CN218672789U

CN218672789U - Refrigeration device

Info

Publication number: CN218672789U
Application number: CN202222580878.XU
Authority: CN
Inventors: 郑皓宇; 张强; 孙丰磊; 李大伟; 王春青
Original assignee: Qingdao Haier Special Refrigerator Co Ltd; Haier Smart Home Co Ltd
Current assignee: Qingdao Haier Special Refrigerator Co Ltd; Haier Smart Home Co Ltd
Priority date: 2022-09-27
Filing date: 2022-09-27
Publication date: 2023-03-21
Anticipated expiration: 2032-09-27

Abstract

The utility model particularly relates to a refrigeration device, which comprises an inner container and a refrigeration system, wherein the inner container comprises an inner container opening, an inner container rear wall arranged opposite to the inner container opening and an inner container top wall connected to the top of the inner container rear wall; the evaporator is spirally arranged on the outer surface of the inner container from the outlet end of the capillary tube to the lower part, and the outlet end of the evaporator extends downwards to the air inlet end of the compressor. The utility model provides a refrigeration plant has the heat transfer and stabilizes, refrigeration effect is good, the reliable advantage of stable in structure.

Description

Refrigeration device

Technical Field

The utility model relates to a refrigeration technology field, especially refrigeration plant.

Background

At present, the temperature of refrigerating equipment, particularly ultra-low temperature vertical refrigerators, can reach-95 ℃ or even lower after capillary throttling; at such low temperatures, the viscosity of the press oil increases and the flow properties weaken; the press oil is dissolved in the refrigerant, but the dissolved amount is greatly influenced by the temperature of the refrigerant; at the high-temperature high-pressure end of the system, more compressor oil is dissolved in the refrigerant, and the temperature of the refrigerant is reduced after the compressor oil is throttled by the capillary tube, so that the compressor oil is separated out (liquid state); when the temperature of the refrigerant is lower than the flocculation point of the press oil, the press oil is easy to flocculate near the outlet of the capillary tube to block the capillary tube, and the refrigeration cycle is not in operation and cannot be cooled.

Therefore, there is a need to develop a refrigerating apparatus to solve the above problems.

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing a refrigeration plant that the heat transfer is stable, refrigeration effect is good, stable in structure is reliable.

In order to achieve the above object, an embodiment of the present invention provides a refrigeration device, including a liner and a refrigeration system, wherein the liner includes a liner opening, a liner rear wall disposed opposite to the liner opening, and a liner top wall connected to the top of the liner rear wall, the refrigeration system includes a compressor, a condenser, a capillary tube and an evaporator connected by a pipeline, the compressor and the condenser are disposed below the liner, the capillary tube extends from bottom to top to the outer surface of the liner, and the outlet end of the capillary tube is disposed close to the liner top wall;

the evaporator is spirally arranged on the outer surface of the inner container from the outlet end of the capillary tube to the lower part, and the outlet end of the evaporator extends downwards to the air inlet end of the compressor.

As an embodiment of the utility model provides a further improvement, the inner bag still including set up in two inner bag lateral walls of the inner bag back wall left and right sides, wherein, the exit end of capillary set up in on the inner bag lateral wall, the capillary is followed the direction of height of inner bag lateral wall extends the setting.

As a further improvement of an embodiment of the present invention, the horizontal cross section of the evaporator is a U-shaped tubular structure, the U-shaped tubular structure includes a horizontal pipe disposed on the rear wall of the inner container and side pipes disposed on the side walls of the inner container, respectively, wherein an included angle between the horizontal pipe and the side pipes is 87 ° to 89 °.

As a further improvement of an embodiment of the present invention, the evaporator is arranged along the edge extending in the height direction of the inner container side wall and the capillary tube is preset with a gap.

As a further improvement of an embodiment of the present invention, the distance between the capillary tube and the inner container opening is greater than 80mm.

As a further improvement of one embodiment of the present invention, the refrigeration system further comprises a heat regenerator and an air return pipe, wherein the heat regenerator comprises a heat regenerator high temperature pipe and a heat regenerator low temperature pipe which are adjacently arranged, the heat regenerator high temperature pipe is connected between the condenser and the capillary tube, the heat regenerator low temperature pipe is connected between the evaporator and the compressor, the air return pipe is connected between the evaporator and the heat regenerator low temperature pipe,

the compressor, the condenser, the heat regenerator high-temperature tube, the capillary tube, the evaporator, the air return tube and the heat regenerator low-temperature tube are sequentially connected to form a refrigeration loop.

As a further improvement of an embodiment of the present invention, the inner container further includes an inner container bottom wall disposed opposite to the inner container top wall, the heat regenerator is fixed on the outer surface of the inner container bottom wall, the capillary tube is close to the outer side of the heat regenerator and the outer side of the air return pipe are contacted.

As an embodiment of the present invention, the refrigerating system is a single-system refrigerating system, the single-system refrigerating system further includes a dry filter connected between the condenser and the heat regenerator high temperature tube, a dew prevention tube connected between the condenser and the dry filter, the dew prevention tube set up in the inner container opening.

As an embodiment of the utility model provides a further improvement, refrigerating system is dual system refrigerating system, refrigerating system includes first refrigerating system and second refrigerating system, and first refrigerating system and second refrigerating system all include compressor, condenser, regenerator high temperature tube, capillary, evaporimeter, muffler and regenerator cryotube, wherein, first refrigerating system still including connect in condenser and regenerator high temperature tube between the drier-filter, connect in the condenser with prevent dew pipe between the drier-filter, prevent dew pipe set up in the inner bag opening part.

As a further improvement of an embodiment of the present invention, the evaporator of the first refrigeration system is a first coil, the evaporator of the second refrigeration system is a second coil, the first coil and the second coil are arranged in a double-layer interval distribution and independent from each other, wherein, it is adjacent that the distance between the first coil and the second coil is 60mm.

As a further improvement of an embodiment of the present invention, the present invention further includes a condensing fan, the first refrigeration system and the second refrigeration system are single-stage compression systems, the compressor of the first refrigeration system and the compressor of the second refrigeration system are distributed along the first direction interval, and the condenser of the first refrigeration system and the condenser of the second refrigeration system share one of the condensing fans.

