difficulty is reduced while the vibration reduction effect is ensured.

In some further embodiments, each cold-guiding heat pipe 252 may have at least one bending portion 254 with a bending angle greater than or equal to 150 ° 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 present invention are described below with reference to more specific examples, but the present invention is not limited to these examples.

Example 1

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

Example 2

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

Comparative example 1

Fig. 20 is a schematic side view of a cold conduction 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 cold guide heat pipes are respectively 80 °, 75 °, 70 ° and 65 °.

The diameters and the relative positions of the end parts at both sides of the cold conduction heat pipes in the above examples 1-2 and comparative example 1 were the same.

The examples 1-2 and comparative example 1 were subjected to performance tests. Description of the test: and (3) retaining and fixing the connecting structure of the cold guide heat pipe, the Stirling refrigerator and the heat exchanger (namely the cold end adapter, the second cold guide plate and the locking piece), applying a forced displacement of 10 micrometers (mum) to the connecting structure for connecting the Stirling refrigerator, and measuring the maximum stress and the maximum acceleration of the cold guide heat 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, in which the abscissa is frequency (in Hz) and the ordinate is maximum stress (in MPa); FIG. 18 is a stress test chart of example 2, in which 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, under the same test conditions, the maximum stress of the cold conduction heat pipes of examples 1 and 2 at each frequency was much smaller than that of the cold conduction heat pipe of comparative example 3, in the case where the diameter of the cold conduction heat pipe and the linear distance between both side ends were the same. That is, in practical use, the stress applied to the heat exchanger by the cold guide heat pipes of the embodiment 1 and the embodiment 2 is much smaller than the stress applied to the heat exchanger by the cold guide heat pipes of the comparative example 3, so that the connection between the cold guide heat pipes 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) (ii) a 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 cold conduction heat pipe and the relative positions of the both side ends are the same, the maximum acceleration of the cold conduction heat pipe of example 1 is slightly smaller than that of the cold conduction heat pipe of example 2 under the same test conditions. That is, the vibration intensity of the cold-conducting heat pipe of example 1 is slightly smaller than that of the cold-conducting heat pipe of example 2, and the vibration noise is small in practical application.

In addition, the cold-conducting heat pipes of examples 1 to 2 were subjected to natural frequency tests, and the natural frequencies of the first three stages of the cold-conducting heat pipes of example 1 were 36HZ, 149HZ, and 205HZ, respectively, and the natural frequencies of the first three stages of the cold-conducting heat pipes of example 2 were 36HZ, 49HZ, and 78HZ, respectively. The cold guide heat pipe in the embodiment 1 is more suitable for a common Stirling refrigerator with 50-90 Hz, and has lower possibility of generating resonance with the common Stirling refrigerator.

Fig. 22 is a schematic cross-sectional view of the resilient foot 290 of fig. 12. Referring to fig. 12 and 22, in some embodiments, the bottom of the casing 270 may be provided with a plurality of feet 273. The refrigerating and freezing apparatus 200 may further include a plurality of elastic feet 290 respectively disposed between the plurality of feet 273 and the mounting surface of the mounting case 270 to further reduce the 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 legs 290 may be formed with a mounting hole 291 penetrating the elastic leg 290 in a vertical direction and a mounting groove 292 extending in a circumferential direction thereof and opening outward. Wherein, the internal perisporium of erection column 219 can be used for cooperating with the fastener, and erection column 219 can be located to mounting hole 291 cover, and stabilizer blade 273 joint is in mounting groove 292 to reduce stirling refrigerator 220's vibration on the vertical direction, and reduce certain stirling refrigerator 220's vibration on the horizontal direction, and then prevent that the vibration that stirling refrigerator 220 produced from leading cold heat pipe 252 to enlarge.

In the embodiment of fig. 12, each half-shell 271 is provided with one support leg 273, and each support leg 273 is configured to be snapped into the mounting groove 292 of the two elastic support legs 290.

The outer diameter of a portion of each elastic leg 290 located at the lower side of the mounting groove 292 may be greater than that of a portion located at the upper side of the mounting groove 292 to save the manufacturing cost and improve the reliability of the elastic leg 290.

Each elastic pad foot 290 can be further provided with two buffer grooves 293 which are mutually communicated with the mounting hole 291 and are respectively positioned on the inner side and the lower side of the mounting groove 292, so that the elasticity of the elastic pad foot 290 is improved by utilizing the air chambers formed by the two buffer grooves 293 and the mounting column 219, the vibration damping effect is further improved, and the service life of the elastic pad foot 290 is prolonged.

