CN219318746U

CN219318746U - Double-system ultralow-temperature refrigerating system and refrigerating equipment

Info

Publication number: CN219318746U
Application number: CN202222569093.2U
Authority: CN
Inventors: 郑皓宇; 孙丰磊; 李彦玫; 李大伟; 张书锋
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: 2023-07-07
Anticipated expiration: 2032-09-27

Abstract

The utility model relates to a double-system ultralow temperature refrigeration system and refrigeration equipment, wherein the double-system ultralow temperature refrigeration system comprises a first refrigeration system and a second refrigeration system, and the first refrigeration system comprises a first compressor, a first condenser, an anti-dew pipe, a first dry filter, a first capillary tube and a first evaporator which are connected through pipelines; the second refrigerating system comprises a second compressor, a second condenser, a second dry filter, a second capillary tube and a second evaporator which are connected through pipelines; wherein the first refrigeration system further comprises a first regenerator; the second refrigeration system further comprises a second regenerator, and the flow rate of the first capillary tube is smaller than that of the second capillary tube. The utility model considers the requirements of the refrigerating rate and the refrigerating temperature area, and has the advantages of stable and reliable system, high refrigerating speed, low refrigerating temperature and diversified refrigerating temperature areas.

Description

Double-system ultralow-temperature refrigerating system and refrigerating equipment

Technical Field

The utility model relates to the technical field of refrigeration, in particular to a double-system ultralow-temperature refrigeration system and refrigeration equipment.

Background

At present, most of ultralow temperature refrigeration equipment is a single system, but the reliability of the ultralow temperature refrigeration equipment is limited due to high system pressure, and the ultralow temperature cabinet is a preservation box capable of reducing the temperature in the box to below-60 ℃ and keeping the temperature in the box so as to preserve valuable medical or scientific research products. Because of the large evaporation-condensation pressure difference and the limitation of the compressor, a single compressor is difficult to meet the requirement, the ultralow temperature cabinet in the prior art generally adopts a self-overlapping design, namely, the compressor compresses two working media, and the purpose of specifying the evaporation temperature is achieved after heat exchange is performed in the intermediate heat exchanger by utilizing different physical characteristics of the two working media. The compressor compresses two working media, the compressor pressure ratio born by the compressor is very large, the refrigerating system is easy to break, and the refrigerating problem is easy to occur in long-term operation, so that the stability and the reliability of ultralow-temperature refrigerating equipment in the prior art are lower.

Therefore, there is a need to develop a dual-system ultra-low temperature refrigeration system and a refrigeration device to solve the above problems.

Disclosure of Invention

The utility model aims to provide a double-system ultralow temperature refrigeration system.

In order to achieve the above object, an embodiment of the present utility model provides a dual-system ultralow temperature refrigeration system, including a first refrigeration system and a second refrigeration system, where the first refrigeration system includes a first compressor, a first condenser, an anti-dew tube, a first dry filter, a first capillary tube and a first evaporator connected by a pipeline; the second refrigerating system comprises a second compressor, a second condenser, a second dry filter, a second capillary tube and a second evaporator which are connected through pipelines; the first refrigeration system further comprises a first heat regenerator, the first heat regenerator comprises a first heat regenerator high-temperature pipe and a first heat regenerator low-temperature pipe, the first heat regenerator high-temperature pipe is connected between the first dry filter and the first capillary tube, and the first heat regenerator low-temperature pipe is connected between the first evaporator and the first compressor; the second refrigerating system further comprises a second heat regenerator, the second heat regenerator comprises a second heat regenerator high-temperature pipe and a second heat regenerator low-temperature pipe, the second heat regenerator high-temperature pipe is connected between the second dry filter and the second capillary, and the second heat regenerator low-temperature pipe is connected between the second evaporator and the second compressor; the flow rate of the first capillary is smaller than the flow rate of the second capillary.

As a further improvement of an embodiment of the present utility model, the flow rate of the first capillary is: 5-7L/min; the flow rate of the second capillary is as follows: 7-11L/min.

As a further improvement of an embodiment of the present utility model, the first condenser and the second condenser together form a condenser assembly and share a condensing fan, and the condensing fan is disposed at one side of the condenser assembly.

As a further improvement of an embodiment of the present utility model, the condensation line of the first condenser is at least partially disposed adjacent to the condensation fan, and the condensation line of the second condenser is at least partially disposed adjacent to the condensation fan.

As a further improvement of an embodiment of the utility model, the condensation pipeline of the first condenser and the condensation pipeline of the second condenser are arranged in an up-down layered mode, the condensation fan comprises a plurality of fans, and the fans are distributed in an up-down two rows.

As a further improvement of an embodiment of the present utility model, the condensation pipeline of the first condenser and the condensation pipeline of the second condenser are arranged in a front-back layered manner, and the condensation pipeline of the first condenser is arranged closer to the condensation fan.

