Refrigerator

Abstract

The utility model relates to the technical field of refrigeration equipment, and discloses a refrigerator. The refrigerator comprises a box body defining a compressor cabin; the refrigerating system comprises a fifth compressor and a sixth compressor, and the fifth compressor and the sixth compressor are located in the compressor cabin; the fifth compressor and the sixth compressor are arranged in the compressor cabin side by side, or the length direction of the fifth compressor and the length direction of the sixth compressor are arranged in a crossed mode. In this way, the height of the compressor cabin is not increased, and two compressors do not need to be placed in two compressor cabins respectively. And therefore, the storage space of the liner occupied by the compressor cabin can be reduced, and the storage space and storage experience of the refrigerator are improved.

Description

Technical Field

[0001] The present application relates to the technical field of refrigeration equipment, for example, to a refrigerator. Background Art

[0002] At present, with the improvement of people's living standards, the freshness of food storage has received more and more attention, especially the freshness storage of high-end ingredients. Low-temperature storage, especially storage in a temperature zone below -50℃, can greatly improve the quality and storage period of food. For example, the taste of wild yellow croaker will obviously decrease after being stored in a regular refrigerator for one month, but it will still taste fresh after being stored at -60℃ for half a year.

[0003] A horizontal refrigerator is disclosed in the related technology. The horizontal refrigerator includes a high-temperature refrigeration cycle circuit, including a high-temperature compressor and an evaporating tube; a low-temperature refrigeration cycle circuit, including a low-temperature compressor and a condensing tube, and the evaporating tube and the condensing tube are thermally connected; a cabinet body, including a first compressor compartment, a second compressor compartment, a first inner liner and a second inner liner arranged at a transverse interval, the first inner liner encloses a first storage compartment, and the second inner liner encloses a second storage compartment, the first compressor compartment is located below the first inner liner, the high-temperature compressor is arranged in the first compressor compartment, the second compressor compartment is located below the second inner liner, the low-temperature compressor is arranged in the second compressor compartment, the high-temperature refrigeration cycle circuit provides cooling for the first storage compartment, and the low-temperature refrigeration cycle circuit provides cooling for the second storage compartment.

[0004] In the process of implementing the embodiments of the present disclosure, it is found that there are at least the following problems in the related art:

[0005] The horizontal freezer in the related art is provided with two press chambers and two inner tanks to realize low-temperature storage of the freezer. However, the two press chambers occupy the storage space of the inner tank, which still causes the storage space of the inner tank to become smaller. Moreover, two press chambers are respectively provided corresponding to the two inner tanks, which makes it impossible for the freezer to store larger items, resulting in poor storage effect of the freezer.

[0006] It should be noted that the information disclosed in the above background technology section is only used to enhance the understanding of the background of the present application, and therefore may include information that does not constitute the prior art known to ordinary technicians in the field. Utility Model Content

[0007] In order to provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. The summary is not an extensive review, nor is it intended to identify key / critical components or delineate the scope of protection of these embodiments, but rather serves as a prelude to the detailed description that follows.

[0008] The disclosed embodiment provides a refrigerator to achieve low-temperature storage in the refrigerator while increasing the storage space of the refrigerator, thereby improving the storage effect and storage experience.

[0009] An embodiment of the present disclosure provides a refrigerator, which includes: a box body, which defines a compressor compartment; a refrigeration system, which includes a fifth compressor and a sixth compressor, and the fifth compressor and the sixth compressor are located in the compressor compartment; wherein the fifth compressor and the sixth compressor are arranged side by side in the compressor compartment, or the length direction of the fifth compressor and the length direction of the sixth compressor are arranged crosswise.

[0010] The refrigerator provided in the embodiments of the present disclosure can achieve the following technical effects:

[0011] In the refrigerator of the disclosed embodiment, the fifth compressor and the sixth compressor are both arranged in the same compressor cabin, and the two compressors can be arranged side by side or crosswise according to the size of the compressor cabin, which does not increase the height of the compressor cabin, and does not need to set up two compressor cabins to place the two compressors respectively. In addition, the storage space of the inner liner occupied by the compressor cabin can be reduced, and larger items can be placed, thereby improving the storage space and storage experience of the refrigerator.

[0012] The above general description and the following description are exemplary and explanatory only and are not intended to limit the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0013] One or more embodiments are exemplarily described by corresponding drawings, which do not limit the embodiments. Elements with the same reference numerals in the drawings are shown as similar elements, and the drawings do not constitute a scale limitation, and wherein:

[0014] Figure 1 is a structural schematic diagram of a cascade refrigeration system provided by an embodiment of the present disclosure;

[0015] Figure 2 is a structural schematic diagram of another cascade refrigeration system provided by an embodiment of the present disclosure;

[0016] Figure 3 is a structural schematic diagram of another cascade refrigeration system provided by an embodiment of the present disclosure;

[0017] Figure 4 is a structural schematic diagram of another cascade refrigeration system provided by an embodiment of the present disclosure;

[0018] Figure 5 is a partial structural diagram of a refrigeration device provided by an embodiment of the present disclosure;

[0019] Figure 6 is a partial structural schematic diagram of another refrigeration device provided by an embodiment of the present disclosure;

[0020] Figure 7 is a partial structural schematic diagram of another refrigeration device provided by an embodiment of the present disclosure;

[0021] Figure 8 is a partial structural schematic diagram of another refrigeration device provided by an embodiment of the present disclosure;

[0022] Fig. 9 is a partial structural schematic diagram of another refrigeration device provided by an embodiment of the present disclosure;

[0023] Fig.10 is a partial structural schematic diagram of another refrigeration device provided by an embodiment of the present disclosure;

[0024] Fig.11 is a partial structural schematic diagram of another refrigeration device provided by an embodiment of the present disclosure;

[0025] Fig.12 is a partial structural schematic diagram of another refrigeration device provided by an embodiment of the present disclosure;

[0026] Fig.13 is a partial structural schematic diagram of another refrigeration device provided by an embodiment of the present disclosure;

[0027] Fig.13a is a partial structural schematic diagram of another refrigeration device provided by an embodiment of the present disclosure;

[0028] Fig.14 is a partial structural schematic diagram of another refrigeration device provided by an embodiment of the present disclosure;

[0029] Fig.14a yes Fig.14 Cross-sectional view along the N-N' direction;

[0030] Fig.14b yes Fig.14 Cross-sectional view along the M-M' direction;

[0031] Fig.14c yes Fig.14b A partial enlarged schematic diagram of the middle part;

[0032] Fig.15 is a schematic diagram of the matching structure of a compressor base plate and a compressor provided by an embodiment of the present disclosure;

[0033] Fig.16 is a schematic diagram of the matching structure of another compressor base plate and a compressor provided by an embodiment of the present disclosure;

[0034] Fig.17 is a partial structural schematic diagram of another refrigeration device provided by an embodiment of the present disclosure;

[0035] Fig.18 is a schematic diagram of a structure of a reinforcing iron provided by an embodiment of the present disclosure;

[0036] Fig.19 is a structural schematic diagram of a compressor base plate provided by an embodiment of the present disclosure;

[0037] Fig. 20 is a structural schematic diagram of another compressor base plate provided by an embodiment of the present disclosure;

[0038] Fig.21 It is a structural schematic diagram of another cascade refrigeration system provided in an embodiment of the present disclosure.

[0039] Reference numerals:

[0040] 10. High-temperature refrigeration cycle; 101. Evaporation unit; 102. High-temperature compressor; 103. First pipeline; 104. High-temperature condenser; 105. High-temperature throttling device; 1051. First capillary tube; 1052. Second capillary tube; 106. Second pipeline; 107. Fifth pipeline; 108. High-temperature evaporator; 109. Solenoid valve; 20. Low-temperature refrigeration cycle; 201. Condensation unit; 202 , low temperature compressor; 203, third pipeline; 204, low temperature evaporator; 205, fourth pipeline; 206, low temperature throttling device; 30, evaporative condenser; 301, first regenerator; 3011, first regenerator pipe group; 3012, second regenerator pipe group; 302, second regenerator; 303, third regenerator; 304, return air pipe group; 305, first filter dryer; 306, second filter dryer; 307 , third drying filter; 308, precooling pipe; 401, shell; 4011, first welding hole; 4012, air outlet; 402, liner; 403, compressor cabin; 50, reinforcing iron; 501, frame; 5011, first frame; 5012, second frame; 502, vertical beam; 503, first cross beam; 504, second cross beam; 60, compressor bottom plate; 601, first bottom plate; 6011, first reinforcing rib; 6012, first installation area; 602, second bottom plate; 6021, second reinforcing rib; 6022, second installation area; 70, partition; 80, reinforcing rib; 801, first rib segment; 802, second rib segment; 803, third rib segment; 804, fourth rib segment; 805, fifth rib segment; 806, sixth rib segment; 807, seventh rib segment; 808, eighth rib segment; 809, first placement position; 810, second placement position. DETAILED DESCRIPTION

[0041] In order to be able to understand the features and technical contents of the embodiments of the present disclosure in more detail, the implementation of the embodiments of the present disclosure is described in detail below in conjunction with the accompanying drawings. The attached drawings are for reference only and are not used to limit the embodiments of the present disclosure. In the following technical description, for the convenience of explanation, a full understanding of the disclosed embodiments is provided through multiple details. However, one or more embodiments can still be implemented without these details. In other cases, to simplify the drawings, well-known structures and devices can be simplified for display.

[0042] The terms "first", "second", etc. in the specification and claims of the disclosed embodiments and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the terms used in this way can be interchanged where appropriate to describe the disclosed embodiments here. In addition, the terms "including" and "having" and any variations thereof are intended to cover non-exclusive inclusions.

[0043] In the embodiments of the present disclosure, the terms "upper", "lower", "inside", "middle", "outside", "front", "back" and the like indicate directions or positional relationships based on the directions or positional relationships shown in the accompanying drawings. These terms are mainly intended to better describe the embodiments of the present disclosure and their embodiments, and are not intended to limit the indicated devices, elements or components to have a specific direction, or to be constructed and operated in a specific direction. Moreover, in addition to being used to indicate directions or positional relationships, some of the above terms may also be used to indicate other meanings. For example, the term "upper" may also be used to indicate a certain dependency or connection relationship in certain circumstances. For those of ordinary skill in the art, the specific meanings of these terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0044] In addition, the terms "disposed", "connected", and "fixed" should be understood in a broad sense. For example, "connected" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection, or an electrical connection; it can be a direct connection, or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, elements, or components. For those of ordinary skill in the art, the specific meanings of the above terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0045] Unless otherwise stated, the term "plurality" means two or more.

[0046] The term "and / or" is a description of the association relationship between objects, indicating that three relationships can exist. For example, A and / or B means: A or B, or, A and B.

[0047] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present disclosure may be combined with each other.

[0048] Combination Figures 1 to 21 As shown, the embodiment of the present disclosure provides a refrigeration device, which can provide a low-temperature environment to store food, medicine or other items at low temperatures. For example, the refrigeration device can be a refrigerator, a freezer, a freezer, a biomedical refrigeration device or other refrigeration device.

[0049] The refrigeration equipment includes a cascade refrigeration system, which may be a two-stage cascade cycle system, a three-stage cascade cycle system, or a four-stage cascade cycle system, and the number of cascade stages is not specifically limited. This embodiment is only exemplified by a cascade refrigeration system with a two-stage cascade cycle system, and those skilled in the art should be fully capable of expanding on this basis.

[0050] like Figures 1 to 4 As shown, the embodiment of the present disclosure provides a cascade refrigeration system, which includes a high-temperature refrigeration cycle circuit 10 and a low-temperature refrigeration cycle circuit 20. A first refrigerant circulates in the high-temperature refrigeration cycle circuit 10, and a second refrigerant circulates in the low-temperature refrigeration cycle circuit 20. The high-temperature refrigeration cycle circuit includes a high-temperature compressor 102, a high-temperature condenser 104, a high-temperature throttling device 105, and an evaporation portion 101, which are sequentially connected to the same circuit along the flow direction of the first refrigerant; the low-temperature refrigeration cycle circuit includes a low-temperature compressor 202, a condensation portion 201, a low-temperature throttling device 206, and a low-temperature evaporator 204, which are sequentially connected to the same circuit along the flow direction of the second refrigerant. The evaporation portion and the condensation portion form an evaporation condenser 30, so that the first refrigerant in the evaporation portion can exchange heat with the second refrigerant in the condensation portion.

[0051] Optionally, the high-temperature refrigeration cycle circuit 10 includes a high-temperature compressor 102, a first pipeline 103, a high-temperature condenser 104, a high-temperature throttling device 105, a second pipeline 106 and an evaporation portion 101, which are sequentially connected to the same circuit along the first refrigerant flow direction. The first pipeline 103 is connected between the outlet of the evaporation portion 101 and the inlet of the high-temperature compressor 102; the high-temperature condenser 104 is connected to the outlet of the high-temperature compressor 102; the inlet of the high-temperature throttling device 105 is connected to the outlet of the high-temperature condenser 104, and the outlet of the high-temperature throttling device 105 is connected to the inlet of the evaporation portion 101; the second pipeline 106 is connected between the outlet of the high-temperature condenser 104 and the inlet of the high-temperature throttling device 105.

[0052] Optionally, the low-temperature refrigeration cycle 20 includes a low-temperature compressor 202, a third pipeline 203, a low-temperature evaporator 204, a fourth pipeline 205, a low-temperature throttling device 206 and a condensing portion 201 which are sequentially connected to the same circuit along the flow direction of the second refrigerant. The condensing portion 201 and the evaporating portion 101 form an evaporative condenser 30, and the second refrigerant in the condensing portion 201 can exchange heat with the first refrigerant in the evaporating portion 101; the third pipeline 203 is connected between the outlet of the low-temperature compressor 202 and the inlet of the condensing portion 201; the inlet of the low-temperature evaporator 204 is connected to the outlet of the condensing portion 201; the fourth pipeline 205 is connected between the outlet of the low-temperature evaporator 204 and the inlet of the low-temperature compressor 202; the inlet of the low-temperature throttling device 206 is connected to the outlet of the condensing portion 201, and the outlet of the low-temperature throttling device 206 is connected to the low-temperature evaporator 204.