Compared with the prior art, the beneficial effects of the utility model reside in that: the utility model provides a refrigeration plant is through setting up compressor and condenser in the below of inner bag, thereby increase the size in holding chamber, the high-usage rate, the capillary extends the setting from bottom to top simultaneously, can let the press oil that the part appeared in the capillary return naturally to the condenser during compressor shut down, avoid press oil near capillary export flocculation, block up the capillary, set up from bottom to top through the capillary, flow direction for going into down in the evaporimeter with the realization refrigerant, the press oil that can effectively avoid the compressor is accumulated in the evaporimeter, be favorable to the keeping of compressor oil return and evaporimeter heat transfer stability, it is stable to have the heat transfer, the refrigeration effect is good, the reliable and stable advantage of structure.

Drawings

Fig. 1 is a schematic structural composition diagram of the refrigeration equipment of the present invention;

fig. 2 is a schematic horizontal cross-sectional view of an evaporator of the refrigeration apparatus of the present invention;

fig. 3 is a system configuration diagram of the refrigeration system of the refrigeration apparatus of the present invention, when the refrigeration system is a single-system refrigeration system;

fig. 4 is a system configuration diagram of an embodiment of the refrigeration system of the refrigeration apparatus of the present invention, when the refrigeration system is a dual-system refrigeration system;

fig. 5 is a schematic structural view of the first coil and the second coil of the refrigeration apparatus of the present invention;

fig. 6 is a layout schematic diagram of a condensing fan of the refrigeration equipment of the present invention;

fig. 7 is a schematic structural diagram of a first embodiment of a first condenser and a second condenser of the refrigeration apparatus of the present invention;

fig. 8 is a schematic structural diagram of a second embodiment of the first condenser and the second condenser of the refrigeration apparatus of the present invention;

fig. 9 is a schematic structural diagram of a third embodiment of the first condenser and the second condenser of the refrigeration apparatus of the present invention;

fig. 10 is a schematic structural view of a condensing fan of the refrigeration equipment of the present invention;

fig. 11 is a system configuration diagram of another embodiment of the refrigeration system of the refrigeration apparatus of the present invention, when the refrigeration system is a dual system refrigeration system.

In the figure: 11. the inner container is opened; 12. the inner container rear wall; 13. a top wall of the inner container; 14. a side wall of the inner container; 15. a bottom wall of the inner container; 21. a compressor; 22. a condenser; 23. a heat regenerator; 231. a regenerator high temperature tube; 232. a regenerator low temperature tube; 24. a capillary tube; 25. an evaporator; 251. a horizontal tube; 252. a side tube; 26. an air return pipe; 27. drying the filter; 28. a dew prevention pipe; 3. a condensing fan; 41. a first compressor; 42. a first condenser; 43. a first heat regenerator; 431. a first recuperator high temperature tube; 432. a first recuperator cryostraw; 44. a first capillary tube; 45. a first evaporator; 46. a first gas return pipe; 47. a first dry filter; 51. a second compressor; 52. a second condenser; 53. a second regenerator; 531. a second regenerator high temperature tube; 532. a second regenerator cryotube; 54. a second capillary tube; 55. a second evaporator; 56. a second muffler; 57. and a second dry filter.

Detailed Description

The following detailed description of the preferred embodiments of the present invention will be provided in conjunction with the accompanying drawings, so as to enable those skilled in the art to more easily understand the advantages and features of the present invention, and thereby define the scope of the invention more clearly and clearly.

The terms "comprising" and "having," as well as any variations thereof, in the present application are intended to cover non-exclusive inclusions. Reference herein to "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment can be included in at least one embodiment of the application. The appearances of the phrase in various places in the specification are not necessarily all referring to the same embodiment, nor are separate or alternative embodiments mutually exclusive of other embodiments. It is explicitly and implicitly understood by one skilled in the art that the embodiments described herein may be combined with other embodiments.

As shown in fig. 1, the present invention mainly relates to: a refrigeration device is explained by taking an ultra-low temperature vertical refrigerator as an example. The refrigeration equipment comprises an inner container and a refrigeration system, wherein the inner container defines a containing cavity, and comprises an inner container opening 11, an inner container rear wall 12 opposite to the inner container opening 11 and an inner container top wall 13 connected to the top of the inner container rear wall 12.

In the present embodiment 1, the refrigeration system includes a compressor 21, a condenser 22, a capillary tube 24, and an evaporator 25 connected by a pipeline, and the refrigerant is led from the compressor 21 to the condenser 22, the capillary tube 24, and the evaporator 25 in this order, and then returned to the compressor 21, thereby forming a refrigeration cycle. The compressor 21 and the condenser 22 are arranged below the inner container, the condenser 22 is arranged on one side of the compressor 21, the capillary tube 24 extends to the outer surface of the inner container from bottom to top, the inlet end of the capillary tube 24 is connected with the outlet end of the condenser 22, the outlet end of the capillary tube 24 is arranged close to the top wall 13 of the inner container, and the flow direction of a refrigerant in the capillary tube 24 is from bottom to top.

The inlet end of the evaporator 25 is connected with the outlet end of the capillary tube 24, the evaporator 25 is spirally arranged on the outer surface of the liner in a downward serpentine manner from the outlet end of the capillary tube 24, the outlet end of the evaporator 25 extends downwards to the air inlet end of the compressor 21, and the capillary tube 24 extends from bottom to top to realize that the refrigerant flows in the evaporator 25 in an upward-in-downward-out manner, so that the accumulation of the compressor oil of the compressor 21 in the evaporator 25 can be effectively avoided, and the oil return of the compressor 21 is facilitated; and secondly, the capillary tube 24 is arranged in a manner of extending from bottom to top, so that part of the press oil separated out in the capillary tube 24 naturally flows back to the condenser 22 during the shutdown of the compressor 21, the press oil is prevented from flocculating and blocking the capillary tube 24 near the outlet of the capillary tube 24, and the refrigeration stability of the refrigeration system is improved.

Further, the inner container also comprises two inner container side walls 14 arranged on the left side and the right side of the inner container rear wall 12, wherein the outlet end of the capillary tube 24 is arranged on the inner container side walls 14, and the capillary tube 24 extends along the height direction of the inner container side walls 14.

Referring to fig. 2, the evaporator 25 is spirally wound on the two liner side walls 14 and the liner rear wall 12, the horizontal section of the evaporator 25 is a U-shaped tubular structure, the U-shaped tubular structure includes a horizontal tube 251 disposed on the liner rear wall 12 and side tubes 252 disposed on the liner side walls 14, so as to effectively ensure the refrigeration effect of the two liner side walls 14 and the liner rear wall 12, and ensure the uniformity of refrigeration in the accommodating chamber. Wherein, the included angle between the horizontal pipe 251 and the side pipe 252 is 87 degrees to 89 degrees, which is matched with the outer surface of the inner container as much as possible.