In order to solve the above technical problems, a refrigeration device is further provided below.

A refrigeration device comprises the double-system ultralow temperature refrigeration system and a condensing fan for radiating heat for a first condenser and a second condenser in the double-system ultralow temperature refrigeration system.

As a further improvement of an embodiment of the utility model, the evaporator further comprises a shell and a liner arranged in the shell, wherein the first evaporator and the second evaporator are arranged on the outer surface of the liner up and down.

As a further improvement of an embodiment of the present utility model, the evaporator further comprises a housing, and a liner disposed in the housing, wherein the first evaporator and the second evaporator are disposed on the outer surface of the liner in a left-right manner.

As a further improvement of an embodiment of the present utility model, the air conditioner further comprises a housing, an inner container disposed in the housing, and a foaming layer defined between the housing and the inner container, wherein the inner container comprises an inner container bottom wall, the foaming layer comprises a bottom foaming layer disposed between the inner container bottom wall and the housing, and the first compressor, the first condenser, the second compressor and the second condenser are disposed below the inner container bottom wall; the first evaporator and the second evaporator are arranged on the outer surface of the inner container, and the first heat regenerator and the second heat regenerator are arranged in the bottom foaming layer.

As a further improvement of an embodiment of the utility model, the first evaporator is a first coil pipe extending along the height of the inner container, the second evaporator is a second coil pipe extending along the height of the inner container, and the first coil pipe and the second coil pipe are distributed at intervals and are independent of each other, wherein the first heat regenerator and the second heat regenerator are distributed in the bottom foaming layer at intervals along the length direction of the inner container.

Compared with the prior art, the utility model has the beneficial effects that: the utility model provides a double-system ultralow-temperature refrigerating system, refrigerating equipment and a refrigerating control method, wherein independent refrigerating circulation is respectively formed through a first refrigerating system and a second refrigerating system so as to realize different refrigerating temperature areas, the flow rates of the first capillary tube and the second capillary tube are different, so that the first refrigerating system and the second refrigerating system can respectively reach different minimum refrigerating temperatures, the refrigerating requirements in different low-temperature areas are met, the flow rate of the first capillary tube is smaller than the flow rate of the second capillary tube, the refrigerating rate of the first refrigerating system is smaller than the refrigerating rate of the second refrigerating system, and the lowest temperature which can be reached by the first refrigerating system is lower than the lowest temperature which can be reached by the second refrigerating system. The system has the advantages of stability and reliability, high refrigerating speed, low refrigerating temperature and diversified refrigerating temperature intervals.

Drawings

FIG. 1 is a schematic diagram of the structural composition of a refrigeration apparatus of the present utility model;

FIG. 2 is a schematic horizontal cross-sectional view of an evaporator of the refrigeration apparatus of the present utility model;

FIG. 3 is a system configuration diagram of the refrigeration apparatus of the present utility model 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 present utility model when the refrigeration system is a dual-system ultra-low temperature refrigeration system;

FIG. 5 is a schematic diagram of the first coil and the second coil of the refrigeration apparatus of the present utility model;

FIG. 6 is a schematic diagram of a condensing fan layout of a refrigeration unit according to the present utility model;

FIG. 7 is a schematic view of a first embodiment of a first condenser and a second condenser of the refrigeration apparatus of the present utility model;

FIG. 8 is a schematic diagram of a second embodiment of a first condenser and a second condenser of the refrigeration apparatus of the present utility model;

fig. 9 is a schematic structural view of a third embodiment of a first condenser and a second condenser of the refrigeration apparatus of the present utility model;

FIG. 10 is a schematic view of a condensing fan of the refrigeration apparatus of the present utility model;

fig. 11 is a system configuration diagram of another embodiment of the refrigeration system of the refrigeration apparatus according to the present utility model when the refrigeration system is a dual-system ultra-low temperature refrigeration system.

In the figure: 11. an opening of the inner container; 12. the rear wall of the inner container; 13. a top wall of the liner; 14. the side wall of the inner container; 15. a bottom wall of the inner container; 21. a compressor; 22. a condenser; 23. a 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 pipe; 26. an air return pipe; 27. drying the filter; 28. an anti-dew tube; 3. a condensing fan; 41. a first compressor; 42. a first condenser; 43. a first regenerator; 431. a first regenerator high temperature tube; 432. a first regenerator low temperature tube; 44. a first capillary; 45. a first evaporator; 46. a first muffler; 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 low temperature tube; 54. a second capillary; 55. a second evaporator; 56. a second muffler; 57. and a second dry filter.

Detailed Description

The preferred embodiments of the present utility model will be described in detail below with reference to the accompanying drawings so that the advantages and features of the present utility model can be more easily understood by those skilled in the art, thereby making clear and defining the scope of the present utility model.