[0053] In the disclosed embodiment, the evaporation part 101 in the high-temperature refrigeration cycle 10 can exchange heat with the evaporation part 101 of the low-temperature refrigeration system, so that the first refrigerant in the high-temperature refrigeration cycle 10 can be used to cool the second refrigerant in the low-temperature refrigeration cycle 20, that is, the first refrigerant in the evaporation part 101 absorbs the heat of the second refrigerant in the condensation part 201 to achieve the cooling of the second refrigerant, and then the cooled second refrigerant is further cooled by the low-temperature refrigeration cycle 20, thereby achieving the low temperature of the refrigeration equipment. The low-temperature throttling part 206 and the high-temperature throttling part 105 can both be capillaries or electronic expansion valves.

[0054] Optionally, the evaporation part 101 includes an evaporation tube, and the condensation part 201 includes a condensation tube, and the evaporation tube and the condensation tube are close to each other (fitted or close to each other) to achieve heat exchange between the evaporation tube and the condensation tube. Optionally, the evaporation part 101 and the condensation part 201 can also be in the form of a sleeve to achieve heat exchange.

[0055] Optionally, the high-temperature refrigeration cycle 10 further includes a third drying filter 307, which is located between the high-temperature condenser 104 and the high-temperature throttling member 105. The low-temperature refrigeration cycle 20 further includes a second drying filter 306, which is located between the condensing portion 201 and the low-temperature throttling member 206, and is used to dry and filter the low-temperature refrigerant flowing out of the condensing portion 201.

[0056] In this embodiment, the refrigerant is cooled and cooled to become a low-temperature liquid refrigerant after flowing through the condensation section 201 or the high-temperature stage condenser 104. In this state, the compressor lubricating oil and the refrigerant medium have good miscibility, and the dry filter intercepts and adsorbs less compressor lubricating oil, thereby reducing the risk of oil blockage, and the dry filter has a better adsorption and interception effect on other impurities.

[0057] Alternatively, if Figure 1 As shown, the high-temperature stage throttling element 105 is connected or in contact with the first pipeline 103 to form a return air pipe group 304, and the return air pipe group 304 is used to exchange heat between the first refrigerant in the high-temperature stage throttling element 105 and the first refrigerant in the first pipeline 103. In this way, after the first refrigerant after heat exchange between the evaporation part 101 and the condensation part 201 flows along the first pipeline 103 to the return air pipe group 304, the first refrigerant in the first pipeline 103 exchanges heat with the high-temperature stage throttling element 105 to become a low-pressure and normal-temperature gaseous refrigerant, and then enters the high-temperature stage compressor 102 to complete the cycle. Here, the return air pipe group 304 can cool down the first refrigerant flowing through the high-temperature stage throttling element 105, thereby reducing the temperature of the first refrigerant flowing into the evaporation part 101, and improving the heat exchange efficiency in the evaporative condenser 30.

[0058] The first refrigerant in the high-temperature refrigeration cycle loop 10 is pressurized by the high-temperature compressor 102 to form a high-temperature and high-pressure superheated gas. After entering the high-temperature condenser 104, it is condensed into a supercooled liquid or a saturated liquid or a gas-liquid two-phase. Then, after passing through the third drying filter 307 to filter out moisture and impurities, it enters the high-temperature throttling device 105 of the return air pipe group 304 for throttling and cooling. After throttling by the high-temperature throttling device 105, the first refrigerant becomes a low-temperature and low-pressure state and enters the cold end pipe of the evaporative condenser 30 to release the cold. After that, it returns to the return air pipe group 304 along the first pipeline 103, and after heat exchange with the high-temperature throttling device 105, it becomes a low-pressure and normal-temperature refrigerant gas, and enters the high-temperature compressor 102 to complete the cycle.

[0059] The second refrigerant in the low-temperature refrigerant circulation loop is compressed and pressurized by the low-temperature compressor 202 to form a high-temperature and high-pressure superheated gas. After passing through the third pipeline 203, it enters the condenser of the evaporative condenser 30 to dissipate heat and become a supercooled liquid or a saturated liquid or a gas-liquid two-phase. Then, it enters the low-temperature throttling device 206 to throttle to a low-temperature and low-pressure state and enters the low-temperature evaporator 204 for refrigeration, so that low-temperature storage below -45°C can be achieved. After the second refrigerant absorbs heat in the low-temperature evaporator 204 and becomes a superheated gas, it is sucked into the low-temperature compressor 202 to complete the refrigeration cycle. Optionally, the high-temperature throttling device 105 and the first pipeline 103 use close contact heat exchange or sleeve heat exchange to exchange heat.

[0060] In some optional embodiments, such as Figure 2 As shown, the third pipeline 203 and the fourth pipeline 205 are connected or in contact with each other and form a first regenerator 301 , and the first regenerator 301 is used to exchange heat between the second refrigerant in the third pipeline 203 and the second refrigerant in the fourth pipeline 205 .

[0061] In the disclosed embodiment, the third pipe 203 in the first regenerator 301 can be regarded as the hot end of the first regenerator 301, and the fourth pipe 205 in the first regenerator 301 can be regarded as the cold end of the first regenerator 301. The second refrigerant in the low-temperature refrigeration cycle is compressed and pressurized by the low-temperature compressor 202 to form a high-temperature and high-pressure superheated gas. After flowing into the first regenerator 301 through the third pipe 203, it dissipates heat in the first regenerator 301, and part of the second refrigerant becomes a gas-liquid two-phase state. Then, the second refrigerant after heat dissipation enters the condenser of the evaporative condenser 30, dissipates heat, and becomes a supercooled liquid or a saturated liquid or a gas-liquid two-phase state. Then, it enters the low-temperature throttling device 206 to throttle to a low-temperature and low-pressure state and enters the low-temperature evaporator 204 for refrigeration, so that low-temperature storage below -45°C can be achieved. After the second refrigerant absorbs heat in the low-temperature evaporator 204, it flows into the cold end of the first regenerator 301 through the fourth pipeline 205, absorbs the heat of the hot end to become superheated gas, and is sucked into the low-temperature compressor 202 to complete the refrigeration cycle. Here, the setting of the first regenerator 301 can reduce the temperature difference between the fourth pipeline 205 and the ambient temperature, thereby solving the problem that the fourth pipeline 205 of the low-temperature refrigeration cycle 20 is easy to frost, especially the problem that the fourth pipeline 205 is easy to frost in the compressor cabin 403.

[0062] Optionally, the third pipeline 203 and the fourth pipeline 205 perform heat exchange by contact heat exchange or in the form of sleeve heat exchange.

[0063] Optionally, the cascade refrigeration system further includes a first filter dryer 305, which is disposed in the third pipeline 203 and is located between the outlet of the first regenerator 301 and the inlet of the evaporative condenser 30. Here, the first filter dryer 305 can filter the second refrigerant flowing out of the first regenerator 301 after heat exchange before flowing into the evaporative condenser 30, thereby reducing impurities flowing into the condensation part 201 and improving the heat exchange efficiency of the evaporative condenser 30.

[0064] like Figure 3 As shown, optionally, the low-temperature refrigeration cycle circuit 20 also includes a precooling pipe 308, and the precooling pipe 308 is connected between the outlet of the third pipeline 203 and the inlet of the condensation part.

[0065] In the disclosed embodiment, the precooling pipe 308 is used as a "condenser", which can be used to cool the low-temperature refrigerant output by the low-temperature compressor 202, thereby reducing the heat load of the low-temperature refrigerant subsequently output to the evaporative condenser 30, so that the low-temperature refrigerant output from the evaporative condenser 30 can reach a lower temperature. The second refrigerant in the low-temperature refrigerant circulation loop is compressed and pressurized by the low-temperature compressor 202 to form a high-temperature and high-pressure superheated gas, which flows into the precooling pipe 308 along the third pipeline 203 for precooling, so that the temperature of the high-temperature and high-pressure superheated gas is reduced to close to the ambient temperature, thereby improving the subsequent heat exchange efficiency of the second refrigerant.

[0066] Alternatively, if Figure 3 As shown, the low-temperature refrigeration cycle 20 includes a precooling pipe 308, a hot end of the first regenerator 301 and a first filter dryer 305, which are sequentially arranged along the flow direction of the second refrigerant. The precooling pipe 308 is located upstream of the first regenerator 301. After the second refrigerant flowing through the precooling pipe 308 flows into the first regenerator 301 through the third pipeline 203, it dissipates heat in the first regenerator 301, and part of the second refrigerant becomes a gas-liquid two-phase state. Then, the second refrigerant after heat dissipation is filtered by the first filter dryer 305 and flows into the condenser of the evaporative condenser 30. After heat dissipation, it becomes a supercooled liquid or a saturated liquid or a gas-liquid two-phase state, and then enters the low-temperature throttling device 206 to throttle to a low temperature and low pressure state and enter the low-temperature evaporator 204 for refrigeration, so that low-temperature storage below -45°C can be achieved. After absorbing heat in the low-temperature evaporator 204, the second refrigerant flows into the cold end of the first regenerator 301 through the fourth pipeline 205, absorbs the heat of the hot end and becomes a superheated gas, and is sucked into the low-temperature compressor 202 to complete the refrigeration cycle.

[0067] It should be noted that the precooling pipe can also be located in the middle of the third pipeline, that is, the second refrigerant flowing out of the outlet of the low-temperature compressor can first flow into the third pipeline 203, and then flow to the condensation part through the precooling pipe 308. The improvement of the precooling pipe 308 being located in the middle of the third pipeline is the same as the improvement of the precooling pipe being located at the entrance of the third pipeline in the present application, and will not be described again.

[0068] In some further optional embodiments, the drying filter includes a fourth drying filter, which is arranged in the pipeline between the precooling pipe 308 and the first reheater 301 of the low-temperature circulation loop 20, and is used to dry and filter the low-temperature refrigerant medium flowing out of the precooling pipe 308.

[0069] Here, the precooling pipe 308 is arranged in a space such as a compressor compartment that is easy to exchange heat with the external environment. In this embodiment, the fourth drying filter is located downstream of the flow path of the precooling pipe 308. It can also be arranged in the above-mentioned compressor compartment and other spaces to enable more convenient maintenance and replacement of the drying filter.

[0070] Based on the above embodiments of various layout forms of drying filters, the cascade refrigeration system provided in the present application can be provided with one or more drying filters, and the specific arrangement position of each drying filter can refer to any one of the embodiments shown in the above embodiments.

[0071] like Figure 4 As shown, in some other optional embodiments, the second pipeline 106 is in contact with or connected to the fourth pipeline 205 to form a second regenerator 302, and the second regenerator 302 is used to exchange heat between the first refrigerant in the second pipeline 106 and the second refrigerant in the fourth pipeline 205.

[0072] In the disclosed embodiment, the second pipe 106 in the second regenerator 302 is equivalent to the hot end of the second regenerator 302, and the fourth pipe 205 in the second regenerator 302 is equivalent to the cold end of the second regenerator 302. In this way, the second refrigerant in the high-temperature refrigeration cycle 10 flows through the high-temperature condenser 104 to become a supercooled liquid or a saturated liquid or a gas-liquid two-phase, and then enters the second regenerator 302, and after heat exchange with the second refrigerant in the fourth pipe 205 of the low-temperature refrigeration cycle 20, it flows to the high-temperature throttling device 105. In this way, the condensation temperature of the second refrigerant can be further reduced or the degree of supercooling can be increased. The second refrigerant after cooling down in the second regenerator 302 flows through the return air pipe group 304, and then exchanges heat with the high-temperature throttling device 105 to become a low-pressure and normal-temperature refrigerant gas, and enters the high-temperature compressor 102 to complete the cycle.

[0073] Optionally, the second pipeline 106 and the fourth pipeline 205 perform heat exchange by contact heat exchange or in the form of sleeve heat exchange.

[0074] Alternatively, if Figure 4 As shown, the low-temperature refrigeration cycle 20 includes a second regenerator 302, a precooling pipe 308 and a second drying filter 306. The precooling pipe 308 is arranged in the third pipeline 203, and the second drying filter 306 is located between the condensation part 201 and the low-temperature throttling device 206.

[0075] In the disclosed embodiment, the second refrigerant in the low-temperature refrigeration cycle is compressed and pressurized by the low-temperature compressor 202 to form a high-temperature and high-pressure superheated gas, which flows into the precooling pipe 308 along the third pipeline 203 for precooling, so that the temperature of the high-temperature and high-pressure superheated gas is reduced to close to the ambient temperature. After the heat dissipation, the second refrigerant enters the condenser of the evaporative condenser 30 and dissipates heat to become a supercooled liquid or a saturated liquid or a gas-liquid two-phase, and then enters the second drying filter 306 for filtration and enters the low-temperature throttling device 206 to throttle to a low-temperature and low-pressure state and enters the low-temperature evaporator 204 for refrigeration. The second drying filter 306 can avoid the blockage of the low-temperature throttling device 206. In this way, low-temperature storage below -45°C can be achieved. After the second refrigerant absorbs heat from the low-temperature evaporator 204, it flows into the cold end of the second regenerator 302 through the fourth pipeline 205. After absorbing the heat of the hot end and becoming a superheated gas, the problem of frost on the fourth pipeline 205 in the compressor cabin 403 can be solved, and then the second refrigerant is sucked into the low-temperature compressor 202 to complete the refrigeration cycle.