Further, the edge of the evaporator 25 extending along the height direction of the liner side wall 14 is preset with a distance from the capillary 24, and the capillary 24 is not in contact with the evaporator 25, so that heat exchange between the evaporator and the capillary is avoided.

Further, the distance between the capillary tube 24 and the inner container opening 11 is larger than 80mm, so that heat exchange with the inner container opening 11 is avoided, the temperature of the refrigerant after the capillary tube 24 is throttled is not affected by the ambient temperature, and the refrigeration stability of the refrigeration system is ensured.

Referring to fig. 3, the refrigeration system further includes a heat regenerator 23 and a gas return pipe 26, where the heat regenerator 23 includes a heat regenerator high temperature pipe 231 and a heat regenerator low temperature pipe 232 which are adjacently disposed, and heat exchange is performed between the heat regenerator high temperature pipe 231 and the heat regenerator low temperature pipe 232, where the heat regenerator high temperature pipe 231 is connected between the condenser 22 and the capillary tube 24, the heat regenerator low temperature pipe 232 is connected between the evaporator 25 and the compressor 21, and the gas return pipe 26 is connected between the evaporator 25 and the heat regenerator low temperature pipe 232.

The compressor 21, the condenser 22, the heat regenerator high temperature tube 231, the capillary tube 24, the evaporator 25, the air return tube 26 and the heat regenerator low temperature tube 232 are connected in sequence to form a refrigeration loop. The refrigerant is compressed by the compressor 21 and then enters the condenser 22, is condensed into a gas-liquid two-phase refrigerant, and then enters the heat regenerator high temperature tube 231 after exiting from the condenser 22, and is further condensed by the heat regenerator high temperature tube 231 to become a supercooled liquid; the refrigerant enters the capillary tube 24 for throttling, the temperature and the pressure of the refrigerant are reduced to the required evaporation temperature, the refrigerant enters the evaporator 25 and exchanges heat with the heat load of the refrigeration equipment, so that the outlet end of the evaporator 25 is a gas-liquid two-phase refrigerant, the gas-liquid two-phase refrigerant enters the heat regenerator low-temperature tube 232 at the moment, the refrigerant at the outlet end of the heat regenerator low-temperature tube 232 is superheated gas, the refrigerant in a superheated gas state enters the gas return tube 26 at the moment and finally returns to the compressor 21, and therefore the heat exchange efficiency of the evaporator 25 is improved, the energy efficiency ratio is improved, and the refrigeration efficiency is improved.

The refrigerating system is an ultralow temperature refrigerating system, and the temperature of the refrigerant can reach-95 ℃ or even lower after the capillary tube 24 is throttled. At such a low temperature, the viscosity of the press oil is increased, the flowing property is weakened, and the press oil is dissolved in the refrigerant, and the dissolved amount is greatly influenced by the temperature of the refrigerant; in the high-temperature pipe 231 of the heat regenerator, the pressure oil is more dissolved in the refrigerant, the temperature of the refrigerant is reduced after the capillary 24 is throttled, so that the liquid pressure oil is separated out, the capillary 24 is arranged to extend from bottom to top, and part of the pressure oil separated out in the capillary 24 naturally flows back to the condenser 22 during the shutdown period of the compressor 21, so that the pressure oil is prevented from flocculating near the outlet of the capillary 24 and blocking the capillary 24, and the stable operation of the refrigerating system is ensured.

Further, the inner container also comprises an inner container bottom wall 15 opposite to the inner container top wall 13, the heat regenerator 23 is fixed on the outer surface of the inner container bottom wall 15, the outer wall of the capillary tube 24 close to the heat regenerator 23 is contacted with the outer side of the air return pipe 26, specifically, the outer wall of the capillary tube 24 is contacted with the outer side of the air return pipe 26 on the outer surface of the inner container, and the heat exchange efficiency of the refrigerant in the air return pipe 26 and the refrigerant in the capillary tube 24 is improved.

Referring to fig. 3, the refrigeration system is a single-system refrigeration system, the single-system refrigeration system further includes a dry filter 27 connected between the condenser 22 and the high-temperature heat regenerator tube 231, and an anti-dew tube 28 connected between the condenser 22 and the dry filter 27, the anti-dew tube 28 is disposed at the opening 11 of the inner container, and the compressor 21, the condenser 22, the anti-dew tube 28, the dry filter 27, the high-temperature heat regenerator tube 231, the capillary tube 24, the evaporator 25, the air return tube 26, and the low-temperature heat regenerator tube 232 are sequentially connected to form a refrigeration loop. The refrigerant is compressed and then flows to the condenser 22 through a pipeline, and then passes through the anti-dew pipe 28, the refrigerant heats the opening 11 of the inner container in the anti-dew pipe 28, and both the condenser 22 and the anti-dew pipe 28 have the function of condensing the refrigerant. The refrigerant flows to the dry filter 27 after being cooled, and the moisture and impurities of the refrigerant are reduced after the dry filter.

Referring to fig. 4, the refrigeration system is a dual-system ultralow-temperature refrigeration system, and the refrigeration system includes a first refrigeration system and a second refrigeration system, both of which include a compressor 21, a condenser 22, a high-temperature regenerator tube 231, a capillary tube 24, an evaporator 25, an air return tube 26, and a low-temperature regenerator tube 232, wherein the first refrigeration system further includes a dry filter 27 connected between the condenser 22 and the high-temperature regenerator tube 231, and an anti-dew tube 28 connected between the condenser 22 and the dry filter 27. The second refrigeration system also includes a dry filter 27 between the condenser 22 and the high temperature tube 231 of the heat regenerator, and the refrigeration processes of the first refrigeration system and the second refrigeration system of the dual-system ultra-low temperature refrigeration system are the same as those of the single-system refrigeration system, which will not be described in detail herein.

As shown in fig. 5, the evaporator 25 of the first refrigeration system is a first coil, the evaporator 25 of the second refrigeration system is a second coil, the first coil and the second coil are distributed at intervals and are arranged independently, and the first coil and the second coil are respectively arranged on the outer surface of the inner container in a spiral manner from top to bottom, wherein the distance between the adjacent first coil and the second coil is 60mm, so as to avoid mutual interference, thereby improving the refrigeration independence of the first refrigeration system and the second refrigeration system, and the pipeline arrangement has the advantages that the lengths of the first refrigeration system and the second refrigeration system and the contact area of the first refrigeration system and the second refrigeration system are basically consistent, the heat exchange amount of the evaporator 25 is basically consistent, thereby facilitating the uniform temperature rise in the inner container, and no matter whether any one of the first refrigeration system and the second refrigeration system operates or both operate simultaneously.