The terms "comprising" and "having" and any variations thereof herein are intended to cover a non-exclusive inclusion. Reference herein to "an embodiment" means that a particular feature, structure, or characteristic described in connection with the embodiment may be included in at least one embodiment of the present application. The appearances of such phrases 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. Those of skill in the art will explicitly and implicitly appreciate that the embodiments described herein may be combined with other embodiments.

Referring to fig. 1, the present utility model mainly relates to: a refrigerating device is explained by taking an ultralow temperature vertical refrigerator as an example. The refrigeration equipment comprises a liner and a refrigeration system, wherein the liner defines a containing cavity, and comprises a liner opening 11, a liner rear wall 12 arranged opposite to the liner opening 11 and a liner top wall 13 connected to the top of the liner rear wall 12.

In this embodiment 1, the refrigeration system includes a compressor 21, a condenser 22, a capillary tube 24, and an evaporator 25 connected by a pipe, and the refrigerant is sequentially led from the compressor 21 to the condenser 22, the capillary tube 24, and the evaporator 25, and is returned to the compressor 21, thereby forming a refrigeration cycle. The compressor 21 and the condenser 22 are arranged below the liner, the condenser 22 is arranged at one side of the compressor 21, the capillary tube 24 extends to the outer surface of the liner 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 close to the liner top wall 13, and the flow direction of the 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 from the outlet end of the capillary tube 24 downwards in a serpentine manner, the outlet end of the evaporator 25 extends downwards to the air inlet end of the compressor 21, and the flow direction of the refrigerant in the evaporator 25 is up-and-down through the arrangement of the capillary tube 24, so that the accumulation of press oil of the compressor 21 in the evaporator 25 can be effectively avoided, and the oil return of the compressor 21 is facilitated; and the capillary tube 24 is arranged in a way of extending from bottom to top, so that part of compressor oil separated out in the capillary tube 24 can naturally flow back to the condenser 22 during the stop of the compressor 21, flocculation of the compressor oil near the outlet of the capillary tube 24 and blockage of the capillary tube 24 are avoided, and the refrigerating system has the advantage of improving the refrigerating stability of the refrigerating system.

Further, the inner container further includes two inner container side walls 14 disposed at the left and right sides of the inner container rear wall 12, wherein the outlet end of the capillary tube 24 is disposed on the inner container side wall 14, and the capillary tube 24 extends along the height direction of the inner container side wall 14.

Referring to fig. 2, the evaporator 25 is spirally wound on the two inner container side walls 14 and the inner container rear wall 12, the horizontal section of the evaporator 25 is a U-shaped tubular structure, and the U-shaped tubular structure comprises a horizontal tube 251 arranged on the inner container rear wall 12 and side tubes 252 respectively arranged on the inner container side walls 14, so that the refrigerating effect of the two inner container side walls 14 and the inner container rear wall 12 can be effectively ensured, and the refrigerating uniformity in the accommodating cavity can be ensured. Wherein, the included angle between the horizontal tube 251 and the side tube 252 is 87-89 degrees, which is matched with the outer surface of the inner container as far as possible.

Further, the edge of the evaporator 25 extending along the height direction of the liner sidewall 14 is spaced from the capillary tube 24, and the capillary tube 24 is not in contact with the evaporator 25, so that heat exchange between the two is avoided.

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

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

The compressor 21, the condenser 22, the high-temperature heat regenerator pipe 231, the capillary tube 24, the evaporator 25, the air return pipe 26 and the low-temperature heat regenerator pipe 232 are sequentially connected to form a refrigeration loop. The refrigerant is compressed by the compressor 21 and enters the condenser 22, and is condensed into gas-liquid two-phase refrigerant which is discharged from the condenser 22 and enters the high-temperature tube 231 of the heat regenerator, and the gas-liquid two-phase refrigerant is further condensed by the high-temperature tube 231 of the heat regenerator and becomes supercooled liquid; the refrigerant enters the capillary tube 24 to throttle, the temperature and the pressure of the refrigerant are reduced to the required evaporating 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 low-temperature tube 232 of the heat regenerator at the moment, the refrigerant at the outlet end of the low-temperature tube 232 of the heat regenerator is overheated gas, and the refrigerant in the overheated gas state enters the muffler 26 and finally returns to the compressor 21, thereby improving the heat exchange efficiency of the evaporator 25, the energy efficiency ratio and the refrigeration efficiency.

The refrigeration system is an ultralow temperature refrigeration system, and the temperature of the refrigerant can reach-95 ℃ or even lower after the capillary tube 24 is throttled. At such low temperature, the viscosity of the press oil is increased, the flow performance 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 compressor oil is more dissolved in the refrigerant, the temperature of the refrigerant is reduced after the capillary tube 24 is throttled to cause the precipitation of liquid compressor oil, and the capillary tube 24 extends from bottom to top, so that part of the compressor oil precipitated in the capillary tube 24 naturally flows back to the condenser 22 during the shutdown of the compressor 21, the flocculation of the compressor oil near the outlet of the capillary tube 24 is avoided, the capillary tube 24 is blocked, and the stable operation of the refrigerating system is ensured.