[0076] like Fig.21 As shown, in some other optional embodiments, the cascade refrigeration system further includes a fifth pipeline 107 and a high-temperature stage evaporator 108, the fifth pipeline 107 is connected between the outlet of the high-temperature stage throttling member 105 and the inlet of the evaporation portion 101, and the high-temperature stage evaporator 108 is connected between the outlet of the high-temperature stage throttling member 105 and the first pipeline 103. Optionally, there are multiple high-temperature stage throttling members 105, and the multiple high-temperature stage throttling members 105 include a first capillary tube 1051 and a second capillary tube 1052, and the first capillary tube 1051 and the second capillary tube 1052 are arranged in parallel, wherein the first capillary tube 1051 is connected to the fifth pipeline 107, and the second capillary tube 1052 is connected to the high-temperature stage evaporator 108. The cascade refrigeration system further includes a solenoid valve 109, which is connected between the second pipeline 106 and the first capillary tube 1051 and the second capillary tube 1052, and the solenoid valve 109 is used to control the connection between the first capillary tube 1051 and the second capillary tube 1052 and the second pipeline 106. Optionally, the first capillary tube 1051, the second capillary tube 1052 and the first pipeline 103 form a return air pipe group 304.

[0077] In the disclosed embodiment, the second refrigerant in the high-temperature refrigeration cycle 10 flows through the high-temperature condenser 104 to become a supercooled liquid or a saturated liquid or a gas-liquid two-phase, then enters the return pipe group 304, and respectively enters the two parallel high-temperature throttling devices 105 of the return pipe group 304 to cool down, and then respectively flows to the high-temperature evaporator 108 and the evaporation part 101 to release the cold and then returns to the return pipe group 304. After heat exchange with the high-temperature throttling device 105 in the return pipe group 304, it becomes a low-pressure and normal-temperature refrigerant gas, and enters the high-temperature compressor 102 to complete the cycle. Through the arrangement of the high-temperature evaporator 108, the solenoid valve 109 and the parallel high-temperature throttling device 105, the high-temperature refrigeration cycle 10 can be operated in cascade or separately, so that when the cascade refrigeration system is started, the flow path of the high-temperature refrigeration cycle 10 can be adjusted to improve the startup stability and reduce the noise. With the cascade refrigeration system of the embodiment of the present disclosure, when it is determined that the actual temperature of the storage chamber meets the startup conditions, the low-temperature refrigeration cycle can be started first for refrigeration, and the low-temperature refrigeration demand can be met by repeatedly starting and stopping the low-temperature refrigeration cycle. During the above-mentioned time period when the low-temperature refrigeration cycle is working, the high-temperature refrigeration cycle is temporarily in a shutdown state or operates alone without exchanging heat with the low-temperature refrigeration system. In this way, the overall working noise of the refrigeration equipment can be greatly reduced, so that the refrigeration equipment has more diverse application scenarios.

[0078] Optionally, the high-temperature refrigeration cycle 10 includes a third filter dryer 307, which is located between the high-temperature condenser 104 and the high-temperature throttling member 105 and can filter the refrigerant flowing out of the high-temperature condenser 104. Optionally, the low-temperature refrigeration cycle 20 includes a first regenerator and a first filter dryer 305, which have the same functions as described above and are not described in detail herein.

[0079] Optionally, the evaporation part 101 and the condensation part 201 form an evaporative condenser 30. When the refrigeration device includes a first regenerator or a second regenerator 302 (collectively referred to as a regenerator), the heat exchange capacity of the regenerator is less than the heat exchange capacity of the evaporative condenser 30. Specifically, the length of the evaporative condenser 30 is greater than the length of the regenerator. According to experimental data, this can reduce the operating pressure of the low-temperature refrigeration cycle 20. When the refrigeration device is pulled down or powered on for the first time, the regenerator has limited effect, the second refrigerant is completely evaporated in the low-temperature evaporator 204, and the cooling input of the regenerator is too low. The evaporative condenser 30 can provide sufficient precooling capacity to ensure that the pressure is controllable.

[0080] Optionally, the first refrigerant and the second refrigerant both include hydrocarbons and / or hydrofluoroolefins with a critical pressure ≤ 4.7 MPa. Critical pressure refers to the pressure of a substance when it is in a critical state, that is, the minimum pressure required to liquefy a gas at a critical temperature. It is also the saturated vapor pressure of a liquid at a critical temperature. At a critical temperature and a critical pressure, the molar volume of a substance is called a critical molar volume. The state at a critical temperature and a critical pressure is called a critical state.

[0081] In the disclosed embodiment, the first refrigerant and the second refrigerant are both hydrocarbon and / or hydrofluoroolefin refrigerants with a critical pressure ≤4.7Mpa. This type of refrigerant has a relatively low critical pressure and can achieve a gas-liquid state conversion when the system pressure is relatively low. In this way, the system can operate at a relatively low pressure, thereby reducing the operating noise. At the same time, the boiling point of hydrocarbon and / or hydrofluoroolefin refrigerants with a critical pressure ≤4.7Mpa can achieve a low temperature. In this way, the operating pressure of the cascade refrigeration system can be reduced while achieving low temperature and noise reduction functions, so that the low-temperature refrigeration equipment can meet the noise requirements of household use.

[0082] Optionally, the critical pressure of the first refrigerant is ≤4 MPa. This can further reduce the pressure in the high-temperature refrigeration cycle 10, thereby reducing noise.

[0083] Optionally, the first refrigerant is one or more of R600, R600a, R290, R1270, R1243zf, and R1234yf; and / or, the second refrigerant is one or more of R290 and R1270, or the second refrigerant is one of R290 and R1270 and one or more of the first refrigerants. Optionally, the second refrigerant can be a mixed refrigerant of one of R290 and R1270 and one or more of R600, R600a, R1243zf, and R1234yf.

[0084] It can be understood that the second refrigerant can be only R290 or R1270, a mixed refrigerant of R290 and R1270, a mixed refrigerant of R290 with one or more of R600, R1243zf, and R1234yf, or a mixed refrigerant of R1270 with one or more of R600, R1243zf, and R1234yf.

[0085] In the disclosed embodiment, the first refrigerant and the second refrigerant use the above-mentioned components, which can reduce the pressure difference, reduce the requirements for the compressor model, and reduce noise to achieve low-noise operation.

[0086] In the embodiment of the present disclosure, as shown in Table 1, the critical pressure of various refrigerants is less than 4.7Mpa. The boiling point temperature of the second refrigerant is less than or equal to the boiling point temperature of the first refrigerant, which facilitates the evaporative condenser 30 to achieve heat exchange between the first refrigerant and the second refrigerant. Using the refrigerant type of the embodiment of the present disclosure, when the cascade refrigeration system uses an R600a compressor, the operating noise of the entire system is between 30 and 38dB (A), which greatly reduces the noise of the system operation.

[0087] Table 1

[0088]

[0089] Optionally, the first refrigerant of the high-temperature refrigeration cycle circuit 10 is a single refrigerant, and / or the second refrigerant of the low-temperature refrigeration cycle circuit 20 is a single refrigerant.

[0090] For example, the first refrigerant in the high temperature refrigeration cycle 10 may be any one of R600, R600a, R290, R1270, R1243zf, and R1234yf. The second refrigerant in the low temperature refrigeration cycle 20 may be any one of R290 and R1270.

[0091] Optionally, the first refrigerant of the high-temperature refrigeration cycle 10 is a mixed refrigerant, and / or the second refrigerant of the low-temperature refrigeration cycle 20 is a mixed refrigerant. When the second refrigerant of the low-temperature refrigeration cycle 20 is a mixed refrigerant, the proportion of R290 or R1270 is greater than 40%. This enables the system to operate at a lower operating pressure.

[0092] Optionally, when the second refrigerant is R290 and / or R1270, the high-pressure side pressure range of the low-temperature refrigeration cycle circuit 20 in a stable operating state is configured to be 0.1Mpa-0.9Mpa, and the low-pressure side pressure range of the low-temperature refrigeration cycle circuit 20 in a stable operating state is configured to be 0.015Mpa-0.1Mpa.

[0093] The high-pressure side in the low-temperature refrigeration cycle 20 refers to the portion between the discharge port of the low-temperature compressor 202 and the upstream of the suction port of the low-temperature throttling device 206 in the low-temperature refrigeration cycle 20 in the flow direction of the second refrigerant. The low-pressure side in the low-temperature refrigeration cycle 20 refers to the portion between the discharge port downstream of the low-temperature throttling device 206 and the suction port of the low-temperature compressor 202 in the flow direction of the second refrigerant.

[0094] In the embodiment of the present disclosure, the low-temperature refrigeration cycle 20 is set with the above parameters, which can reduce the pressure ratio and pressure difference. When the low-temperature refrigeration cycle 20 is running, the low-temperature compressor 202 in the loop can have a lower suction pressure and a lower exhaust pressure. At this time, the compressor vibration is low and the efficiency is high, thereby achieving a low noise effect. The high-pressure side of the low-temperature refrigeration cycle 20 includes a third pipeline 203, a condensing part 201, and a first drying filter 305. It can be seen from Table 2 that the pressure at the high-pressure end of the low-temperature refrigeration cycle of the conventional external cascade refrigeration system is mostly greater than 0.9Mpa, so the noise generated is relatively large. The second refrigerant in the low-temperature refrigeration cycle 20 of the present disclosure embodiment adopts R290 or R1270 or a mixed refrigerant of the two. After precooling by the evaporative condenser 30, the high-pressure side and low-pressure side pressures of the low-temperature cycle refrigeration circuit can be configured within the above range, which can reduce the operating pressure in the low-temperature refrigeration cycle, thereby making the noise of the low-temperature compressor 202 controllable between 30 and 45dB (A).

[0095] Table 2

[0096]

[0097] Optionally, the high-pressure side pressure range of the low-temperature refrigeration cycle circuit 20 in a stable operating state is configured to be 0.2Mpa-0.9Mpa.

[0098] For example, the high-pressure side pressure range of the low-temperature refrigeration cycle circuit 20 in a stable operating state is configured to be 0.1 MPa, 0.2 MPa, 0.3 MPa, 0.4 MPa, 0.5 MPa, 0.6 MPa, 0.7 MPa, 0.8 MPa, and 0.9 MPa.

[0099] As shown in Table 3, the low-pressure side pressure range of the low-temperature refrigeration cycle circuit 20 in a stable operating state is configured to be 0.015Mpa-0.1Mpa, so that the temperature inside the refrigeration equipment can reach below -55°C, and can even reach -60°C and -70°C, thereby achieving better low-temperature storage effects.

[0100] Optionally, the low-pressure side pressure range of the low-temperature refrigeration cycle 20 in a stable operating state is configured to be 0.02Mpa-0.05Mpa. This can further reduce the temperature in the box and improve the freshness of the stored food.

[0101] Table 3

[0102]

[0103] For example, the low-pressure side pressure range of the low-temperature refrigeration cycle circuit 20 in a stable operating state is configured to be 0.015Mpa, 0.018Mpa, 0.02Mpa, 0.025Mpa, 0.03Mpa, 0.04Mpa, 0.05Mpa, 0.06Mpa, 0.08Mpa, 0.1Mpa, etc.

[0104] In some optional embodiments, when the first refrigerant is one or more of R600a and / or R600, R1243zf, and R1234yf, the low-pressure side pressure range of the high-temperature refrigeration cycle circuit 10 in a stable operating state is configured to be lower than one atmosphere; when the second refrigerant is R290 and / or R1270, the low-pressure side pressure range of the low-temperature refrigeration cycle circuit 20 in a stable operating state is configured to be lower than one atmosphere.

[0105] In the disclosed embodiment, the ambient atmospheric pressure is usually 0.101Mpa, when the first refrigerant is one or more of R600a and / or and / or R600, R1243zf, and R1234yf, and when the second refrigerant is R290 and / or R1270, the low-pressure side of the high-temperature refrigeration cycle 10 and the low-pressure side of the low-temperature refrigeration cycle 20 are both configured to be lower than one atmosphere, that is, both are negative pressure operation. In the refrigeration system, the lower the operating pressure, the lower the noise generated by the compressor and the refrigerant, the lower the operating pressure, and the lower the condensation pressure. Under the same pressure ratio, the low-pressure side of the high-temperature refrigeration cycle 10 and the low-pressure side of the low-temperature refrigeration cycle 20 are both configured to be lower than one atmosphere to obtain a lower evaporation pressure, that is, a lower evaporation temperature. As shown in Table 3, the lower the pressure, the lower the refrigeration temperature. In this way, low-temperature storage below -45°C can be achieved, and at the same time, the refrigeration equipment can be ensured to operate at a low noise level of less than 40dB (A).

[0106] In other optional embodiments, when the first refrigerant is R290 and / or R1270, the low-pressure side pressure range of the high-temperature refrigeration cycle circuit 10 in a stable operating state is configured to be higher than one atmosphere; when the second refrigerant is R290 and / or R1270, the low-pressure side pressure range of the low-temperature refrigeration cycle circuit 20 in a stable operating state is configured to be lower than one atmosphere.

[0107] In the embodiment of the present disclosure, when the first refrigerant and the second refrigerant are both R290 and / or R1270, the low-pressure side pressure range of the high-temperature refrigeration cycle circuit 10 in a stable operating state is configured to be higher than one atmosphere, which can also achieve low-temperature storage below -45°C, and at the same time ensure that the refrigeration equipment operates at a low noise level of less than 40dB(A).

[0108] In the related art, when a conventional single refrigeration system uses R290 refrigerant, the system operating pressure is high, and its high-pressure side pressure is usually higher than 1Mpa, and the low-pressure side pressure is usually between 0.08Mpa and 0.15Mpa. The compressor needs to operate at high pressure, and the starting performance and pressure resistance requirements are high, resulting in high weight and large vibration of the compressor. When the system uses R600a refrigerant, the high-pressure side pressure is usually between 0.3Mpa and 0.6Mpa, and the low-pressure side pressure is between 0.04Mpa and 0.08Mpa. The system operating pressure is low, the compressor is light and the vibration is low, but it cannot achieve a low temperature environment below -45°C. In the related art, a low temperature of about -60°C is achieved. Generally, low-temperature refrigerants such as R170, R1150, R507, and R508B are used in low-temperature refrigeration systems. The operating pressure of these refrigerants is higher than that of R290, which can achieve low temperatures but cannot solve the noise problem. Therefore, the embodiment of the present disclosure utilizes the external cascade technology to reduce the operating pressure of the low-temperature refrigeration cycle loop 20 to the level of a conventional refrigeration system using R600a refrigerant, thereby achieving both low temperature and noise reduction.