As shown in fig. 6, the refrigeration apparatus further includes a condensing fan 3, the first refrigeration system and the second refrigeration system are single-stage compression systems, the compressor 21 of the first refrigeration system and the compressor 21 of the second refrigeration system are distributed at intervals along the first direction, the condenser 22 of the first refrigeration system and the condenser 22 of the second refrigeration system form a condenser assembly together and share the condensing fan 3, and the condensing fan 3 is disposed between the compressor 21 and the condenser assembly in the second direction. When the first refrigeration system or the second refrigeration system operates, the condensing fan 3 can operate independently without linkage control. The first refrigeration system and the second refrigeration system share the condensing fan 3, and the condensing fan has the advantages that other components can be used universally, and the error rate in the installation process is reduced.

Compared with the prior art, the utility model provides a refrigeration plant sets up in the below of inner bag through compressor 21 and condenser 22, thereby increase the size in holding chamber, increase the utilization ratio, capillary 24 extends the setting from bottom to top simultaneously, can let the part press oil that appears in capillary 24 in compressor 21 during shut down in condenser 22 of natural reflux, avoid press oil near capillary 24 export flocculation, block up capillary 24, set up from bottom to top through capillary 24, in order to realize that the refrigerant is for going into down in evaporator 25's flow direction, the press oil that can effectively avoid compressor 21 accumulates in evaporator 25, be favorable to compressor 21 oil return and evaporator 25 heat transfer stability's maintenance, it is stable to have the heat transfer, refrigeration effect is good, the advantage of stable in structure is reliable.

Embodiment 2 is a further description of the refrigeration system mentioned in embodiment 1 as a dual system ultra-low temperature refrigeration system, as shown in fig. 1 to 6 in conjunction therewith. It should be understood that the compressor 21 of the first refrigeration system in embodiment 1 is the first compressor 41 in embodiment 2, and the compressor 21 of the second refrigeration system in embodiment 1 is the second compressor 51 in embodiment 2, and the names of other technical features are the same and will not be described in detail.

The refrigeration equipment comprises an inner container and a refrigeration system, wherein the refrigeration system is a dual-system ultralow-temperature refrigeration system.

The refrigeration system comprises a first refrigeration system and a second refrigeration system, wherein the first refrigeration system comprises a first compressor 41, a first condenser 42, an anti-dew pipe 28, a first drying filter 47, a first capillary tube 44 and a first evaporator 45 which are connected through pipelines, and the second refrigeration system comprises a second compressor 51, a second condenser 52, a second drying filter 57, a second capillary tube 54 and a second evaporator 55 which are connected through pipelines. Preferably, the dew prevention tube 28 is provided at the liner opening 11. The refrigeration processes of the first refrigeration system and the second refrigeration system are described in the foregoing, and are not described in detail here.

The refrigerant is compressed and then flows to the first condenser 42 through a pipeline, the refrigerant heats the opening 11 of the inner container in the anti-dew pipe 28, and the first condenser 42 and the anti-dew pipe 28 both have the function of condensing the refrigerant.

The refrigeration equipment also comprises a condensing fan 3;

the first compressor 41 and the second compressor 51 are distributed below the inner container at intervals along the first direction, the first condenser 42 and the second condenser 52 together form a condenser assembly, and the first condenser 42 and the second condenser 52 are disposed below the inner container and share the condensing fan 3.

The aforementioned condensing fan 3 is disposed between the first compressor 41 and the first condenser 42 in the second direction. The condensing fan 3 is closer to the first condenser 42 than the first compressor 41. In this embodiment 2, the first direction is a longitudinal direction of the liner, and the second direction is a width direction of the liner, but it is understood that the first direction may be a width direction of the liner, and the second direction may be a longitudinal direction of the liner.

When the first refrigeration system or the second refrigeration system operates, the condensing fan 3 can operate independently without linkage control. The first refrigeration system and the second refrigeration system share the condensing fan 3, and the advantage that other components can be used universally, and the error rate in the installation process is reduced.

Referring to fig. 7, the condensing line of the first condenser 42 is at least partially disposed adjacent to the condensing fan, and the condensing line of the second condenser 52 is at least partially disposed adjacent to the condensing fan.

The condensation pipeline of the first condenser 42 and the condensation pipeline of the second condenser 52 are at least partially crossed, and the condensation pipeline of the first condenser 42 and the condensation pipeline of the second condenser 52 are arranged in a continuous bending line type. The condensing line of the first condenser 42 is crossed with the condensing line of the second condenser 52 at an intermediate position, and the two are arranged in an X shape.

Referring to fig. 8 and 9, the condensing pipes of the first condenser 42 and the condensing pipes of the second condenser 52 are arranged in a vertically layered manner or a front-back layered manner, wherein when the condensing pipes of the first condenser 42 and the condensing pipes of the second condenser 52 are arranged in a front-back layered manner, the first condenser 42 is closer to the condensing fan 3 than the second condenser 52.

The first refrigeration system is a common system, the running time of the first refrigeration system is long, so that the temperature of the first condenser 42 close to the condensing fan 3 is high, the temperature of the second condenser 52 far away from the condensing fan 3 is low, downstream heat exchange is formed between the first condenser and the wind of the condensing fan 3, and the heat exchange efficiency is high.

As shown in fig. 10, the condensing fan 3 includes a plurality of fans arranged in an array, wherein the plurality of fans are correspondingly disposed in an area between the first compressor 41 and the second compressor 51. It is ensured that the blower fan can uniformly blow toward the first compressor 41 and the second compressor 51.

Further, when the condensing pipelines of the first condenser 42 and the condensing pipelines of the second condenser 52 are layered up and down, two rows of fans are arranged in the vertical direction, and the number of the fans in the two rows is the same. For example, the number of the fans is 6, the fans are arranged in 2 rows, each row has 3 fans, the condensation pipeline of the first condenser 42 is located at the upper layer, the condensation pipeline of the second condenser 52 is located at the lower layer, when the first condenser 42 needs to operate, the 3 fans at the upper row operate, and when the second condenser 52 needs to operate, the 3 fans at the lower row operate.