Further, the inner container further 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 tube 26, specifically, the outer wall of the capillary tube 24 is contacted with the outer side of the air return tube 26, and the heat exchange efficiency of the refrigerant in the air return tube 26 and the refrigerant in the capillary tube 24 is improved.

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

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

Referring to 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 in a double layer and are arranged independently, the first coil and the second coil are respectively arranged on the outer surface of the liner from top to bottom in a spiral mode, the interval between the adjacent first coil and second coil is 60mm, mutual interference is avoided, refrigeration independence of the first refrigeration system and the second refrigeration system is improved, the pipeline arrangement has the advantages that the pipeline length of the first refrigeration system and the pipeline length of the second refrigeration system are basically consistent with the contact area of the first refrigeration system and the second refrigeration system and the heat exchange amount of the evaporator 25 is basically consistent, and uniform in-box temperature lifting is facilitated, and the first refrigeration system and the second refrigeration system are operated by any one set of single system or by two single systems simultaneously.

Referring to fig. 6, the refrigeration apparatus further includes a condensation 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 together form a condenser assembly and share the condensation fan 3, and the condensation fan 3 is disposed between the compressor 21 and the condenser assembly in the second direction. When the first refrigerating system or the second refrigerating system is operated, the condensing fan 3 can be independently operated without linkage control. The first refrigerating system and the second refrigerating system share the condensing fan 3, and the condensing fan has the advantages that other components can be used commonly, and the error rate in the installation process is reduced.

Compared with the prior art, the refrigerating equipment provided by the utility model has the advantages that the size of the accommodating cavity is increased and the utilization rate is improved by arranging the compressor 21 and the condenser 22 below the inner container, meanwhile, the capillary tube 24 is arranged in an extending manner from bottom to top, part of compressor oil separated out from the capillary tube 24 naturally flows back to the condenser 22 during the shutdown of the compressor 21, the compressor oil is prevented from flocculating near the outlet of the capillary tube 24 and blocking the capillary tube 24, the flow direction of the refrigerant at the evaporator 25 is changed from bottom to top through the arrangement of the capillary tube 24, the compressor oil of the compressor 21 can be effectively prevented from accumulating in the evaporator 25, the maintenance of the oil return of the compressor 21 and the heat exchange stability of the evaporator 25 is facilitated, and the refrigerating equipment has the advantages of stable heat exchange, good refrigerating effect and stable and reliable structure.

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 connection with fig. 1-6. It is understood that the compressor 21 of the first refrigeration system in embodiment 1 is the first compressor 41 of embodiment 2, and the compressor 21 of the second refrigeration system in embodiment 1 is the second compressor 51 of embodiment 2, and other technical features are the same as those described above and will not be described in detail.

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

The refrigeration system includes a first refrigeration system including a first compressor 41, a first condenser 42, an anti-dew tube 28, a first dry filter 47, a first capillary tube 44, and a first evaporator 45 connected by a pipe, and a second refrigeration system including 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 a pipe. Preferably, the anti-dew tube 28 is provided at the liner opening 11. The refrigeration processes of the first refrigeration system and the second refrigeration system have been described above and are not described in detail herein.

The refrigerant is compressed from the refrigerant and then flows to the first condenser 42 through the pipeline, the refrigerant heats the opening 11 of the inner container in the dew-proof tube 28, and both the first condenser 42 and the dew-proof tube 28 play a role in condensing the refrigerant.

The refrigeration equipment also comprises a condensing fan 3;

the first compressor 41 and the second compressor 51 are spaced below the inner container 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 condensing fan 3 is disposed between the first compressor 41 and the first condenser 42 in the second direction. The condensing fan 3 is located closer to the first condenser 42 than the first compressor 41. In embodiment 2, the first direction refers to the longitudinal direction of the liner, and the second direction refers to the width direction of the liner, and it is understood that the first direction may be the width direction of the liner, and the second direction may be the longitudinal direction of the liner.

When the first refrigerating system or the second refrigerating system is operated, the condensing fan 3 can be independently operated without linkage control. The first refrigerating system and the second refrigerating system share the condensing fan 3, and the condensing fan has the advantages that other components can be used commonly, and the error rate in the installation process is reduced.

As shown in connection with fig. 7, the condensing duct of the first condenser 42 is at least partially disposed adjacent the condensing fan and the condensing duct of the second condenser 52 is at least partially disposed adjacent the condensing fan.

The condensation line of the first condenser 42 and the condensation line of the second condenser 52 are at least partially crossed, and the condensation line of the first condenser 42 and the condensation line of the second condenser 52 are arranged in a continuous bending line type. The condensing lines of the first condenser 42 are disposed at the middle position to intersect the condensing lines of the second condenser 52, and form an "X" arrangement.