[0109] It can be seen from Table 4 that when the pressure is lower than 0.01Mpa, conventional capillary throttling is difficult, and the refrigeration flow of the refrigeration system is very low, and the refrigeration capacity is also correspondingly low; when the pressure is higher than 1.3Mpa, it will cause high vibration and noise of the compressor. It can be seen that R170 and R1150 can achieve -60℃ low temperature in the current industry, but the noise cannot be controlled. Therefore, the second refrigerant selection of R290, R1270 or a mixture of the two can achieve low noise and low temperature at the same time.

[0110] Table 4

[0111]

[0112]

[0113] Preferably, when the third pipeline 203 and the fourth pipeline 205 are connected or contacted to form the first regenerator 301, the first refrigerant is R600a, and / or the second refrigerant is R290. In this way, low temperature and noise reduction can be achieved at the same time.

[0114] Optionally, when the first refrigerant is R600a and / or R600, the cylinder volume of the high-temperature stage compressor 102 is greater than or equal to the cylinder volume of the low-temperature stage compressor 202; or, when the first refrigerant is R290 and / or R1270, the cylinder volume of the high-temperature stage compressor 102 is less than or equal to the cylinder volume of the low-temperature stage compressor 202.

[0115] In the disclosed embodiment, as shown in Table 5, the refrigeration capacity per unit volume of R290 and R1270 refrigerants is 2.8 to 5.1 times that of R600 and R600a refrigerants, that is, the exhaust volume of R290 and R1270 compressors to achieve the same refrigeration capacity is 2.8 to 5.1 times smaller than that of R600 and R600a. Therefore, when the high-temperature compressor 102 is an R600a compressor or an R600 compressor, the cylinder volume of the high-temperature compressor 102 is greater than or equal to the cylinder volume of the low-temperature compressor 202. When the high-temperature compressor 102 is an R290 compressor or an R1270 compressor, the cylinder volume of the high-temperature compressor 102 is less than or equal to the cylinder volume of the low-temperature compressor 202.

[0116] Table 5

[0117]

[0118] Optionally, when the second refrigerant is R290 and / or R1270, the outlet temperature of the low-pressure pipe of the condensing part 201 during stable operation is between -15°C and 20°C. In this way, the low-temperature compressor 202 has low vibration and high efficiency, achieving a low noise effect.

[0119] Optionally, the ratio of the internal volume V1 of the evaporation section 101 to the total volume Vh of the high-temperature refrigeration cycle loop 10 is set to: 5% Vh≤V1≤90% Vh; the ratio of the internal volume V2 of the condensation section 201 to the total volume Vc of the low-temperature refrigeration cycle loop 20 is set to: 2% Vc≤V2≤80% Vc.

[0120] The cascade refrigeration system provided by the embodiment of the present disclosure is adopted, by setting an evaporative condenser 30, using the high-temperature refrigeration cycle 10 to refrigerate the evaporative condenser 30, and when the temperature of the evaporative condenser 30 drops, the low-temperature refrigeration cycle 20 is started again to pre-cool the second refrigerant in the low-temperature refrigeration cycle 20 in advance. In the scheme of the present application, the content volume of the evaporation part 101 in the evaporative condenser 30 is set to within 5% to 90% of the total volume of the high-temperature refrigeration cycle 10, and the content volume of the condensation part 201 is set to within 2% to 80% of the total volume of the low-temperature refrigeration cycle 20. The cooling effect of the high-temperature refrigeration cycle 10 on the second refrigerant in the low-temperature refrigeration cycle 20 can be maintained, and the cooling temperature of the second refrigerant can be controlled within a reasonable range. Without affecting the refrigeration efficiency of the low-temperature refrigeration cycle 20, the maximum value of the condensation pressure in the low-temperature refrigeration cycle 20 can be effectively suppressed, thereby avoiding the increase in noise caused by excessive pressure and excessive flow rate of the second refrigerant, and better avoiding the problem of excessive noise during low-temperature refrigeration.

[0121] It can be understood that the evaporation part 101 and the condensation part 201 are both refrigerant coils, wherein the internal volume of the evaporation part 101 and the condensation part 201 refers to the internal volume of the corresponding refrigerant coils. The total volume of the high-temperature refrigeration cycle 10 refers to the sum of the volumes of all positions through which the first refrigerant flows in the high-temperature refrigeration cycle 10, and the total volume of the low-temperature refrigeration cycle 20 refers to the sum of the volumes of all positions through which the second refrigerant flows in the low-temperature refrigeration cycle 20.

[0122] Optionally, the ratio of the internal volume V1 of the evaporation part 101 to the total volume Vh of the high-temperature refrigeration cycle 10 is set to: 10% Vh≤V1≤70% Vh. In this way, by setting the volume of the evaporation part 101 to between 10% and 70% of the total volume of the high-temperature refrigeration cycle 10, the evaporation part 101 can make full use of the first refrigerant in the high-temperature refrigeration cycle 10 to cool down, and while generating sufficient cooling capacity at the evaporation part 101, avoid excessive refrigerant pressure in the high-temperature refrigeration cycle 10, improve the refrigeration efficiency of the high-temperature refrigeration cycle 10, and reduce the noise generated by the high-temperature refrigeration cycle 10.

[0123] Optionally, the ratio of the internal volume V1 of the evaporation part 101 to the total volume Vh of the high-temperature refrigeration cycle 10 is set to: 20% Vh≤V1≤50% Vh. In this way, by setting the volume of the evaporation part 101 to between 20% and 50% of the total volume of the high-temperature refrigeration cycle 10, the refrigeration capacity of the evaporation part 101 can be maintained to the maximum extent, and the condensation part 201 can be cooled better, so that the minimum refrigeration temperature of the overall cascade refrigeration system is lower, and the speed of temperature drop is increased, so that the refrigeration temperature reaches the minimum value in less time, the energy consumption is lower, and the speed of power-on startup to enter the low-temperature refrigeration working state is increased. At the same time, the noise during the refrigeration process can be kept at a low level, the refrigeration noise is effectively reduced, and the deep refrigeration technology is convenient for application in the home.

[0124] Optionally, the ratio of the internal volume V1 of the evaporation portion 101 to the total volume Vh of the high-temperature stage refrigeration cycle circuit 10 may also be set to: V1 = 20% Vh or V1 = 60% Vh.

[0125] Among them, when the ratio of the content volume V2 of the condensing part 201 to the total volume Vc of the low-temperature refrigeration cycle 20 is 15%, the ratio of the content volume V1 of the evaporating part 101 to the total volume Vh of the high-temperature refrigeration cycle 10 is 20%, 45% and 60% respectively as comparative examples, and the initial power-on precooling time min, the maximum condensing pressure MPa at an ambient temperature of 32°C, the empty box refrigeration depth °C, the empty box cooling speed to -60°C min, the 50kg high load cooling speed to -18°C h, the 50kg high load cooling maximum condensing pressure MPa, 32°C ambient temperature, the power consumption kWh / 24h when the temperature drops to -60°C, and the noise db (A) are verified, and the results shown in Table 6 below are obtained:

[0126] Table 6

[0127] Total volume ratio of evaporation section 101 / high temperature stage refrigeration cycle 10 20％ 45％ 60％ Precooling time after first power-on (min) 15 15 15 32℃ ambient temperature, maximum condensing pressure MPa 1.593 1.325 0.995 Empty box refrigeration depth ℃ -62 -67 -65 Empty box cooling to -60℃ speed min 246 210 220 50kg high load cooling to -18℃ speed h 25 20 19 50kg high load cooling maximum condensing pressure MPa 1.632 1.113 0.899 32℃ ambient temperature, power consumption dropped to -60℃ kWh / 24h 3.0 2.5 3.2 Noise db(A) 36 37 38

[0128] By comparison, it can be seen that when the content volume V1 of the evaporation part 101 accounts for 45% of the total volume Vh of the high-temperature refrigeration cycle loop 10, the empty box refrigeration depth is the lowest, the empty box is cooled to -60°C the fastest, and the ambient temperature is 32°C, the power consumption is the lowest when it drops to -60°C, and the speed of cooling a high load of 50kg to -18°C and the noise db(A) are moderate, which can better meet the purpose of improving the refrigeration efficiency and maintaining the quiet effect. Accordingly, when the content volume V1 of the evaporation part 101 accounts for 45% of the total volume Vh of the high-temperature refrigeration cycle loop 10, a better effect is achieved.

[0129] Optionally, the ratio of the internal volume V2 of the condenser 201 to the total volume Vc of the low-temperature refrigeration cycle 20 is set to: 5% Vc ≤ V2 ≤ 50% Vc. In this way, by setting the volume of the condenser 201 to between 5% and 50% of the total volume of the low-temperature refrigeration cycle 20, the condenser 201 can fully cool the second refrigerant in the low-temperature refrigeration cycle 20, and can pre-cool the second refrigerant in the low-temperature refrigeration cycle 20 during the startup phase, so that it can mix with the high-temperature part of the second refrigerant, reduce the temperature of the overall refrigerant, and thus avoid the condensation pressure in the low-temperature circulation pipeline, maintain the temperature of the second refrigerant within a reasonable range, and thus prevent the pressure in the low-temperature circulation pipeline from fluctuating too much, while maintaining the refrigeration efficiency, effectively reducing the increase in noise caused by excessive pressure and excessive flow rate of the second refrigerant.

[0130] Optionally, the ratio of the internal volume V2 of the condensing part 201 to the total volume Vc of the low-temperature refrigeration cycle 20 is set to: 7% Vc ≤ V2 ≤ 30% Vc. In this way, by setting the volume of the condensing part 201 to between 7% and 30% of the total volume of the total capacity of the low-temperature refrigeration cycle 20, the temperature of the second refrigerant can be better maintained within a reasonable range, and the maximum value of the condensation pressure of the low-temperature refrigeration cycle 20 can be avoided to be too high, so that the minimum refrigeration temperature of the overall cascade refrigeration system is lower, and the speed of temperature drop is increased, so that the refrigeration temperature reaches the minimum value in less time, the energy consumption is lower, and the speed of power-on startup into the low-temperature refrigeration working state is increased. At the same time, the noise during the refrigeration process can be kept at a low level, the refrigeration noise is effectively reduced, and the deep refrigeration technology is convenient for the family.

[0131] Optionally, the ratio of the internal volume V2 of the condensing section 201 to the total volume Vc of the low-temperature refrigeration cycle circuit 20 may also be set to: V2 = 5% Vc or V2 = 35% Vc.

[0132] Among them, when the ratio of the content volume V1 of the evaporation part 101 to the total volume Vh of the high-temperature refrigeration cycle 10 is 45%, the ratio of the content volume V2 of the condensation part 201 to the total volume Vc of the low-temperature refrigeration cycle 20 is 5%, 15% and 35% respectively as comparative proportions, and the initial power-on precooling time min, the maximum condensing pressure MPa at an ambient temperature of 32°C, the empty box refrigeration depth °C, the empty box cooling speed to -60°C min, the 50kg high load cooling speed to -18°C h, the 50kg high load cooling maximum condensing pressure MPa, 32°C ambient temperature, the power consumption kWh / 24h when the temperature drops to -60°C, and the noise db (A) are verified, and the results shown in Table 7 are obtained:

[0133] Table 7

[0134] Total volume ratio of condensing part to low temperature stage refrigeration cycle 5％ 15％ 35％ Precooling time after first power-on (min) 15 15 15 32℃ ambient temperature, maximum condensing pressure MPa 1.653 1.325 1.021 Empty box refrigeration depth ℃ -65 -67 -62 Empty box cooling to -60℃ speed min 235 210 245 50kg high load cooling to -18℃ speed h 26 20 22 50kg high load cooling maximum condensing pressure MPa 1.532 1.113 0.957 32℃ ambient temperature, power consumption dropped to -60℃ kWh / 24h 3.1 2.5 2.9 Noise db(A) 39 37 37

[0135] By comparison, it can be seen that when the volume V2 of the condensing section 201 accounts for 15% of the total volume Vc of the low-temperature refrigeration cycle 20, the empty box refrigeration depth is the lowest, the empty box is cooled to -60°C the fastest, and the ambient temperature is 32°C, the power consumption is the lowest when the temperature drops to -60°C, and the speed of cooling a high load of 50kg to -18°C and the noise db (A) are moderate, which can better meet the purpose of improving the refrigeration efficiency and maintaining the quiet effect. Therefore, when the volume V2 of the condensing section 201 accounts for 15% of the total volume Vc of the low-temperature refrigeration cycle 20, a better effect is achieved.

[0136] Optionally, the internal volume V1 of the evaporation section 101 accounts for 45% of the total volume Vh of the high-temperature refrigeration cycle 10, while the internal volume V2 of the condensation section 201 accounts for 15% of the total volume Vc of the low-temperature refrigeration cycle 20.

[0137] Optionally, an expansion tank is provided at the exhaust port of the low-temperature compressor 202. In this way, since the exhaust port of the low-temperature compressor 202 discharges high-pressure refrigerant, the noise will increase due to excessive pressure and excessive flow rate. Therefore, by arranging the expansion tank at the exhaust port of the low-temperature compressor 202, the pressure and flow rate of the second refrigerant can be buffered, which has a better effect of reducing noise.

[0138] Optionally, the ratio of the internal volume V3 of the expansion tank to the total volume Vc of the low-temperature refrigeration cycle 20 is: 1% Vc ≤ V3 ≤ 30% Vc. In this way, by setting the internal volume of the expansion tank to between 1% and 30% of the total volume of the low-temperature refrigeration cycle 20, it can not only reduce the pressure and flow rate of the second refrigerant, but also maintain sufficient pressure for the second refrigerant to enter the evaporative condenser 30, thereby improving the heat exchange efficiency, and further reducing the noise in the low-temperature refrigeration cycle 20 while maintaining the refrigeration effect of the low-temperature refrigeration cycle 20.