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

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

Claims (10)

1. A heat exchanger, characterized in that, comprising: The first cold-conducting plate is provided with a refrigerant pipe connection structure for thermal connection with the refrigerant pipe; and The second cold-conducting plate is configured to be thermally connected to the first cold-conducting plate, and is provided with a heat pipe connection structure for thermally connecting with the heat pipe. 2. The heat exchanger of claim 1, further comprising: a back plate, arranged on the side of the first cold-conducting plate close to the second cold-conducting plate; wherein The refrigerant pipe connection structure includes at least one refrigerant pipe groove; and The back plate is provided with at least one refrigerant pipe groove, which is combined with at least one refrigerant pipe groove of the first cold-conducting plate along the longitudinal direction of the refrigerant pipe and sandwiches the refrigerant pipe therebetween. 3. The heat exchanger of claim 2, wherein: The second cold-conducting plate is configured to be integrally formed with the first cold-conducting plate or directly thermally connected to the first cold-conducting plate; and The back plate is provided with an escape hole, and the second cold-conducting plate is arranged to pass through the escape hole and the heat pipe connection structure is located on a side of the back plate away from the first cold-conducting plate. 4. The heat exchanger of claim 2, wherein: the backplane is configured to be thermally connected to the first cold conducting plate; and The second cold-conducting plate is disposed on a side of the back plate away from the first cold-conducting plate, and is thermally connected to the back plate. 5. The heat exchanger of claim 1, further comprising: a locking member, disposed on the side of the second cold-conducting plate away from the first cold-conducting plate; wherein the heat pipe connection structure includes at least one heat pipe slot; and The locking member is provided with at least one heat pipe groove, which is combined with at least one heat pipe groove of the second cold-conducting plate along the longitudinal direction of the heat pipe and sandwiches the heat pipe therebetween. 6. The heat exchanger according to claim 1, wherein the first cold conducting plate comprises: a base plate provided with the refrigerant pipe connection structure; and a plurality of fins, arranged at intervals and extending from the base plate in a direction away from the second cold conducting plate; wherein The base plate is provided with at least one heating pipe slot with an opening facing away from the second cold-conducting plate, and is used for thermal connection with the electric heating pipe. 7. A refrigeration and freezing device, characterized in that, comprising: The box is limited to a cryogenic compartment; a vapor compression refrigeration system, comprising a refrigerant pipe arranged in the cryogenic compartment; a Stirling refrigeration system, comprising a Stirling refrigerator and at least one cold-conducting heat pipe thermally connected to a cold end of the Stirling refrigerator; and The heat exchanger according to claim 1, wherein the first cold-conducting plate is arranged in the cryogenic compartment, and the one refrigerant pipe is arranged to be connected to the first cold-conducting plate through the refrigerant pipe connection structure For thermal connection, the at least one cold-conducting heat pipe is configured to be thermally connected to the second cold-conducting plate through the heat pipe connection structure; wherein the one refrigerant pipe is an evaporation pipe. 8. The refrigerating and freezing device according to claim 7, wherein the box body comprises: The cryogenic inner tank defines the cryogenic compartment, and the cryogenic inner tank is provided with a plurality of clamping claws; wherein The heat exchanger is further configured as the heat exchanger according to claim 3, wherein the one refrigerant pipe is fastened to the plurality of claws and makes the second cold-conducting plate and the at least one heat-conducting plate pipe thermal connection; or The heat exchanger is further configured as the heat exchanger according to claim 4, the second cold-conducting plate is fixed on the cryogenic inner tank, and the one refrigerant pipe is fixed on the plurality of claws and The back plate is thermally connected to the second cold conducting plate. 9. The refrigerating and freezing device according to claim 7, wherein the box body comprises: outer box; a cryogenic inner tank defining the cryogenic compartment and having a mounting opening; and an insulating layer, arranged between the outer box and the cryogenic inner tank; wherein The heat exchanger is further configured as a heat exchanger according to claim 5; The portion of the at least one cold-conducting and heat-conducting pipe close to the second cold-conducting plate and the locking member are preset in the heat insulating layer; and The second cold-conducting plate is disposed to pass through the installation opening and is thermally connected with the at least one cold-conducting and heat pipe. 10. The refrigerating and freezing device according to claim 9, characterized in that, further comprising: The cover is arranged on the outer side of the cryogenic inner tank, and covers the part of the at least one cold-conducting heat pipe close to the second cold-conducting plate and the locking member inside.

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