Further, the first refrigeration system further includes a first heat regenerator 43, a first air return pipe 46, the first heat regenerator 43 includes a first heat regenerator high temperature pipe 431 and a first heat regenerator low temperature pipe 432, wherein the first heat regenerator high temperature pipe 431 is connected between the first dry filter 47 and the first capillary tube 44, the first heat regenerator low temperature pipe 432 is connected between the first evaporator 45 and the first compressor 41, and the first air return pipe 46 is connected between the first evaporator 45 and the first heat regenerator low temperature pipe 432. The refrigeration process of the first refrigeration system is described above and will not be described in detail here.

Further, the second refrigeration system further includes a second regenerator 53 and a second air return pipe 56, the second regenerator 53 includes a second regenerator high temperature pipe 531 and a second regenerator low temperature pipe 532, wherein the second regenerator high temperature pipe 531 is connected between the second dry filter 57 and the second capillary tube 54, the second regenerator low temperature pipe 532 is connected between the second evaporator 55 and the second compressor 51, and the second air return pipe 56 is connected between the second evaporator 55 and the second regenerator low temperature pipe 532. The refrigeration process of the second refrigeration system is described above and will not be described in detail here.

Further, the first regenerator 43 and the second regenerator 53 are respectively fixed on the bottom outer wall of the liner, which is the outer surface of the liner bottom wall 15 in the foregoing.

First capillary 44 contacts the outside of first muffler 46 near the outer wall of first regenerator 43, and second capillary 54 contacts the outside of second muffler 56 near the outer wall of second regenerator 53. Specifically, the outer wall of the first capillary tube 44 contacts the outer surface of the liner outside of the first gas return tube 46. The heat exchange efficiency of the refrigerant in the first return pipe 46 and the refrigerant in the first capillary tube 44 is improved. Similarly, the outer wall of the second capillary tube 54 contacts the bottom of the inner container with the outer side of the second muffler 56. The heat exchange efficiency of the refrigerant in the second muffler 56 and the refrigerant in the second capillary tube 54 is improved.

In order to solve the technical problem, a refrigeration control method of a refrigeration device, which is convenient to implement, is also provided below.

A refrigeration control method of a refrigeration device as described above, comprising the steps of:

the temperature T of the inlet end of the first filter-drier 47 is taken _Drying Obtaining the ambient temperature T of the refrigeration equipment _{Environment(s)} ；

At acquisition of T _Drying 、T _{Environment(s) of} Then, Δ T is calculated, where Δ T = T _Drying -T _{Environment(s)} ；

When obtaining the delta T, judging whether the delta T meets the condition that the delta T is more than 3 ℃ and less than or equal to 5 ℃;

when the delta T meets the condition that the delta T is more than 3 ℃ and less than or equal to 5 ℃, controlling the condensing fan 3 to preset duty ratio DR _{Preset of} Running;

when the delta T meets the condition that the delta T is less than or equal to 3 ℃, controlling the condensing fan 3 to be less than the preset duty ratio DR _{Preset of} Is operated, wherein the minimum value of the duty cycle DR is 40%;

when the delta T meets the temperature of more than 5 ℃, the condensing fan 3 is controlled to be more than the preset duty ratio DR _{Preset of} Is detected, wherein the maximum value of the duty cycle DR is 100%.

Specifically, the condensing fan 3 is a variable frequency fan, and the duty ratio of the condensing fan 3 is adjusted by monitoring the difference between the inlet end temperature of the first drying filter 47 and the ambient temperature. The control method is simple and easy to realize, and the duty ratio of the condensing fan 3 is 40-100%.

Ambient temperature T of a refrigeration device _{Environment(s)} The temperature sensors are arranged in a plurality of places which are in contact with the environment, such as a grating of the refrigeration equipment or the outer surface of a door body of the refrigeration equipment.

It is understood that the duty cycle of the condensing fan 3 can also be adjusted by monitoring the difference between the inlet temperature of the second dry filter 57 and the ambient temperature, and the adjustment method is the same as that described above and will not be described in detail here.

Preferably, when obtaining the delta T, judging whether the delta T meets the requirement that the delta T is less than 3 ℃ and less than or equal to 5 ℃ every 30 seconds.

Further, the refrigeration control method of the refrigeration equipment comprises the following steps:

acquiring a signal of initial power-on of the refrigeration equipment, wherein the initial power-on of the refrigeration equipment refers to when the unpowered time of the refrigeration equipment exceeds a first preset time t ₁ When the refrigeration equipment is powered on;

when a signal of the initial electrification of the refrigeration equipment is acquired, the duty ratio DR of the condensation fan 3 is set to be 50%, and meanwhile the duty ratio DR of the condensation fan 3 is set to be in a second preset time t ₂ The inner gradually increases to 100%;

when the duty ratio DR of the condensing fan 3 is increased to 100%, the duty ratio DR of the condensing fan 3 is set to be maintained at 100% for a third preset time t ₃ Wherein, t ₁ ＞t ₃ ＞t ₂ ；

At the third preset time t ₃ Thereafter, the temperature T at the inlet end of the first filter-drier 47 is obtained _Drying Obtaining the ambient temperature T of the refrigeration equipment _{Environment(s)} ；

When T is obtained _Drying 、T _{Environment(s)} Then, Δ T is calculated, where Δ T = T _Drying -T _{Environment(s)} The refrigeration control is performed by the refrigeration control method of the refrigeration apparatus described above.

In example 2, t ₁ Is 1h, t ₂ Is 3min ₃ It is 30min.

The operation of the condensing fan 3 is affected by the first compressor 41, that is, the first compressor 41 starts to operate, and then the condensing fan 3 operates; similarly, the operation of the condensing fan 3 is also affected by the second compressor 51, that is, the second compressor 51 starts to operate, and then the condensing fan 3 operates.

When the first compressor 41 is stopped, the condensing fan 3 has the following three control modes:

(1) the condensing fan 3 operates for 3min after the first compressor 41 is stopped

(2) After the first compressor 41 is stopped, the condensing fan 3 is continuously operated until the delta T is less than or equal to 3 DEG C

(3) After the first compressor 41 is stopped, the condensing fan 3 is continuously operated until the delta T3 is less than or equal to 15 ℃, wherein the delta T1 is the temperature T of the first compressor 41 _{Press 1} And the ambient temperature T _{Environment(s)} Δ T3= T _{Press 1} -T _{Environment(s)} 。

When the second compressor 51 is stopped, the condensing fan 3 has the above-described three control modes.