[0139] Optionally, the ratio of the internal volume V3 of the expansion tank to the total volume Vc of the low-temperature refrigeration cycle 20 is: 2% Vc ≤ V3 ≤ 10% Vc. In this way, further setting the internal volume of the expansion tank to between 2% and 10% of the total volume of the low-temperature refrigeration cycle 20 can better maintain the pressure and flow rate of the second refrigerant, which can reduce noise and maintain the refrigeration effect of the low-temperature refrigeration cycle 20.

[0140] Optionally, the ratio of the internal volume V3 of the expansion tank to the total volume Vc of the low-temperature refrigeration cycle 20 is: V3=5%Vc. In this way, setting the internal volume of the expansion tank to 5% of the total volume of the low-temperature refrigeration cycle 20 can minimize the noise in the low-temperature refrigeration cycle 20 and maintain the refrigeration effect of the low-temperature refrigeration cycle 20.

[0141] Optionally, the evaporative condenser 30 further includes a heat exchange portion. The evaporation portion 101 and the condensation portion 201 are connected to the same set of heat exchange portions. In this way, the heat exchange efficiency between the evaporation portion 101 and the condensation portion 201 can be improved, and the cold generated by the high-temperature refrigeration cycle loop 10 can be better utilized to cool the refrigerant in the low-temperature refrigeration cycle loop 20, thereby improving the refrigeration efficiency of the overall cascade refrigeration system, and through the rapid heat exchange between the two, the low-temperature refrigeration cycle loop 20 can achieve a rapid refrigeration effect, thereby improving the overall refrigeration speed.

[0142] The heat exchange part may be a whole metal heat exchange medium, and the evaporation part 101 and the condensation part 201 are staggeredly arranged on the metal heat exchange medium. Alternatively, the heat exchange part may be a liquid heat exchange medium enclosed in a heat preservation box, and the evaporation part 101 and the condensation part 201 are staggeredly arranged in the heat preservation box and submerged by the liquid heat exchange medium.

[0143] Optionally, the ratio of the internal volume V3 of the first regenerator 301 to the total volume Vc of the low-temperature refrigeration cycle 20 is set to: 1% Vc ≤ V3 ≤ 80% Vc. In this way, in order to reduce the maximum condensing pressure of the low-temperature refrigeration cycle 20, it is necessary to set the volume of the first regenerator 301 to be as small as possible relative to the total volume of the low-temperature refrigeration cycle 20. However, if the ratio of the volume of the first regenerator 301 to the total volume of the low-temperature circulation filter is set too small, the temperature of the return air pipe at the return air port of the low-temperature compressor 202 will be too low, resulting in the risk of frost and compressor shutdown. Therefore, setting the internal volume of the first regenerator 301 to within 1% to 80% of the total volume of the low-temperature refrigeration cycle 20 can balance the maximum condensing pressure in the low-temperature refrigeration cycle 20 and the temperature of the return air pipe of the low-temperature compressor 202, thereby avoiding the maximum condensing pressure in the low-temperature refrigeration cycle 20 from being too high and preventing the risk of frost and compressor shutdown due to the temperature of the return air pipe of the low-temperature compressor 202 being too low.

[0144] Optionally, the ratio of the internal volume V3 of the first regenerator 301 to the total volume Vc of the low-temperature refrigeration cycle 20 is set to: 4% Vc ≤ V3 ≤ 60% Vc. In this way, by setting the internal volume of the first regenerator 301 to within 4% to 60% of the total volume of the low-temperature refrigeration cycle 20, the condensation pressure in the low-temperature refrigeration cycle 20 can be better maintained to avoid the maximum value of the condensation pressure being too high, and the risk of frost formation on the return air pipe (fourth pipeline) of the low-temperature compressor 202 and the risk of compressor shutdown can be avoided to the greatest extent.

[0145] Optionally, the ratio of the internal volume V3 of the first regenerator 301 to the total volume Vc of the low-temperature refrigeration cycle 20 is set to: 5% Vc ≤ V3 ≤ 40% Vc. In this way, the internal volume of the first regenerator 301 is set to within 5% to 40% of the total volume of the low-temperature refrigeration cycle 20, so that the first regenerator 301 can better transfer the heat of the high-temperature refrigerant at the exhaust port of the low-temperature compressor 202 to the low-temperature refrigerant at its return port, avoid frosting of the return air pipe at the return air port of the low-temperature compressor 202, and prevent the condensation pressure in the low-temperature refrigeration cycle 20 from being too high.

[0146] The first regenerator 301 includes a hot end and a cold end, the hot end is connected between the exhaust port of the low-temperature compressor 202 and the evaporative condenser 30; the cold end is connected between the air inlet of the low-temperature compressor 202 and the low-temperature evaporator 204. Through the heat exchange between the cold end and the hot end, the temperature of the low-temperature refrigerant pipe part between the air inlet of the low-temperature compressor 202 and the evaporator of the low-temperature evaporator 204 can be increased to avoid frosting and the risk of compressor shutdown. Optionally, the hot end and the cold end of the first regenerator 301 have the same internal volume. In this way, the heat exchange between the two can be kept equal to avoid waste, and while maintaining a good effect of avoiding frosting, the increase of the maximum condensation pressure in the low-temperature refrigeration cycle 20 can be avoided. Maintain a good silent effect.

[0147] It can be understood that the internal volume of the first regenerator 301 refers to the sum of the internal volume of its hot end and the internal volume of its cold end.

[0148] Optionally, the ratio of the internal volume V3 of the first regenerator 301 to the total volume Vc of the low-temperature refrigeration cycle 20 may also be set to: V3 = 5% Vc, V3 = 10% Vc or V3 = 30% Vc.

[0149] Among them, when the ratio of the content volume V1 of the evaporation part 101 to the total volume Vh of the high-temperature refrigeration cycle 10 is 45% and the ratio of the content volume V2 of the condensation part 201 to the total volume Vc of the low-temperature refrigeration cycle 20 is 15%, the ratio of the content volume V3 of the first regenerator 301 to the total volume Vc of the low-temperature refrigeration cycle 20 is 5%, 10% and 30% as a comparative example, the initial power-on precooling time min, 32°C ambient temperature, the maximum condensing pressure MPa, 32°C ambient temperature, the low-temperature return air temperature °C under the same refrigerant filling amount, the empty box refrigeration depth °C and the noise db (A) are verified, and the results shown in Table 8 below are obtained:

[0150] Table 8

[0151]

[0152] By comparison, it can be seen that when the ratio of the content volume V1 of the evaporation part 101 to the total volume Vh of the high-temperature refrigeration cycle loop 10 is 45% and the ratio of the content volume V2 of the condensation part 201 to the total volume Vc of the low-temperature refrigeration cycle loop 20 is 15%, when the ratio between the content volume of the first regenerator 301 and the total volume of the low-temperature refrigeration cycle loop 20 is set to 10%, at an ambient temperature of 32°C and the same refrigerant filling amount, the low-temperature return air temperature ℃ is moderate, the empty box refrigeration depth ℃ is the lowest, and the noise db (A) value is also lower. Therefore, setting the ratio between the content volume of the first regenerator 301 and the total volume of the low-temperature refrigeration cycle loop 20 to 10% is the best for the performance of the overall cascade refrigeration system.

[0153] Optionally, the content of R290 or R1270 in the second refrigerant is greater than 50%.

[0154] In the related art, in the field of household appliances, R290 is generally used in combination with conventional refrigerants, such as R290 and R600a in a cascade refrigeration system, which can achieve a temperature of -40°C or lower, but its content is less than 50%. When the content of R290 exceeds 50%, it will cause greater pressure on the refrigeration system, thereby causing greater vibration, making the refrigeration equipment noisy during operation. In the embodiment of the present disclosure, the second refrigerant uses R290 or R1270 as the main refrigerant, and the content is greater than 50%, and in combination with the above-mentioned volume ratio and other parameter settings of the evaporative condenser and various parameter settings of the first regenerator, it can reduce the pressure difference, reduce noise, and achieve low-noise operation of the refrigeration equipment.

[0155] Generally, the compressor startup sequence of the cascade refrigeration system is to start the high-temperature compressor first and then the low-temperature compressor. However, in actual application, after the high-temperature compressor is started, since the low-temperature compressor has not yet started and the condensing part of the evaporative condenser is in a "no heat source" state, the liquid high-temperature refrigerant after throttling by the high-temperature throttling device will accumulate in the evaporation part of the evaporative condenser, and the accumulation amount can even reach 70% to 80% of the total amount of refrigerant in the high-temperature circulation loop; and after the low-temperature compressor is started, a large amount of heat is transferred from the condensing part to the evaporation part, causing the high-temperature refrigerant stored in the evaporation part to evaporate quickly, and a large amount of gaseous high-temperature refrigerant is generated, which makes it difficult to control the temperature and pressure of the evaporation part of the evaporative condenser.

[0156] Optionally, the high-temperature circulation loop also includes a high-temperature liquid reservoir, which can be used to store part of the high-temperature refrigerant and release the stored high-temperature refrigerant to the high-temperature circulation loop. In this way, the liquid refrigerant generated by the high-temperature circulation loop at the initial start-up of the compressor can be partially stored in the high-temperature liquid reservoir, reducing the amount of refrigerant accumulated in the evaporative condenser 30, thereby reducing the peak pressure of the evaporation part 101 in the process of generating a large amount of gaseous refrigerant by evaporation, so as to achieve a buffering and stabilizing effect.

[0157] Optionally, the high-temperature liquid reservoir is arranged on the pipeline between the evaporative condenser 30 and the high-temperature compressor 102 of the high-temperature circulation loop. Exemplarily, the high-temperature liquid reservoir includes a first high-temperature liquid reservoir and / or a second high-temperature liquid reservoir. Among them, the first high-temperature liquid reservoir is arranged on the pipeline between the evaporative condenser 30 and the return air pipe group 304 of the high-temperature circulation loop to accumulate part of the liquid high-temperature refrigerant on the liquid outlet side of the evaporative condenser 30. The second high-temperature liquid reservoir is arranged on the pipeline between the return air pipe group 304 and the high-temperature compressor 102 of the high-temperature circulation loop to accumulate part of the liquid high-temperature refrigerant on the liquid inlet side of the high-temperature compressor 102. This arrangement can also reduce the risk of "liquid hammer".

[0158] Here, Tables 9 and 10 show the experimental test results of two types of prototypes A and B under the ambient temperature conditions of 25°C and 32°C, respectively. Prototype A is a model without a high-temperature liquid storage tank, and prototype B is a model with a high-temperature liquid storage tank according to the previous embodiment.

[0159] Table 9

[0160]

[0161]

[0162] Table 10

[0163]

[0164] Combining Tables 9 and 10, it can be seen that compared with Model A, Model B equipped with a high-temperature liquid storage tank not only has the mass of the cold medium in the high-temperature circulation loop increased by about 50%, but also its peak pressure decreased by about 0.1MPa under an ambient temperature of 25°C and by about 0.22MPa under an ambient temperature of 32°C. This model is less susceptible to peak pressure shock and the system operation is more stable.

[0165] In some other optional embodiments, the exhaust temperatures of the low-temperature compressor 202 of different types of cascade refrigeration systems are different, and the corresponding high-temperature evaporation temperature and low-temperature condensation temperature are respectively defined, so that the displacement of the corresponding high-temperature compressor 102 and low-temperature compressor 202 can be tested. As shown in the following Table 11:

[0166] Table 11

[0167]

[0168]

[0169] Combined with Table 11, in order to ensure that the low-temperature storage temperature and the system temperature are controllable, the high-temperature compressor 102 and the low-temperature compressor 202 satisfy the following displacement relationship:

[0170] 1.5:1≤CC 高温级 :CC 低温级 ≤1:1.5,

[0171] Among them, CC 高温级 is the displacement of the high temperature stage compressor 102, CC 低温级 is the displacement of the low temperature stage compressor 202.

[0172] It can be seen from Table 11 that by setting the displacement CC high-temperature stage compressor 140 and the displacement CC low-temperature stage compressor 250 within the above-mentioned displacement range, not only the low-temperature stage condensing temperature and the high-temperature stage evaporating temperature can meet the system temperature setting requirements and the system condensing heat load requirements; at the same time, the low-temperature stage exhaust temperature can also be within a more reasonable temperature range, reducing the probability of safety problems of the whole machine caused by high heat load and excessively high exhaust temperature.

[0173] Furthermore, the present application also tests the exhaust temperature and the temperature inside the box corresponding to different low-temperature compressor 202 displacements when the high-temperature compressor 102 displacement is a fixed value, as shown in Table 12-1; and the exhaust temperature and the temperature inside the box corresponding to different high-temperature compressor 102 displacements when the low-temperature compressor 202 displacement is a fixed value, as shown in Table 12-2. The displacements of the high-temperature compressor 102 and the low-temperature compressor 202 in the two sets of test data are set to 9cc respectively.

[0174] Table 12-1

[0175] Low temperature stage displacement cc 7 7.6 8.3 9 9.7 10.4 Low temperature exhaust temperature ℃ 83.2 86.19 89.31 91.13 93.86 97.5 Low temperature evaporation temperature ℃ -65 -65.5 -66.5 -66.9 -67.4 -67.6 Temperature in the box ℃ -62.6 -63.1 -64.1 -64.6 -65 -65.2

[0176] Table 12-2

[0177] High temperature displacement cc 10.8 9.9 9 8.1 7.2 6.3 5.4 4.5 High temperature exhaust temperature ℃ 93.96 92.16 89.88 86.76 84.72 81 79.08 77.64 Low temperature evaporation temperature ℃ -69.2 -69.9 -69.5 -69.4 -69.3 -68.5 -68.3 -67.3 Temperature in the box ℃ -65.3 -65.4 -65.3 -65.1 -64.7 -64.2 -63.5 -62.5

[0178] It can be seen from Table 12-1 that when the displacement of the high-temperature compressor 102 is set to 9cc, the low-temperature compressor 202 is also 9cc (i.e., the ratio is 1:1), the exhaust temperature is more reasonable, and the compressor matching is more reasonable. And, it can be seen from Table 12-2 that when the displacement of the low-temperature compressor 202 is set to 9cc, the high-temperature compressor 102 is also 9cc (i.e., the ratio is 1:1), the exhaust temperature is more reasonable, and the compressor matching is more reasonable.