As shown in fig. 8 and 9, the condensation lines of the first condenser 42 and the second condenser 52 are arranged in a top-bottom layered or front-back layered manner, wherein when the condensation lines of the first condenser 42 and the second condenser 52 are arranged in a front-back layered manner, the first condenser 42 is closer to the condensation fan 3 than the second condenser 52.

The first refrigerating system is a common system, and the running time of the first refrigerating system is long, so that the temperature of the first condenser 42 close to the condensing fan 3 side is high, the temperature of the second condenser 52 far away from the condensing fan 3 side is low, and the downstream heat exchange is formed with 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 can blow evenly to the first compressor 41 and the second compressor 51.

Further, when the condensation lines of the first condenser 42 and the condensation lines of the second condenser 52 are layered up and down, 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. With the number of fans being 6 for illustration, the fans are in upper and lower 2 rows, 3 fans in each row, 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 in the upper row operate, and when the second condenser 52 needs to operate, the 3 fans in the lower row operate.

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

Further, the second refrigeration system further comprises a second regenerator 53 and a second muffler 56, wherein the second regenerator 53 comprises 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, the second regenerator low temperature pipe 532 is connected between the second evaporator 55 and the second compressor 51, and the second muffler 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 herein.

Further, the first regenerator 43 and the second regenerator 53 are respectively fixed on the bottom outer wall of the inner container, that is, the outer surface of the bottom wall 15 of the inner container.

The outer wall of the first capillary tube 44 near the first regenerator 43 contacts the outside of the first muffler 46, and the outer wall of the second capillary tube 54 near the second regenerator 53 contacts the outside of the second muffler 56. Specifically, the outer wall of the first capillary tube 44 is in contact with the outer surface of the inner liner outside the first muffler 46. The heat exchange efficiency of the refrigerant in the first muffler 46 and the refrigerant in the first capillary tube 44 is improved. Similarly, the outer wall of the second capillary tube 54 contacts the outer side of the second muffler 56 at the bottom of the inner container. 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 problems, the following further provides a refrigeration control method of the refrigeration equipment, which is convenient to implement.

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

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

After T is acquired _Drying 、T _{Environment (environment)} At that time, Δt is calculated, where Δt=t _Drying -T _{Environment (environment)} ；

When delta T is obtained, judging whether delta T meets 3 ℃ and delta T is less than or equal to 5 ℃;

when delta T meets 3 ℃ less than delta T less than or equal to 5 ℃, the condensing fan 3 is controlled to have a preset duty ratio DR _Presetting Operating;

when the delta T meets the delta T not more than 3 ℃, the condensing fan 3 is controlled to be smaller than the preset duty ratio DR _Presetting Wherein the minimum value of the duty cycle DR is 40%;

when the delta T satisfies the temperature of more than 5 ℃, the condensing fan 3 is controlled to be larger than the preset duty ratio DR _Presetting 10 of (2)% operation, 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 temperature of the inlet end 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 refrigeration plant _{Environment (environment)} By placing the temperature sensor in a place that is in relatively high contact with the environment, such as a grille of a refrigeration appliance or a door outer surface of a refrigeration appliance, etc.

It will be appreciated that the duty cycle of the condensing fan 3 may also be adjusted by monitoring the difference between the inlet end temperature of the second filter drier 57 and the ambient temperature in the same manner as described above and not described in detail herein.

Preferably, when DeltaT is obtained, it is judged whether DeltaT satisfies 3 ℃ and DeltaT.ltoreq.5 ℃ every 30 seconds.

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

acquiring a signal of primary power-on of the refrigeration equipment, wherein the primary 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 refrigerating equipment is electrified;

when the signal of the primary power-on of the refrigeration equipment is obtained, setting the duty ratio DR of the condensing fan 3 to be 50% and setting the duty ratio DR of the condensing fan 3 to be at 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 100% to maintain the third preset time t ₃ Wherein t is ₁ ＞t ₃ ＞t ₂ ；

At the third preset time t ₃ After that, the temperature T of the inlet end of the first dry filter 47 is obtained _Drying Obtaining the ambient temperature T of the refrigeration equipment _{Environment (environment)} ；

After T is acquired _Drying 、T _{Environment (environment)} At that time, Δt is calculated, where Δt=t _Drying -T _{Environment (environment)} The refrigeration control is performed by the refrigeration control method of the refrigeration equipment.

In example 2, t ₁ 1h, t ₂ For 3min, t ₃ 30min.

The operation of the condensing fan 3 is affected by the first compressor 41, i.e. the first compressor 41 starts to operate, and the condensing fan 3 operates; similarly, the operation of the condensing fan 3 is also affected by the second compressor 51, i.e. the second compressor 51 starts to operate, and 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 is operated for 3min after the first compressor 41 is stopped

(2) After the first compressor 41 is stopped, the condensing fan 3 continuously operates 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 delta T1 is the temperature T of the first compressor 41 _{Press 1} And ambient temperature T _{Environment (environment)} Delta T3 = T _{Press 1} -T _{Environment (environment)} 。

When the second compressor 51 is shut down, the condensing fan 3 has the above three control modes.