Compared with the prior art, the utility model provides a refrigeration plant and refrigeration plant's refrigeration control method sets up compressor 21 and condenser 22 in the below of inner bag, thereby increase the size in holding chamber, increase the utilization ratio, with first compressor 41 and second compressor 51 along the below of first direction interval distribution in inner bag, mutually couple first condenser 42 and second condenser 52 in the second direction sets up in the below of inner bag, rational layout refrigerating system's component, first condenser 42 and second condenser 52 share one aforementioned condensation fan 3, has material saving, reduce installation space's advantage, aforementioned condensation fan 3 sets up between first compressor 41 and first condenser 42 in the second direction, first refrigerating system or second refrigerating system operation, condensation fan 3 can the autonomous operation, need not coordinated control. Has the advantages of compact structure, reasonable layout and convenient control of the condensing fan 3.

In order to improve the stability and reliability of the refrigeration of the dual-system ultra-low temperature refrigeration system, embodiment 3 further provides a dual-system ultra-low temperature refrigeration system, embodiment 3 is a further limited description of embodiment 2, embodiment 3 is described from the perspective of the flow rate of the first capillary tube and the flow rate of the second capillary tube, and the rest of the same contents are not repeated.

A dual-system ultralow-temperature refrigerating system comprises a first refrigerating system and a second refrigerating system.

The first refrigeration system includes a first compressor 41, a first condenser 42, an anti-dew pipe 28, a first filter drier 47, a first capillary tube 44, and a first evaporator 45 connected by piping.

The second refrigeration system includes a second compressor 51, a second condenser 52, a second dry filter 57, a second capillary tube 54, and a second evaporator 55 connected by piping.

The first refrigeration system further includes a first heat regenerator 43, the first heat regenerator 43 includes a first heat regenerator high temperature pipe 431 and a first heat regenerator low temperature pipe 432, the first heat regenerator high temperature pipe 431 is connected between the first drying filter 47 and the first capillary tube 44, and the first heat regenerator low temperature pipe 432 is connected between the first evaporator 45 and the first compressor 41.

The second refrigeration system further includes a second regenerator 53, the second regenerator 53 includes a second regenerator high-temperature pipe 531 and a second regenerator low-temperature pipe 532, the second regenerator high-temperature pipe 531 is connected between the second dry filter 57 and the second capillary tube 54, and the second regenerator low-temperature pipe 532 is connected between the second evaporator 55 and the second compressor 51.

The refrigeration processes of the first refrigeration system and the second refrigeration system are described in the foregoing, and are not described in detail here.

Further, the flow rate of the first capillary 44 or the second capillary 54 is related to the inner diameter, the length, and the pressure difference across the inlet and outlet.

The flow rate through the first capillary 44 is different from that through the second capillary 54, so that the first refrigeration system and the second refrigeration system can respectively reach different minimum refrigeration temperatures, thereby meeting the refrigeration requirements of different low-temperature regions.

Preferably, the flow rate of the first capillary 44 is less than the flow rate of the second capillary 54. The first capillary tube 44 passes a smaller amount of refrigerant per unit time than the second capillary tube 54. That is, the refrigeration rate of the first refrigeration system is less than the refrigeration rate of the second refrigeration system, but the lowest temperature that can be reached by the first refrigeration system is lower than the lowest temperature that can be reached by the second refrigeration system.

It is understood that the first condenser 42 and the second condenser 52 may share a single condensing fan, or the first condenser 42 and the second condenser 52 may correspond to the first condensing fan and the second condensing fan, respectively.

Further, the flow rate of the first capillary 44 is: 5-7L/min;

the flow rate of the second capillary 54 is: 7-11L/min.

Further, the refrigerant in the first refrigeration system is a mixture of two refrigerants, namely R600 (a) and R1150, and the mass ratio of the R1150 in the two refrigerants is 20-50%.

The refrigerant of the second refrigeration system is a mixture of two refrigerants, namely R600 (a) and R170 mixed refrigerants respectively, and the mass ratio of the R170 in the two refrigerants is 10-60%.

Preferably, the flow rate of the first capillary tube 44 of the aforementioned first refrigeration system is: 5-7L/min, and the refrigeration temperature can reach-86 deg.C or below, such as-90 deg.C or 95 deg.C at 32 deg.C and ambient temperature

The flow rate of the second capillary tube 54 of the second refrigeration system is: 7-11L/min, and the refrigeration temperature can reach-60 ℃ at 32 ℃ ring temperature by matching with the refrigerant formula, so that the refrigeration requirements of different temperature intervals are met.

Further, the first condenser 42 and the second condenser 52 together form a condenser assembly and share a condensing fan, and the condensing fan is disposed at one side of the condenser assembly.

Further, the condensing line of the first condenser 42 is at least partially disposed adjacent to the condensing fan, and the condensing line of the second condenser 52 is at least partially disposed adjacent to the condensing fan.

Specifically, referring to fig. 7, the condensing pipeline of the first condenser 42 and the condensing pipeline of the second condenser 52 are at least partially crossed, and the condensing pipeline of the first condenser 42 and the condensing pipeline of the second condenser 52 are arranged in a continuous bending line manner. The condensing line of the first condenser 42 is crossed with the condensing line of the second condenser 52 at an intermediate position, and the two are arranged in an X shape.

Further, the condensation pipeline of the first condenser 42 and the condensation pipeline of the second condenser 52 are arranged in a vertical layered manner, and the condensation fan comprises a plurality of fans which are arranged in an upper row and a lower row.

The fans are arranged in two rows in the vertical direction, and the number of the fans distributed in the two rows is the same. For example, the number of the fans is 6, the fans are arranged in 2 rows, each row has 3 fans, the condensation pipeline of the first condenser 42 is located at the upper layer, the condensation pipeline of the second condenser 52 is located at the lower layer, when the first condenser 42 needs to operate, the 3 fans at the upper row operate, and when the second condenser 52 needs to operate, the 3 fans at the lower row operate. Furthermore, the condensing pipeline of the first condenser 42 and the condensing pipeline of the second condenser 52 are arranged in a front-back layered manner, and the condensing pipeline of the first condenser 42 is closer to the condensing fan.

When the condensing pipeline of the first condenser 42 and the condensing pipeline of the second condenser 52 are arranged in a front-back layered manner, the first condenser 42 is closer to the condensing fan 3 than the second condenser 52.

The arrangement of the first condenser 42, the second condenser 52 and the condensing fan 3 is described in detail in the foregoing, and will not be described repeatedly.

A refrigeration apparatus includes the dual-system ultra-low temperature refrigeration system and the condensing fan for dissipating heat of the first condenser 42 and the second condenser 52 in the dual-system ultra-low temperature refrigeration system.