[0179] Therefore, in the embodiment of the present application, the displacement ratio of the high-temperature compressor 102 CC high-temperature stage and the low-temperature compressor 202 CC low-temperature stage is preferably 1:1.

[0180] In some optional embodiments, such as Figures 6 to 13a As shown, the high temperature stage throttling element 105, the evaporation part 101, the first pipeline 103 and the condensation part 201 are integrated into one.

[0181] In the disclosed embodiment, the high temperature stage throttling device 105, the evaporation part 101, the first pipeline 103, and the condensation part 201 of the cascade refrigeration system are integrated into one, that is, the connection of these pipelines is transferred outside the assembly process of the refrigeration equipment, so that when assembling the refrigeration equipment, the integrated pipeline can be directly assembled to the box body, reducing the welding and other work in the assembly process, optimizing the assembly process, and improving production efficiency. In addition, the pipelines are parallel, the overall space occupied is small, and the transportation is convenient, which reduces the adverse conditions caused by transportation.

[0182] In some optional embodiments, such as Figures 6 to 13a As shown, when the low-temperature stage compressor and the condensing part are connected through the third pipeline, and the low-temperature stage evaporator and the low-temperature stage compressor are connected through the fourth pipeline, the high-temperature stage throttling device 105, the evaporating part 101, the first pipeline 103, the condensing part 201, the third pipeline 203, the fourth pipeline 205 and the low-temperature stage throttling device 206 are integrated into one.

[0183] In the disclosed embodiment, the high temperature stage throttling device 105, the evaporation part 101, the first pipeline 103, the condensation part 201, the third pipeline 203 and the fourth pipeline 205 of the cascade refrigeration system are integrated into one, so that the integrated pipelines and components can be increased, and the integration of the pipelines can be further improved. When assembling the refrigeration equipment, the integrated pipelines can be directly assembled to the box body, which reduces the welding and other work in the assembly process, optimizes the assembly process, and improves the production efficiency. The pipelines are parallel, and the overall space occupied is small, which further improves the convenience of transportation and reduces the adverse conditions generated during transportation.

[0184] In other optional embodiments, the high-temperature stage condenser and the high-temperature stage throttling device are connected via the second pipeline, and the low-temperature stage evaporator and the low-temperature stage compressor are connected via the fourth pipeline 205, and the high-temperature stage throttling device, the evaporating part, the first pipeline, the condensing part, the second pipeline and the fourth pipeline are integrated into one.

[0185] In the disclosed embodiment, the second pipeline and the fourth pipeline of the cascade refrigeration system may also be integrated with other components. In practical applications, different pipelines may be integrated with the high-temperature stage throttling device, the evaporating part, the first pipeline and the condensing part according to different pipeline settings of the cascade refrigeration system.

[0186] Optionally, the high temperature stage throttling element 105, the evaporation portion 101, the first pipeline 103 and the condensation portion 201 are welded together.

[0187] In the disclosed embodiment, multiple pipelines of the cascade refrigeration system are integrated into one by welding, which increases the connection stability of the pipelines and prevents the pipelines from falling off during transportation of the refrigeration equipment.

[0188] Optionally, the high temperature stage throttling member 105, the evaporation part 101, the first pipeline 103 and the condensation part 201, the third pipeline 203 and the fourth pipeline 205 are welded together. Alternatively, the high temperature stage throttling member, the evaporation part, the first pipeline, the condensation part, the second pipeline and the fourth pipeline are welded together.

[0189] In practical applications, the integrated pipelines and components are welded through multiple welding points to enhance the stability of the connection between the pipelines.

[0190] An embodiment of the present disclosure further provides a refrigeration device, which includes the cascade refrigeration system as described in any of the above embodiments.

[0191] The refrigeration device provided in the embodiment of the present disclosure includes the cascade refrigeration system described in any of the above embodiments, and thus has the beneficial effects of the cascade refrigeration system of any of the above embodiments, which will not be described in detail here.

[0192] The following description is based on the refrigeration equipment being a refrigerator, particularly a horizontal refrigerator:

[0193] The refrigeration equipment includes a box, such as Figure 6 As shown, the box body defines a compression chamber 403, and the box body includes an inner liner 402 and an outer shell 401. The outer shell 401 is located on the outside of the inner liner 402, and the outer shell 401 and the inner liner 402 enclose the compression chamber 403. The inner liner 402 includes a plurality of enclosure panels, and the plurality of enclosure panels enclose a storage cavity, which is configured as a low-temperature storage space for accommodating items. The plurality of enclosure panels include a bottom wall and a side wall, the side wall is connected to the end of the bottom wall and extends upward, the side walls are sequentially arranged along the circumference of the bottom wall, the side walls and the bottom wall enclose a storage cavity, and the bottom wall portion of the inner liner 402 protrudes upward to form a step. The outer shell 401 and the step enclose the compression chamber 403.

[0194] Optionally, the press cabin 403 can be located at least one of the left side of the box, the right side of the box, and the rear side of the box. In actual application, the position of the press cabin can be set according to the size of the box and the use requirements.

[0195] Optionally, the high temperature stage compressor 102 and the low temperature stage compressor 202 are both located in the same compressor cabin 403. This can reduce the space of the inner tank 402 occupied by the compressor cabin 403 and increase the storage capacity of the inner tank 402.

[0196] For ease of description, Figure 6As shown, when the press cabin is located on the left or right side of the box body, the front-to-back direction is defined as the depth direction of the press cabin 403 , and the left-to-right direction is defined as the width direction of the press cabin 403 .

[0197] Optionally, the fifth compressor and the sixth compressor are arranged side by side in the compressor chamber 403, or the length direction of the fifth compressor and the length direction of the sixth compressor are arranged crosswise.

[0198] In the embodiment of the present disclosure, the fifth compressor and the sixth compressor are both arranged in the same compressor cabin 403, and the two compressors can be arranged side by side or crosswise according to the size of the compressor cabin 403, which does not increase the height of the compressor cabin 403, and does not need to set up two compressor cabins 403 to place the two compressors respectively. In addition, the storage space of the inner tank 402 occupied by the compressor cabin 403 can be reduced, and the storage space and storage experience of the refrigeration equipment can be improved.

[0199] Specifically, when the depth of the compressor cabin 403 is large enough, the two compressors can be arranged side by side in the depth direction of the compressor cabin 403. When the depth of the compressor cabin 403 is small, the two compressors can be placed crosswise. When the width of the compressor cabin 403 in the left-right direction is large enough, the two compressors can also be arranged side by side in the left-right direction of the compressor cabin 403.

[0200] For example, when the compressor cabin is located on the left or right side of the box, the two compressors can be arranged side by side in the front-to-back direction, and when the compressor cabin is located on the rear side of the box, the two compressors can be arranged side by side in the left-to-right direction. It can be understood that the method of arranging two compressors in one compressor cabin belongs to an optional embodiment of the present application.

[0201] Optionally, the fifth compressor and the sixth compressor are located in the same horizontal plane, which facilitates the installation of the two compressors, as well as the corresponding bottom plates and reinforcement frame structures of the two compressors, and reduces the space occupied by the compressor cabin in the height direction.

[0202] For example, when the compressor cabin is located on the left or right side of the box, the two compressors can be arranged side by side in the front-to-back direction, and when the compressor cabin is located on the rear side of the box, the two compressors can be arranged side by side in the left-to-right direction. It can be understood that the method of arranging two compressors in one compressor cabin belongs to an optional embodiment of the present application.

[0203] Optionally, the fifth compressor and the sixth compressor are located in the same horizontal plane, which facilitates the installation of the two compressors, as well as the corresponding bottom plates and reinforcement frame structures of the two compressors, and reduces the space occupied by the compressor cabin in the height direction.

[0204] It should be noted that the fifth compressor and the sixth compressor can be the high-temperature compressor and the low-temperature compressor of the cascade refrigeration system, or they can be compressors of other types of refrigeration systems. For example, compressors of two independent refrigeration systems can also be arranged in the manner of the fifth compressor and the sixth compressor of the present application.

[0205] like Fig.15 As shown, for the high-temperature compressor 101, that is, the fifth compressor, its length direction refers to the length along the X-axis direction, and its width direction refers to the length along the Y-axis direction. For the low-temperature compressor 202, that is, the sixth compressor, its length direction refers to the length along the Y-axis direction, and its width direction refers to the length along the X-axis direction.

[0206] The following is an example in which the fifth compressor is a high-temperature compressor and the sixth compressor is a low-temperature compressor:

[0207] Optionally, when the width direction of the compressor chamber 403 is larger, the fifth compressor and the sixth compressor can be arranged side by side along the width direction of the compressor chamber 403.

[0208] Optionally, when the length direction of the fifth compressor and the length direction of the sixth compressor are cross-arranged, the angle α between the length direction of the fifth compressor and the length direction of the sixth compressor is in the range of 10°≤α≤170°.

[0209] In the embodiment of the present disclosure, the positions of the two compressors in the compressor cabin 403 can be adjusted according to the size of the compressor cabin 403, and the angle between the two compressors can be adjusted between 10° and 170°.

[0210] Optionally, when the length direction of the fifth compressor and the length direction of the sixth compressor are arranged crosswise, the range of the angle α between the length direction of the fifth compressor and the length direction of the sixth compressor is 50°≤α≤130°. In the implementation of the present disclosure, when the angle between the two is between 50° and 130°, the compressor structure in the compressor cabin is more compact.

[0211] For example, α can be 10°, 20°, 30°, 40°, 50°, 60°, 70°, 80°, 90°, 100°, 110°, 120°, 140°, 150°, 170°, etc.

[0212] In a specific embodiment, at least one of the fifth compressor and the sixth compressor has its length direction inclined relative to the depth direction of the compressor chamber 403 to facilitate the arrangement of the two compressors.

[0213] In another specific embodiment, Fig.15 and Fig.16 As shown, the fifth compressor and the sixth compressor are arranged vertically.

[0214] In the disclosed embodiment, the two compressors are vertically arranged to effectively utilize the space of the compressor cabin 403. The compressor cabin 403 does not occupy too much space of the inner tank 402, thereby increasing the volume of the storage chamber.

[0215] Optionally, the length direction of one of the fifth compressor and the sixth compressor extends along the depth direction of the compressor compartment, and the length direction of the other of the fifth compressor and the sixth compressor extends along the width direction of the compressor compartment.

[0216] Optionally, the fifth compressor and the sixth compressor are arranged in sequence along the depth direction of the compressor cabin, so as to facilitate the coordination of the low-temperature stage pipeline and the high-temperature stage pipeline with the compressor.

[0217] It should be noted that the sixth compressor and the fifth compressor may also be arranged in sequence along the depth direction of the compressor compartment. In practical applications, the arrangement directions of the fifth compressor and the sixth compressor may be arranged according to the arrangement of the refrigeration equipment pipelines.

[0218] In this embodiment, the outer shell 401 is coated on the outside of the inner liner 402, and an interlayer space is formed between the outer shell 401 and the inner liner 402, and the interlayer space can be used to accommodate one or more heat exchange parts of the high-temperature refrigeration cycle 10 and / or the low-temperature refrigeration cycle 20. Optionally, the heat exchange part of the high-temperature refrigeration cycle 10 includes but is not limited to the aforementioned evaporation part 101, the high-temperature condenser 104, the high-temperature throttling part 105, and the high-temperature evaporator 108. Another option is that the heat exchange part of the low-temperature refrigeration cycle 20 includes but is not limited to the aforementioned condensation part 201, the low-temperature evaporator 204, and the low-temperature throttling part 206. And the interlayer space can also be used to accommodate the aforementioned regenerator (including the first regenerator 301, the second regenerator 302, and / or the third regenerator 303), the return air pipe group 304, the precooling pipe 308, etc.

[0219] Optionally, the evaporative condenser 30 is located between the inner tank 402 and the outer shell 401, such as Figure 6 and Figure 8 As shown, the evaporator condenser is arranged on the outside of the side wall of the inner tank 402, or, as shown in Figures 9 to 13a As shown, the evaporative condenser 30 is located below the step.

[0220] In the disclosed embodiment, the evaporative condenser 30 is arranged below the step, and the space below the step is used to place the compressor, that is, the space above the compressor cabin 403 is used to place the evaporative condenser 30, so that the evaporation part 101 and the condensation part 201 of the evaporative condenser 30 have sufficient contact length, so that the high-temperature refrigeration cycle 10 can fully cool the condensation part 201 of the low-temperature refrigeration cycle 20, thereby achieving the low-temperature effect of the refrigeration equipment. In addition, the evaporative condenser 30 is arranged below the step, and the space of the refrigeration equipment is reasonably utilized, which improves the rationality of the layout of the pipeline of the refrigeration equipment, reduces the distance between the evaporative condenser 30 and the compressor or other components, and reduces the production cost. The evaporative condenser 30 can also be arranged on the outside of the side wall of the inner tank 402, so that the distance between the evaporative condenser 30 and other components is also reduced compared to when it is arranged below the bottom wall, and the length of the pipeline is also reduced, saving costs.

[0221] Optionally, when the evaporative condenser 30 is located below the step, there is a gap between the evaporative condenser 30 and the bottom of the step to reduce heat exchange between the evaporative condenser 30 and the inner tank 402 .

[0222] Optionally, when the evaporator condenser is disposed outside the side wall of the inner liner 402 , there is a gap between the evaporator condenser 30 and the outer wall surface of the inner liner 402 to reduce heat exchange between the evaporator condenser 30 and the inner liner 402 .

[0223] Optionally, when the refrigeration equipment includes a first heat regenerator 301, the evaporative condenser 30 and the first heat regenerator 301 are both located between the inner tank 402 and the outer shell 401, and the evaporative condenser 30 and the first heat regenerator 301 are arranged on the outside of at least one enclosing plate; or, when the refrigeration equipment includes a first heat regenerator 301 and a return air pipe group 304, the evaporative condenser 30, the first heat regenerator 301 and the return air pipe group 304 are all located between the inner tank 402 and the outer shell 401, and the evaporative condenser 30, the first heat regenerator 301 and the return air pipe group 304 are arranged on the outside of at least one enclosing plate.