Compared with the prior art, the refrigerating equipment and the refrigerating control method of the refrigerating equipment provided by the utility model have the advantages that the size of the accommodating cavity is increased and the utilization rate is improved by arranging the compressor 21 and the condenser 22 below the inner container, 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 are mutually coupled below the inner container along the second direction, the constituent parts of the refrigerating system are reasonably distributed, the first condenser 42 and the second condenser 52 share the condensing fan 3, the material is saved, the installation space is reduced, the condensing fan 3 is arranged between the first compressor 41 and the first condenser 42 along the second direction, and the condensing fan 3 can independently operate without linkage control when the first refrigerating system or the second refrigerating system operates. 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 ultralow temperature refrigeration system, embodiment 3 further provides a dual-system ultralow temperature refrigeration system, embodiment 3 is a further defined 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 will not be repeated.

A dual system ultra-low temperature refrigeration system includes a first refrigeration system and a second refrigeration system.

The first refrigeration system includes a first compressor 41, a first condenser 42, an anti-dew tube 28, a first dry filter 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 regenerator 43, where the first regenerator 43 includes a first regenerator high temperature pipe 431 and a first regenerator low temperature pipe 432, the first regenerator high temperature pipe 431 is connected between the first dry filter 47 and the first capillary tube 44, and the first 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 have been described above and are not described in detail herein.

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

The first and second refrigerating systems can reach different minimum refrigerating temperatures through the different flow rates of the first and

second capillaries

44 and 54, respectively, so as to meet the refrigerating demands 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 amount of refrigerant passing through the first capillary tube 44 is smaller than the amount of refrigerant passing through the second capillary tube 54 per unit time. That is, the refrigeration rate of the first refrigeration system is less than the refrigeration rate of the second refrigeration system, but the minimum temperature that the first refrigeration system can achieve is lower than the minimum temperature that the second refrigeration system can achieve.

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

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

Preferably, the flow rate of the first capillary tube 44 of the first refrigeration system is: 5-7L/min, and the refrigeration temperature which can be reached at the ring temperature of 32 ℃ is less than or equal to 86 ℃ below zero, such as 90 ℃ below zero or 95 ℃ below zero by matching with the refrigerant formula

The flow rate of the second capillary tube 54 of the second refrigeration system is: 7-11L/min, and the refrigeration temperature which can be reached at the ring temperature of 32 ℃ is minus 60 ℃ by matching with the refrigerant formula, thereby meeting the refrigeration requirements of different temperature ranges.

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

Specifically, as shown in fig. 7, the condensation line of the first condenser 42 and the condensation line of the second condenser 52 are at least partially disposed in a crossing manner, and the condensation line of the first condenser 42 and the condensation line of the second condenser 52 are disposed in a continuous meander line. The condensing lines of the first condenser 42 are disposed at the middle position to intersect the condensing lines of the second condenser 52, and form an "X" arrangement.

Further, the condensation pipeline of the first condenser 42 and the condensation pipeline of the second condenser 52 are arranged in an upper-lower layered mode, the condensation fan comprises a plurality of fans, and the fans are distributed in an upper-lower two-row mode.

The fans are in two rows in the vertical direction, and the quantity of the fans distributed in the two rows is the same. With the number of fans being 6 for illustration, the fans are in upper and lower 2 rows, 3 fans in each row, 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 in the upper row operate, and when the second condenser 52 needs to operate, the 3 fans in the lower row operate. Further, the condensation pipeline of the first condenser 42 and the condensation pipeline of the second condenser 52 are arranged in a front-back layered mode, and the condensation pipeline of the first condenser 42 is arranged closer to the condensation fan.

When the condensation lines of the first condenser 42 and the second condenser 52 are arranged in a front-back layered manner, the first condenser 42 is closer to the condensation 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 the description thereof will not be repeated.

A refrigeration apparatus includes a dual-system cryogenic refrigeration system as described above and a condensing fan configured to dissipate heat from the first condenser 42 and the second condenser 52 in the dual-system cryogenic refrigeration system.

The first distribution mode of the first evaporator 45 and the second evaporator 55 is that the first evaporator 45 and the second evaporator 55 are arranged on the outer surface of the liner up and down, and the first evaporator 45 and the second evaporator 55 are arranged up and down in relation to the arrangement of the refrigeration temperature area of the refrigeration equipment, for example, the first evaporator 45 corresponds to the refrigeration area and the temperature change area, and the second evaporator 55 corresponds to the refrigeration area.

The second distribution mode of the first evaporator 45 and the second evaporator 55, the first evaporator 45 and the second evaporator 55 are arranged left and right relative to the arrangement of the refrigeration temperature zone of the refrigeration equipment so as to adapt to different refrigeration temperature arrangements.