The first evaporator 45 and the second evaporator 55 are arranged vertically on the outer surface of the inner container, the first evaporator 45 and the second evaporator 55 are arranged vertically and are related to the arrangement of the refrigeration temperature zones of the refrigeration equipment, for example, the first evaporator 45 corresponds to a refrigeration area and a temperature-changing area, and the second evaporator 55 corresponds to a freezing area.

The first evaporator 45 and the second evaporator 55 are arranged in a left-right manner, and the first evaporator 45 and the second evaporator 55 are arranged in a left-right manner and are related to the setting of the refrigeration temperature zone of the refrigeration equipment so as to adapt to the setting of different refrigeration temperatures.

Further, a third distribution mode of the first evaporator 45 and the second evaporator 55 is that the first evaporator 45 is a first coil pipe extending along the height of the inner container, the second evaporator 55 is a second coil pipe extending along the height of the inner container, the first coil pipe and the second coil pipe are distributed at intervals in a double-layer manner and are arranged independently, the first coil pipe and the second coil pipe are respectively spirally arranged on the outer surface of the inner container from top to bottom, wherein the distance between the adjacent first coil pipe and the second coil pipe is 60mm, mutual interference is avoided, so that the refrigeration independence of the first refrigeration system and the second refrigeration system is improved, and the pipeline arrangement has the advantages that the lengths of the first refrigeration system and the second refrigeration system and the contact area of the first refrigeration system and the second refrigeration system with the inner container are basically consistent, the heat exchange amount of the evaporators 25 is basically consistent, and uniform temperature rise in the inner container is facilitated, and whether any one of the first refrigeration system and the second refrigeration system is operated or both of the first refrigeration system and the second refrigeration system are operated simultaneously.

Further, the refrigeration equipment further comprises a shell, an inner container arranged in the shell, and a foaming layer defined between the shell and the inner container, wherein the inner container comprises an inner container bottom wall, the foaming layer comprises a bottom foaming layer arranged between the inner container bottom wall and the shell, and the first compressor 41, the first condenser 42, the second compressor 51 and the second condenser 52 are arranged below the inner container bottom wall; the first evaporator 45 and the second evaporator 55 are disposed on the outer surface of the inner container, and the first heat regenerator 43 and the second heat regenerator 53 are disposed in the bottom foaming layer. The first heat regenerator 43 and the second heat regenerator 53 need to be connected to other refrigeration components, so the first heat regenerator 43 and the second heat regenerator 53 are arranged in the bottom foaming layer at intervals along the length direction of the liner, the arrangement of a connecting pipeline can be simplified, the utilization rate of space is improved, and the size of the heat regenerator 23 is relatively adaptive to the size of the bottom of the liner.

acquiring a signal that the refrigeration equipment is in a normal on-off state; acquiring the preset temperature T in the box of the refrigeration equipment after acquiring the signal that the refrigeration equipment is in the normal on-off state _{Preset of} Wherein, T _{Preset of} Is a preset temperature value of the refrigeration equipment;

obtaining a preset temperature T in the box _{Preset of} Judging the preset temperature T in the box _{Preset of} Whether or not T is satisfied _{Preset of} ≥T _min2 Wherein, T _min2 The lowest temperature value which can be reached by the second refrigerating system;

when the temperature T is preset in the tank _{Preset of} Satisfy T _{Preset of} ≥T _min2 When the first refrigeration system is operated, the second refrigeration system is operated;

when the preset temperature in the box meets T _min1 ≤T _{Preset of} ＜T _min2 In time, the first refrigeration system is operated, wherein T _min1 ＜T _min2 ，T _min1 Is the lowest temperature value that can be reached by the first refrigeration system.

Specifically, the refrigeration rate of the first refrigeration system is less than the refrigeration rate of the second refrigeration system, and the second refrigeration system can reach T faster _min2 More suitably when T is _{Preset of} ≥T _min2 The second refrigeration system is operated.

When the preset temperature in the box meets T _min1 ≤T _Preset ＜T _min2 And when the temperature exceeds the lowest temperature value which can be reached by the second refrigeration system, the first refrigeration system is started again, and the lowest temperature which can be reached by the first refrigeration system is lower than the lowest temperature which can be reached by the second refrigeration system.

Further, when the first refrigeration system is operated, the condensing fan corresponding to the first condenser 42 is setDuty ratio DR ₁ Is DR _{Preset 1} Wherein, DR _{Preset 1} Is based on the temperature T at the outlet end of the first condenser 42 _{Condensation 1} And the ambient temperature T of the refrigeration appliance _{Environment(s)} Δ T1= T, is adjusted _{Condensation 1} -T _{Ring (C)} And (4) environmental conditions.

Further, the aforementioned DR _{Preset 1} Is set so that Δ T1 satisfies: delta T1 is more than 3 ℃ and less than or equal to 5 ℃.

Specifically, the condensing fan corresponding to the first condenser 42 is a variable frequency fan, and the temperature T of the outlet end of the first condenser 42 is monitored _{Condensation 1} And the ambient temperature T _{Environment(s)} The duty ratio of the condensing fan 3 is adjusted by the difference value. The control method is simple and easy to realize, and the duty ratio of the condensing fan 3 is 40-100%.

Further, when the second refrigeration system is operated, the duty ratio DR of the corresponding condensing fan of the second condenser 52 is set ₂ Is DR _{Preset 2} Wherein, DR _{Preset 2} Is based on the temperature T at the outlet end of the second condenser 52 _{Condensation 2} And the ambient temperature T of the refrigeration appliance _{Environment(s)} Δ T2, Δ T2= T _{Condensation 2} -a T environment.

Further, the aforementioned DR _{Preset 2} Is set so that Δ T2 satisfies: delta T2 is more than 3 ℃ and less than or equal to 5 ℃.

It will be appreciated that the corresponding condensing fan duty cycle of the second condenser 52 may also be monitored by monitoring the temperature T at the outlet end of the second condenser 52 _{Condensation 2} And the ambient temperature T _{Environment(s)} The adjustment method is the same as the above, and will not be described in detail here.

Further, comprising:

when a signal of initial power-on of the refrigeration equipment is acquired, operating a second refrigeration system;

when the second refrigeration system is operated, the duty ratio of the corresponding condensing fan of the second condenser 52 is set to 100% and maintained for the first preset time period t _{Preset 1} ；

At the first preset time period t _{Preset 1} Then, the first refrigeration system is operated and kept for a second preset time period t _{Preset 2} ；

At the second preset time period t _{Preset 2} Then, the temperature T in the refrigerator of the refrigeration equipment is obtained _{In the box} ；

In-box temperature T of refrigeration equipment _{In the box} Then, the in-box temperature T is judged _{In the box} Whether the shutdown temperature is reached;

in the cabinet temperature T _{In the box} And when the shutdown temperature is reached, the first refrigeration system and the second refrigeration system are closed, and the refrigeration equipment is set to be in a normal on-off state.