[0224] In the disclosed embodiment, the evaporative condenser 30, the first heat regenerator 301 and the return air pipe group 304 can be respectively arranged on different enclosure plates, or can be arranged on the same enclosure plate, so that the pipelines can be reasonably arranged and the storage capacity of the refrigeration equipment can be increased.

[0225] In some optional embodiments, the evaporative condenser 30, the first heat regenerator 301 and the return air pipe group 304 are located on the same side wall of the inner tank 402. This makes the multiple pipelines more compact and facilitates the connection of the pipelines with the corresponding compressors. For example, the evaporative condenser 30, the first heat regenerator 301 and the return air pipe group 304 can all be arranged on the front side wall of the inner tank 402, the rear side wall of the inner tank 402, the left side wall of the inner tank 402 or the right side wall of the inner tank 402.

[0226] Optionally, the first heat regenerator 301 and the return air pipe group 304 are arranged on the same side wall of the inner tank 402, and the first heat regenerator 301 and the return air pipe group 304 are connected.

[0227] In the disclosed embodiment, the first heat regenerator 301 and the return air pipe group 304 are arranged on the same side wall of the inner tank 402, which can reduce the length of the pipeline and facilitate the connection between the pipeline and the corresponding compressor.

[0228] Optionally, the first heat regenerator 301 and the return air pipe group 304 are arranged in sequence from the inside to the outside.

[0229] In the disclosed embodiment, the first heat regenerator 301 and the return air pipe group 304 are stacked and arranged with an interval, which further reduces the space occupied by the first heat regenerator 301 and the return air pipe group 304.

[0230] For example, Figure 8 As shown, the first heat regenerator 301 matches the return air pipe group 304, that is, the first heat regenerator 301 and the return air pipe group 304 have the same or similar shapes and sizes. This facilitates the arrangement of the first heat regenerator 301 and the return air pipe group 304. Optionally, the first heat regenerator 301 is curved, and the return air pipe group 304 is also curved, so that the lengths of the first heat regenerator 301 and the return air pipe group 304 can be guaranteed.

[0231] Optionally, the refrigeration device further includes a connecting piece, which is connected between the first heat regenerator 301 and the return air pipe group 304. There are multiple connecting pieces, which are arranged at intervals along the extension direction of the first heat regenerator 301 or the return air pipe group 304, wherein one end of the connecting piece is connected to the inner tank 402, so that the stability of the return air pipe group 304 and the first heat regenerator 301 can be increased.

[0232] Alternatively, if Figures 6 to 8 As shown, when the evaporative condenser 30 , the first heat regenerator 301 and the return air pipe group 304 are arranged on the same side wall, the first heat regenerator 301 and the return air pipe group 304 are located on a side of the evaporative condenser 30 close to the compressor cabin 403 .

[0233] In the disclosed embodiment, the evaporative condenser 30, the first regenerator 301 and the return air pipe group 304 are all arranged on the same side wall of the inner tank 402, so that more pipelines are integrated on the same side wall of the inner tank 402, which can provide sufficient space to set the evaporative condenser 30, the first regenerator 301 and the return air pipe group 304, ensuring the length and heat exchange efficiency. It can also make the pipeline more compact and ensure the storage space of the refrigeration equipment. The first regenerator 301 and the return air pipe group 304 are closer to the compressor cabin 403, which can reduce the length of the pipeline and facilitate the connection with the corresponding compressor.

[0234] Preferably, if Figure 6 As shown, the evaporative condenser 30 , the first heat regenerator 301 and the return air pipe group 304 are all arranged on the rear side wall of the inner tank 402 .

[0235] Optionally, when the evaporator condenser is arranged on the side wall of the inner tank 402 , the low-temperature stage throttling member 206 is coiled between the side wall of the inner tank 402 and the outer shell 401 , and the low-temperature stage throttling member 206 is located on the outside of the evaporative condenser 30 .

[0236] In the disclosed embodiment, the low temperature stage throttle 206 is also arranged on the side wall of the inner tank 402 to facilitate the connection of the low temperature stage throttle 206 with other pipelines and to provide sufficient space to ensure the length of the low temperature stage throttle 206 .

[0237] Preferably, if Figure 6 As shown, the evaporative condenser 30 , the first regenerator 301 , the low-temperature stage throttling element 206 and the return air pipe group 304 are all arranged on the rear side wall of the inner tank 402 .

[0238] It can be understood that the first heat regenerator 301, the return air pipe group 304, the evaporative condenser 30 and the low-temperature stage throttling device 206 can also be arranged on other side walls of the inner tank 402. This embodiment only takes the rear side wall of the inner tank 402 as an example. On this basis, those skilled in the art should be fully capable of expanding it, and this application will not go into details.

[0239] Alternatively, if Figure 6 and Fig.17 As shown, the compressor cabin 403 includes a partition 70 and a compressor bottom plate 60, the compressor bottom plate 60 is located at the bottom of the compressor cabin 403, the partition 70 is at least partially located at the upper part of the compressor cabin 403, and the partition 70 is spaced below the step. Optionally, the compressor bottom plate 60 is a 1.5 mm thick galvanized sheet.

[0240] In the disclosed embodiment, the partition 70 is located at the upper part of the compressor cabin 403. The partition 70 can be supported above the compressor to protect the compressor. The compressor base plate 60 is located below the compressor to support the compressor and to reduce shock to the compressor.

[0241] Optionally, when the evaporative condenser 30 is located below the step or located on the upper part of the compressor cabin 403, it can be understood that the evaporative condenser 30 is located between the partition plate 70 and the step.

[0242] Optionally, the partition 70 is located at the upper part of the compressor cabin 403 and below the step, and the high-temperature stage compressor 102 and the low-temperature stage compressor 202 are located below the partition, wherein the evaporative condenser is located between the inner liner and the outer shell or between the partition and the inner liner.

[0243] In the disclosed embodiment, when the evaporative condenser is located between the inner container and the outer shell, the evaporative condenser can be located between the side wall of the inner container and the outer shell. The evaporative condenser can also be located between the partition and the inner container, such as between the partition and the step. The partition can also be L-shaped, and the evaporative condenser can also be located between the vertical surface of the partition and the vertical surface of the step.

[0244] Optionally, the return air pipe group 304 or the first heat regenerator may also be located between the inner tank and the outer shell or between the partition and the inner tank. The specific location is the same as that described for the evaporator and condenser, and will not be repeated here.

[0245] In some other optional embodiments, the return air pipe group 304 is located between the inner liner 402 and the outer shell 401 , and the return air pipe group 304 is arranged below the step or on the outer side of the side wall of the inner liner 402 .

[0246] In the disclosed embodiment, the return air pipe group 304 can be arranged below the step or outside the side wall of the inner tank 402, and the return air pipe group 304 is arranged in a curved manner, so that sufficient space can be provided to ensure the length of the return air pipe group 304 and the heat exchange efficiency. Optionally, when the return air pipe group 304 is arranged below the step, the return air pipe group 304 is located between the partition 70 and the step.

[0247] Optionally, the first heat regenerator 301 is disposed below the step or on the outside of the side wall of the inner tank 402 .

[0248] In the disclosed embodiment, the first heat regenerator 301 can also be arranged below the step or outside the side wall of the inner tank 402, and the return air pipe group 304 is arranged in a curved manner, so that sufficient space can be provided to ensure the length of the first heat regenerator 301 and the heat exchange efficiency. Optionally, when the first heat regenerator 301 is arranged below the step, the first heat regenerator 301 is located between the partition 70 and the step.

[0249] In a specific embodiment, Fig. 9 and Fig.10 As shown, the evaporative condenser 30 and the return air pipe group 304 are both located below the step, specifically, the evaporative condenser 30 and the return air pipe group 304 are both located between the step and the partition 70, so that the evaporative condenser 30 and the return air pipe group 304 have sufficient contact length, so that the evaporation part 101 can fully dissipate heat to the condensation part 201, and at the same time can achieve the purpose of noise reduction and energy saving. Optionally, the first regenerator 301 is located on the outside of the side wall of the inner tank 402, so that the heat exchange length of the first regenerator can be guaranteed.

[0250] Optionally, the first pipeline 103, the evaporative condenser 30, and the high-temperature throttling device 105 are all located below the step, wherein the low-temperature throttling device 206 and the first heat exchanger 301 are both located on the rear wall of the inner tank 402, so that the pipelines are arranged in parallel, further reducing the space occupied by the pipelines.

[0251] Optionally, the evaporative condenser 30 and the return air pipe group 304 are arranged below the step in a vertically spaced manner. This ensures the length of the evaporative condenser 30 and the return air pipe group 304, and the spacing between the two can also reduce or avoid heat conduction between the two.

[0252] For example, Fig. 9 As shown, the evaporative condenser 30 is spaced above the return air pipe group 304, and the return air pipe group 304 is spaced above the partition 70, wherein the bottom of the step, the evaporative condenser 30, the return air pipe group 304 and the partition 70 are filled with a foam layer to achieve heat insulation and heat preservation.

[0253] In another specific embodiment, Fig.11 and Fig.12 As shown, the return air pipe group 304, the evaporative condenser 30 and the first regenerator 301 are arranged below the step at intervals in the vertical direction.

[0254] In the disclosed embodiment, the evaporative condenser 30, the return air pipe group 304 and the first regenerator 301 are divided into three layers and are all arranged below the steps, which can further reduce the spatial structure of the pipeline and reduce the transportation cost.

[0255] Optionally, the evaporative condenser 30 is located between the return air pipe group 304 and the first regenerator 301. Specifically, from top to bottom, the first regenerator 301, the evaporative condenser 30 and the return air pipe group 304 are sequentially arranged at intervals. The first regenerator 301 is arranged at intervals from the bottom of the step, the return air pipe group 304 is arranged at intervals from the partition 70, and the bottom of the step, the first regenerator 301, the evaporative condenser 30, the return air pipe group 304 and the partition 70 are all filled with a foaming layer to achieve heat insulation and heat preservation.

[0256] It should be noted that the positions of the return air pipe group 304, the first regenerator 301 and the evaporative condenser 30 can be adjusted according to actual needs, and this application only illustrates the case where the evaporative condenser 30 is located between the return air pipe group 304 and the first regenerator 301. On this basis, those skilled in the art should be fully capable of expanding, and this application will not repeat it.

[0257] In another specific embodiment, Fig.13 and Fig.13a As shown, the fourth pipeline 205 is in contact with or connected to the return air pipe group 304 to form a third regenerator 303 , and the third regenerator 303 is used to enable the second refrigerant in the fourth pipeline 205 to exchange heat with the first refrigerant in the return air pipe group 304 .

[0258] In the disclosed embodiment, the first refrigerant in the return air pipe group 304 exchanges heat with the second refrigerant in the fourth pipe 205 , which can reduce the temperature in the return air pipe group 304 , increase the degree of subcooling, and thereby improve the heat exchange effect of the evaporative condenser 30 .

[0259] Optionally, the fourth pipeline 205 is close to the return air pipe group 304 to achieve heat exchange. Specifically, the fourth pipeline 205 is close to the top of the return air pipe group 304.

[0260] Optionally, the condensation section 201 includes a first condensation section and a second condensation section, the evaporation section 101 is located between the first condensation section and the second condensation section, and the evaporation section 101 is in contact with both the first condensation section and the second condensation section. In the embodiment of the present disclosure, there are multiple condensation sections 201, and the evaporation section 101 is located between two condensation sections 201, which can increase the contact length between the condensation section 201 and the evaporation section 101, thereby improving the heat exchange effect of the evaporative condenser 30.

[0261] Optionally, when the evaporative condenser 30 and the third regenerator 303 are both located below the step, the first condensation section, the evaporation section 101 and the second condensation section are arranged in a vertical direction, and the evaporative condenser 30 is arranged above the third regenerator 303 at intervals.

[0262] In the disclosed embodiment, the third heat exchanger 303 and the evaporative condenser 30 are arranged at intervals in the vertical direction, so that the cascade refrigeration system does not need to be equipped with the first heat exchanger 301. The first heat exchanger 301 and the return air pipe group 304 are integrated into one, which can further simplify the heat exchange structure and further reduce the space occupied by the pipeline.

[0263] Optionally, the evaporative condenser 30 is spaced apart from the bottom of the step, and the third regenerator 303 is spaced apart from the upper wall of the partition 70. The bottom of the step, the evaporative condenser 30, the third regenerator 303 and the partition 70 are all filled with a foaming layer to achieve heat insulation and heat preservation.

[0264] In some other optional embodiments, combined with Figure 14 to Figure 14c As shown, at least two heat exchange parts in the above embodiment are arranged side by side from the inside to the outside in the interlayer space formed by the inner liner 402 and the outer shell 401, where the inside refers to the side where the inner liner 402 is located, and the outside refers to the side where the outer shell 401 is located. In addition, compared with the working temperature of the heat exchange part on the outer shell side, the working temperature of the heat exchange part located in the inner liner layer is lower, so that a temperature gradient with increasing temperature from the inside to the outside can be formed.

[0265] The working temperature of the heat exchange part of the cascade refrigeration system using the above arrangement is different. For example, the working temperature of the evaporation part 101 of the evaporative condenser 30 during steady-state operation is about -35°C; the working temperature of the condensation part 201 of the evaporative condenser 30 during steady-state operation is about -18 to -30°C; the refrigerant temperature of the cold end of the first regenerator 301 gradually rises from -60°C to 30°C during steady-state operation, and the refrigerant temperature of the hot end gradually decreases from 34°C to -30°C during steady-state operation. Here, for the convenience of subsequent description, the cold end of the first regenerator 301 is defined as the first regenerator tube group 3011, and the hot end is defined as the second regenerator tube group 3012.