Further, the third distribution mode of the first evaporator 45 and the second evaporator 55, 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 and are mutually independent, the first coil pipe and the second coil pipe are respectively arranged on the outer surface of the inner container in a spiral mode from top to bottom, the interval between the adjacent first coil pipe and 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, the pipeline arrangement has the advantages that the pipeline length of the first refrigeration system and the second refrigeration system is basically consistent with the contact area of the inner container, the heat exchange quantity of the evaporator 25 is basically consistent, and the temperature in the box is improved uniformly, and the first refrigeration system and the second refrigeration system are operated in any one set of single system or two systems 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 regenerator 43 and the second regenerator 53 are disposed in the bottom foaming layer. The first heat regenerator 43 and the second heat regenerator 53 need to be connected with other refrigeration components respectively, so that the first heat regenerator 43 and the second heat regenerator 53 are distributed in the bottom foaming layer at intervals along the length direction of the liner, the arrangement of connecting pipelines can be simplified, the space utilization rate is improved, and meanwhile, the size of the heat regenerator 23 is relatively matched with the size of the bottom of the liner.

acquiring a signal of the refrigeration equipment in a normal open and stop state; after acquiring a signal for acquiring normal open and stop state of the refrigeration equipment, acquiring preset temperature T in a box of the refrigeration equipment _Presetting Wherein T is _Presetting A preset temperature value of the refrigeration equipment;

at the time of obtaining the preset temperature T in the box _Presetting Judging the preset temperature T in the box _Presetting Whether or not to satisfy T _Presetting ≥T _min2 Wherein T is _min2 A minimum temperature value achievable for the second refrigeration system;

when the temperature T is preset in the box _Presetting Satisfy T _Presetting ≥T _min2 Operating the second refrigeration system while;

when the preset temperature in the box meets T _min1 ≤T _Presetting ＜T _min2 Operating the first refrigeration system, wherein T _min1 ＜T _min2 ，T _min1 Is the lowest temperature value that can be achieved by the first refrigeration system.

Specifically, the refrigeration rate of the first refrigeration system is smaller than that of the second refrigeration system, and the second refrigeration system can reach T faster _min2 More suitably when T _Presetting ≥T _min2 When the second refrigeration system is operated.

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

Further, in transitWhen the first refrigerating system is operated, the duty ratio DR of the condensing fan corresponding to the first condenser 42 is set ₁ For DR _{Preset 1} Wherein DR _{Preset 1} According to the temperature T at the outlet end of the first condenser 42 _{Condensation 1} And the ambient temperature T of the refrigeration plant _{Environment (environment)} Is adjusted by a temperature difference Δt1, Δt1=t _{Condensation 1} -T _Ring(s) And (5) an environment.

Further, the aforementioned DR _{Preset 1} The basis of the setting is such that Δt1 satisfies: delta T1 is less than or equal to 5 ℃ and is more than 3 ℃.

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

Further, in operating the second refrigeration system, the duty cycle DR of the corresponding condensing fan of the second condenser 52 is set ₂ For DR _{Preset 2} Wherein DR _{Preset 2} According to the temperature T at the outlet end of the second condenser 52 _{Condensation 2} And the ambient temperature T of the refrigeration plant _{Environment (environment)} Is adjusted by a temperature difference Δt2, Δt2=t _{Condensation 2} -T environment.

Further, the aforementioned DR _{Preset 2} The basis of the setting is such that Δt2 satisfies: delta T2 is less than or equal to 5 ℃ and is more than 3 ℃.

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

Further, the method comprises the steps of:

acquiring a signal of primary power-on of the refrigeration equipment, wherein the signal of primary power-on of the refrigeration equipmentMeans when the non-energized time of the refrigeration equipment exceeds a first preset time t ₁ When the refrigerating equipment is electrified;

when a signal of the primary power-on of the refrigeration equipment is obtained, a second refrigeration system is operated;

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

After reaching the first preset time period t _{Preset 1} Thereafter, the first refrigeration system is operated and maintained for a second preset period of time t _{Preset 2} ；

After reaching the second preset time period t _{Preset 2} After that, the temperature T in the refrigerator is obtained _{In the box} ；

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

in-tank temperature T _{In the box} When the shutdown temperature is reached, the first refrigerating system and the second refrigerating system are closed, and the refrigerating equipment is set to be in a normal open and shutdown state.

In example 3, t ₁ 1h.