In example 3, t ₁ Is 1h.

When the refrigerator is initially powered on, the temperature T in the refrigerator is higher, such as 25 ℃ at normal temperature, the second refrigerating system 2 is started, the refrigerating rate of the first refrigerating system is lower than that of the second refrigerating system, and the second refrigerating system can lower the temperature in the refrigerator of the refrigerating equipment more quickly; meanwhile, the duty ratio of the corresponding condensing fan of the second condenser 52 is 100%, so that the heat dissipation function of the corresponding condensing fan of the second condenser 52 can be exerted to the greatest extent.

When the condensing fan corresponding to the first condenser 42 and the condensing fan corresponding to the second condenser 52 are the same condensing fan 3, the operation of the condensing fan 3 is affected by the first compressor 41, that is, the first compressor 41 starts to operate, and then the condensing fan 3 operates; similarly, the operation of the condensing fan 3 is also affected by the second compressor 51, that is, the second compressor 51 starts to operate, and then the condensing fan 3 operates. When the first compressor 41 is stopped, the condensing fan 3 has the following three control modes:

Compared with the prior art, the utility model provides a dual system ultra-low temperature refrigerating system, refrigeration plant and refrigeration control method are respectively through forming independent refrigeration cycle through first refrigerating system and second refrigerating system, in order to realize different refrigeration warm areas, the difference of first capillary 44 and second capillary 54's flow, so that first refrigerating system and second refrigerating system can reach different minimum refrigerating temperature respectively, thereby satisfy the refrigeration demand of different low temperature intervals, flow through first capillary 44 is less than second capillary 54's flow, first refrigerating system's refrigeration rate is less than second refrigerating system's refrigeration rate, but the minimum temperature that first refrigerating system can reach is lower than the minimum temperature that second refrigerating system can reach. The refrigerating system has the advantages of stable and reliable system, high refrigerating speed, low refrigerating temperature and diversified refrigerating temperature intervals by considering the requirements of refrigerating speed and refrigerating temperature regions.

Finally, the above embodiments are intended only to illustrate the technical solutions of the present invention and not to limit the same, and although the present invention has been described in detail with reference to the above preferred embodiments, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the scope of the present invention defined by the appended claims.

Claims

1. A refrigeration device comprises a liner and a refrigeration system, wherein the liner comprises a liner opening, a liner rear wall arranged opposite to the liner opening and a liner top wall connected with the top of the liner rear wall, the refrigeration system comprises a compressor, a condenser, a capillary tube and an evaporator which are connected through pipelines, the compressor and the condenser are arranged below the liner,

the capillary tube extends to the outer surface of the inner container from bottom to top, and the outlet end of the capillary tube is arranged close to the top wall of the inner container;

2. The refrigeration appliance of claim 1 wherein: the inner container also comprises two inner container side walls arranged on the left side and the right side of the rear wall of the inner container, wherein the outlet end of the capillary tube is arranged on the inner container side walls, and the capillary tube extends along the height direction of the inner container side walls.

3. The refrigeration appliance of claim 2, wherein: the horizontal section of the evaporator is of a U-shaped tubular structure, the U-shaped tubular structure comprises horizontal pipes arranged on the rear wall of the inner container and side pipes respectively arranged on the side walls of the inner container, and the included angle between each horizontal pipe and each side pipe is 87-89 degrees.

4. The refrigeration appliance of claim 2, wherein: the edge of the evaporator extending along the height direction of the side wall of the inner container is spaced from the capillary tube in advance.

5. The refrigeration appliance of claim 2, wherein: the distance between the capillary tube and the opening of the inner container is more than 80mm.

6. The refrigeration appliance of claim 1, wherein: the refrigerating system also comprises a heat regenerator and an air return pipe, wherein the heat regenerator comprises a heat regenerator high-temperature pipe and a heat regenerator low-temperature pipe which are adjacently arranged, the heat regenerator high-temperature pipe is connected between the condenser and the capillary tube, the heat regenerator low-temperature pipe is connected between the evaporator and the compressor, the air return pipe is connected between the evaporator and the heat regenerator low-temperature pipe,

7. The refrigeration appliance of claim 6 wherein: the inner container also comprises an inner container bottom wall opposite to the inner container top wall, the heat regenerator is fixed on the outer surface of the inner container bottom wall, and the outer side of the capillary tube close to the heat regenerator is contacted with the outer side of the air return tube.

8. The refrigeration appliance according to claim 6, wherein: the refrigerating system is a single-system refrigerating system, the single-system refrigerating system further comprises a dry filter connected between the condenser and the high-temperature tube of the heat regenerator, and an anti-dew tube connected between the condenser and the dry filter, and the anti-dew tube is arranged at the opening of the inner container.

9. The refrigeration appliance according to claim 6, wherein: the refrigerating system is a dual-system refrigerating system, the refrigerating system comprises a first refrigerating system and a second refrigerating system, the first refrigerating system and the second refrigerating system respectively comprise a compressor, a condenser, a heat regenerator high-temperature tube, a capillary tube, an evaporator, an air return tube and a heat regenerator low-temperature tube, the first refrigerating system further comprises a drying filter connected between the condenser and the heat regenerator high-temperature tube, and an anti-dew tube connected between the condenser and the drying filter, and the anti-dew tube is arranged at the opening of the inner container.

10. The refrigeration appliance according to claim 9, wherein: the evaporator of the first refrigeration system is a first coil pipe, the evaporator of the second refrigeration system is a second coil pipe, the first coil pipe and the second coil pipe are distributed in a double-layer interval mode and are arranged independently, and the first coil pipe and the second coil pipe are adjacent and the interval between the first coil pipe and the second coil pipe is 60mm.

11. The refrigeration appliance according to claim 9, wherein: the refrigeration system comprises a first refrigeration system and a second refrigeration system, and is characterized by further comprising a condensation fan, wherein the first refrigeration system and the second refrigeration system are single-stage compression systems, the compressor of the first refrigeration system and the compressor of the second refrigeration system are distributed at intervals along a first direction, and the condenser of the first refrigeration system and the condenser of the second refrigeration system share the condensation fan.