When the power is initially applied, the temperature T in the box is higher, such as the normal temperature of 25 ℃, the second refrigerating system 2 is started, the refrigerating rate of the first refrigerating system is smaller than that of the second refrigerating system, and the second refrigerating system can enable the temperature in the box of the refrigerating equipment to be reduced 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 corresponding condensing fans of the first condenser 42 and the second condenser 52 are the same condensing fan 3, the operation of the condensing fan 3 is affected by the first compressor 41, i.e. 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, i.e. the second compressor 51 starts to operate, and 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 dual-system ultralow-temperature refrigeration system, the refrigeration equipment and the refrigeration control method provided by the utility model have the advantages that independent refrigeration cycles are respectively formed through the first refrigeration system and the second refrigeration system, so that different refrigeration temperature areas are realized, the first capillary tube 44 and the second capillary tube 54 have different flow rates, so that the first refrigeration system and the second refrigeration system can respectively reach different minimum refrigeration temperatures, the refrigeration requirements in different low-temperature areas are met, the flow rate through the first capillary tube 44 is smaller than the flow rate of the second capillary tube 54, the refrigeration rate of the first refrigeration system is smaller than the refrigeration rate of the second refrigeration system, and the minimum temperature which can be reached by the first refrigeration system is lower than the minimum temperature which can be reached by the second refrigeration system. The system has the advantages of stability and reliability, high refrigerating speed, low refrigerating temperature and diversified refrigerating temperature intervals.

Finally, it is noted that the above-mentioned embodiments illustrate rather than limit the utility model, and that those skilled in the art will be understood that various changes in form and details may be made therein without departing from the scope of the utility model as defined by the appended claims.

Claims

1. A dual-system ultralow temperature refrigeration system comprises a first refrigeration system and a second refrigeration system, and is characterized in that,

the first refrigerating system comprises a first compressor, a first condenser, an anti-dew pipe, a first dry filter, a first capillary tube and a first evaporator which are connected through pipelines;

the second refrigerating system comprises a second compressor, a second condenser, a second dry filter, a second capillary tube and a second evaporator which are connected through pipelines;

the first refrigeration system further comprises a first heat regenerator, the first heat regenerator comprises a first heat regenerator high-temperature pipe and a first heat regenerator low-temperature pipe, the first heat regenerator high-temperature pipe is connected between the first dry filter and the first capillary tube, and the first heat regenerator low-temperature pipe is connected between the first evaporator and the first compressor;

the second refrigerating system further comprises a second heat regenerator, the second heat regenerator comprises a second heat regenerator high-temperature pipe and a second heat regenerator low-temperature pipe, the second heat regenerator high-temperature pipe is connected between the second dry filter and the second capillary, and the second heat regenerator low-temperature pipe is connected between the second evaporator and the second compressor;

The flow rate of the first capillary is smaller than the flow rate of the second capillary.

2. A dual system ultra-low temperature refrigeration system according to claim 1, wherein,

the flow rate of the first capillary tube is as follows: 5-7L/min;

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

3. The dual system ultra-low temperature refrigeration system according to claim 1, wherein said first condenser and said second condenser together form a condenser assembly and share a condensing fan, said condensing fan being disposed on one side of said condenser assembly.

4. A dual system cryogenic refrigeration system as recited in claim 3, wherein the condensing conduit of the first condenser is disposed at least partially adjacent the condensing blower and the condensing conduit of the second condenser is disposed at least partially adjacent the condensing blower.

5. The dual system ultra-low temperature refrigeration system according to claim 3, wherein the condensation pipeline of the first condenser and the condensation pipeline of the second condenser are arranged in an up-down layered manner, the condensation fan comprises a plurality of fans, and the fans are arranged in an up-down two rows.

6. The dual system ultra-low temperature refrigeration system according to claim 3, wherein the condensing pipeline of the first condenser and the condensing pipeline of the second condenser are arranged in a front-back layered manner, and the condensing pipeline of the first condenser is arranged closer to the condensing fan.

7. A refrigeration device, comprising the dual-system ultralow temperature refrigeration system according to any one of claims 1 to 6 and a condensing fan for radiating heat from a first condenser and a second condenser in the dual-system ultralow temperature refrigeration system.

8. The refrigeration unit as recited in claim 7 further comprising a housing, a liner disposed within said housing, said first evaporator and said second evaporator being disposed on an outer surface of said liner.

9. The refrigeration unit as recited in claim 7 further comprising a housing, a liner disposed within said housing, said first evaporator and said second evaporator being disposed on left and right outer surfaces of said liner.

10. The refrigeration unit as recited in claim 7 further comprising a housing, a liner disposed within the housing, a foam layer defined between the housing and the liner, the liner including a liner bottom wall, the foam layer including a bottom foam layer disposed between the liner bottom wall and the housing, the first compressor, the first condenser, the second compressor, and the second condenser being disposed below the liner bottom wall;

the first evaporator and the second evaporator are arranged on the outer surface of the inner container, and the first heat regenerator and the second heat regenerator are arranged in the bottom foaming layer.

11. The refrigeration unit as recited in claim 10 wherein said first evaporator is a first coil extending along a height of said liner, said second evaporator is a second coil extending along a height of said liner, said first coil and said second coil being spaced apart and independently disposed from each other, and wherein said first regenerator and said second regenerator are spaced apart along a length of said liner within said bottom foam layer.