[0266] Therefore, under the above-mentioned arrangement, the working temperature difference between adjacent heat exchange parts is relatively smaller, and the heat exchange parts with a larger working temperature difference are spaced farther apart, thereby reducing the heat conduction rate between each other and slowing down the loss of cold from the inside to the outside (or the conduction of heat from the outside to the inside), so that the interior of the inner tank 402 can better maintain a low-temperature storage environment, effectively reducing the influence of the heat dissipation of the heat exchange parts with high working temperatures (such as pre-cooling tubes, condensers, etc.) on the temperature of the storage space, thereby improving the refrigeration efficiency of the cascade refrigeration system and having a good effect of energy saving and consumption reduction.

[0267] In some embodiments, the heat exchange part using the above arrangement includes two or more of the following types:

[0268] The first heat exchange part is configured to exchange heat with the low-temperature storage space on the inner tank side. For example, the first heat exchange part is a low-temperature evaporator 204 or a fourth pipeline 205. The refrigerant flowing through the low-temperature evaporator 204 and the fourth pipeline 205 is at a low temperature and is arranged close to the inner tank, which can be used to cool the inner tank 402.

[0269] The second heat exchange part is configured to perform heat exchange with the external environment on the side of the housing 401. For example, the second heat exchange part is a precooling tube 308 or a high temperature stage condenser 104.

[0270] The third heat exchange part is configured to allow two heat exchange tube groups with different working temperatures to perform intermediate heat exchange. For example, the third heat exchange part is an evaporative condenser 30, and its two heat exchange tube groups are respectively an evaporation part 101 and a condensation part 201; or, the third heat exchange part is a regenerator, wherein the regenerator can be the first regenerator 301, the second regenerator 302 or the third regenerator 303 in the above embodiment. Taking the first regenerator 301 as an example, its two heat exchange tube groups are respectively a first regenerator tube group 3011 and a second regenerator tube group 3012.

[0271] Here, the two heat exchange tube groups of the third heat exchange part are also arranged from inside to outside according to the temperature, wherein the heat exchange tube group with lower working temperature is located on the inner tank side, and the heat exchange tube group with higher working temperature is located on the outer shell side.

[0272] Optionally, the interlayer space formed by the inner liner 402 and the outer shell 401 is sequentially arranged with the first heat exchange part and the second heat exchange part from the inside to the outside. Alternatively, the interlayer space formed by the inner liner 402 and the outer shell 401 is sequentially arranged with the first heat exchange part and the third heat exchange part from the inside to the outside. Alternatively, the interlayer space formed by the inner liner 402 and the outer shell 401 is sequentially arranged with the second heat exchange part and the third heat exchange part from the inside to the outside. Alternatively, the interlayer space formed by the inner liner 402 and the outer shell 401 is sequentially arranged with the first heat exchange part, the second heat exchange part and the third heat exchange part from the inside to the outside, and so on. This application is not limited to this.

[0273] In some optional embodiments, at least two heat exchange parts are arranged in the first arrangement. Fig.14b and 14c As shown, the first arrangement is constructed by sequentially arranging the low-temperature stage evaporator 204, the evaporation part 101 of the evaporative condenser 30, the condensation part 201 of the evaporative condenser 30 and the precooling tube 308 from the inner tank side to the outer shell side.

[0274] In this embodiment, the working temperatures of each heat exchange part are, in sequence, the inner tank 402 - low temperature evaporator 204 (-65°C) - evaporation part 101 of evaporative condenser 30 (-48 to -35°C) - condensation part 201 of evaporative condenser 30 (-45 to 30°C) - precooling tube 308 (34 to 45°C). It can be seen that the working temperature of the heat exchange part increases successively from the inner tank side to the outer shell side. The heat exchange part with a lower temperature is located on the inner tank side, and the heat exchange part with a higher temperature is located on the outer shell side, so that the conduction of the former cold to the outer shell 401 side can be reduced, so that the cold can be supplied to the inner tank 402 more concentratedly, and the latter heat can be more easily dissipated to the external environment where the outer shell 401 is located, reducing the transfer of heat to the inner tank 402 side. At the same time, the temperature range between adjacent heat exchange parts is closer, and the temperature difference is smaller, which can slow down the conduction of cold to the outer shell 401 side or heat to the inner tank 402 side.

[0275] Optional, such as Fig.14c As shown, in the first arrangement, in the thickness direction of the interlayer space, the distance between the low temperature stage evaporator 204 and the evaporative condenser 30 satisfies the following relationship:

[0276] δ / 6≤H≤δ / 2,

[0277] Wherein, H is the distance between the low temperature stage evaporator 204 and the evaporative condenser 30, and δ is the thickness of the interlayer space.

[0278] In this optional embodiment, the distance between the low-temperature evaporator 204 and the evaporative condenser 30 is determined according to the temperature of the foam layer at different thickness positions, where the closer the foam layer is to the inner liner 402, the lower its temperature, and vice versa, the farther the foam layer is from the inner liner 402, the higher its temperature. In this embodiment, the evaporative condenser 30 is arranged at a thickness position of the foam layer close to its temperature, so as to effectively reduce heat loss.

[0279] For example, the temperature of the inner tank 402 and the low-temperature evaporator 204 is about -65°C, and the temperature of the pre-cooling tube 308 is about 40°C. It can be known through experimental calculations that the temperature of the foaming layer at the 1 / 2 to 1 / 6 thickness position from the inside to the outside is close to -30°C, so this thickness position can be selected as the layout position of the evaporative condenser 30.

[0280] It should be noted that in this embodiment, the low-temperature evaporator 204 and the inner tank 402 are closely arranged through aluminum foil, and there is no gap between them. At the same time, it is assumed that the thickness of the heat exchange tube of the low-temperature evaporator 204 is negligible, so the position of the low-temperature evaporator 204 can be regarded as a reference position with a thickness of 0. Preferably, the distance between the low-temperature evaporator 204 and the evaporative condenser 30 is δ / 3.

[0281] In an optional embodiment, at least two heat exchange parts are arranged in a second arrangement. Specifically, the second arrangement is configured to sequentially arrange a low temperature stage evaporator 204, a first heat return pipe group 3011, a second heat return pipe group 3012 and a precooling pipe 308 from the inner tank side to the outer shell side.

[0282] In this embodiment, the operating temperatures of the heat exchange parts are as follows: inner tank 402 - low temperature evaporator 204 (-65°C) - first heat regeneration pipe group 3011 (-60 to 30°C) - second heat regeneration pipe group 3012 (-30 to 34°C) - precooling pipe 308 (34 to 45°C). It can be seen that the operating temperatures of the low temperature evaporator 204, the heat regeneration pipe and the precooling pipe 308 increase in sequence from the inner tank 402 side to the outer shell 401 side. It can also slow down the conduction of cold to the outer shell side or heat to the inner tank side. Different from the previous embodiment, the previous embodiment focuses on the arrangement of the evaporative condenser 30 in cooperation with the low-temperature evaporator 204 and the pre-cooling tube 308 to reduce the adverse effect of the heat exchange tube group of the evaporative condenser 30 on the inner tank 402, while the present embodiment focuses on the arrangement of the regenerator in cooperation with the low-temperature evaporator 204 and the pre-cooling tube 308 to reduce the heat loss of the regenerator during the heat recovery process and its temperature disturbance effect on other components such as the inner tank 402.

[0283] In some other optional embodiments, the type of heat exchange part disposed in the interlayer space between the inner liner 402 and the outer shell 401 further includes a fourth heat exchange part, which includes a return air pipe group 304 connected to the compressor return air. Optionally, the compressor is a high temperature compressor or a low temperature compressor as mentioned above.

[0284] Here, take the return air pipe group of the low temperature compressor return air as an example. Fig.14a As shown, the refrigerant flowing through the return air pipe group 304 comes from the second reheat pipe group 3012 of the first reheater 301, and its refrigerant temperature is about -25 to 30°C. For the return air pipe group in this temperature range, this embodiment is arranged according to the third arrangement form. Specifically, the third arrangement form is constructed to sequentially arrange the low-temperature stage evaporator 204, the first reheat pipe group 3011, the second reheat pipe group 3012, the return air pipe group 304 and the precooling pipe 308 from the inner tank side to the outer shell side.

[0285] Thus, the operating temperatures of the heat exchange parts in this embodiment are as follows: inner tank 402 - low temperature evaporator 204 (-65°C) - first heat return pipe group 3011 (-60~30°C) - second heat return pipe group 3012 (-30~34°C) - return air pipe group 304 (-25~30°C) - precooling pipe 308 (34~45°C). It can be seen that the temperature of the return air pipe group 304 is relatively close to the second heat return pipe group 3012 and precooling pipe 308 adjacent to both sides thereof, thereby achieving the effect of slowing down the conduction of the return air refrigerant heat to the inner tank 402 side.

[0286] In the foregoing multiple embodiments, at least part of the heat exchange tubes of the low-temperature stage evaporator 204 are located on the same tube layout plane. Optionally, the tube layout plane is parallel to the outer surface of the corresponding side enclosure plate of the inner tank 402 to ensure that the low-temperature stage evaporator 204 and the enclosure plate have sufficient thermal contact area, thereby ensuring the refrigeration and cooling effect on the inner tank 402.

[0287] Similarly, in order to avoid local overheating caused by heat concentration in the interlayer space of the heat exchange part, the heat exchange tubes of one or more other heat exchange parts are also arranged along the set tube layout planes, and the tube layout planes of adjacent heat exchange parts are set parallel to each other.

[0288] For example, Fig.14b and 14cAs shown, taking the first arrangement form as an example, the plane where the low-temperature evaporator 204 is located is set as the first pipe layout plane, the plane where the evaporation part 101 of the evaporative condenser 30 is located is set as the second pipe layout plane, the plane where the condensation part 201 of the evaporative condenser 30 is located is set as the third pipe layout plane, and the plane where the precooling pipe 308 is located is set as the fourth pipe layout plane. In this embodiment, the first pipe layout plane, the second pipe layout plane, the third pipe layout plane and the fourth pipe layout plane are arranged parallel to each other. By adopting the above-mentioned pipe layout form, the heat exchange tubes of each heat exchange part can be distributed more evenly in the foaming layer, and the spacing between each heat exchange tube of the heat exchange part and the adjacent heat exchange part is basically equal.

[0289] In some other embodiments, for a horizontal freezer model, the heat load at the open top and the bottom of the freezer is relatively large. Therefore, in order to ensure the refrigeration effect of the horizontal freezer, the heat exchange tube arrangement density of the low-temperature stage evaporator 204 corresponding to these two positions is greater than the heat exchange tube arrangement density of the other positions, so as to increase the refrigeration capacity at the top and bottom positions by increasing the number of refrigeration tubes.

[0290] Similarly, the compressor arranged in the compressor compartment 403 will also emit a lot of heat during operation. In order to reduce the impact of the compressor heat on the heat load of the inner tank 402, in this embodiment, the heat exchange tube arrangement density in the area near the compressor position of the low-temperature evaporator 204 is greater than the heat exchange tube arrangement density in other positions, thereby using the cooling capacity of the newly added heat exchange tubes to offset the heat of the compressor.

[0291] In addition, in the cascade refrigeration system, both the evaporative condenser 30 and the regenerator (first regenerator 301) are responsible for cooling the refrigerant (refrigerant) of the low-temperature refrigeration cycle 20, wherein the evaporative condenser 30 is responsible for the latent heat of the refrigerant, while the regenerator is responsible for the sensible heat of the refrigerant. Therefore, in order to improve the heat recovery effect of the system, in some embodiments, the evaporative condenser 30 and the regenerator satisfy the following relationship:

[0292] 7 / 2.2≤L1 / L2≤7 / 2.1,

[0293] Wherein, L1 is the effective heat exchange pipe length of the evaporative condenser, and L2 is the effective heat exchange pipe length of the regenerator.

[0294] After testing, it was found that when the effective heat exchange pipe lengths of the evaporator condenser 30 and the regenerator satisfy the above-mentioned numerical range, the sensible heat energy recovery of the refrigerant output by the low-temperature stage evaporator 204 can be effectively increased, and the occurrence of frost and condensation inside the compressor cabin caused by the excessively low return temperature of the low-temperature stage compressor 202 can be reduced.

[0295] For example, in a certain model, the refrigerant circulation volume of the evaporative condenser 30 is about 0.202g / s, the heat load is about 78.12W, the heat exchange coefficient is 3.7W / m / ℃, and the effective pipe length of the evaporative condenser 30 is calculated to be about 7.06m. In addition, in this embodiment, the ratio of the effective heat exchange pipe lengths of the evaporative condenser 30 and the regenerator is 7.06 / 2.13, that is, the effective pipe length of the regenerator is set to 2.13m; when the above regenerator pipe length is met, the temperature rise range △T1 of the cold fluid in the test regenerator can reach about 40℃, and the temperature drop range △T2 of the hot fluid is about 3℃. It can be seen that the above parameter settings can achieve a better heat recovery effect.

[0296] Optionally, the high temperature stage compressor 102 is located in front of the low temperature stage compressor 202 .

[0297] In the disclosed embodiment, the low temperature compressor 202 is located at the rear, which is convenient for connecting the low temperature compressor 202 with the pipeline provided on the rear side wall of the inner tank 402, thereby reducing the length of the pipeline. For example, when the evaporative condenser 30 is located under the step or the back plate, the low temperature compressor 202 is located at the rear, which is convenient for connecting the evaporative condenser 30 with the low temperature compressor 202. In addition, when the first heat exchanger 301 is located under the back plate or the step, it is also convenient for connecting the first heat exchanger 301 with the low temperature compressor 202.

[0298] Optionally, the length direction of one of the high-temperature stage compressor 102 and the low-temperature stage compressor 202 extends along the depth direction of the compressor cabin 403, and the length direction of the other of the high-temperature stage compressor 102 and the low-temperature stage compressor 202 extends along the width direction of the compressor cabin 403. In this way, the space in the compressor cabin 403 can be reasonably utilized, the size of the compressor cabin 403 can be reduced, and the storage capacity of the refrigeration equipment can be ensured.

[0299] Optionally, the length direction of the high temperature stage compressor 102 extends along the depth direction of the compressor cabin 403 , and the length direction of the low temperature stage compressor 202 extends along the width direction of the compressor cabin 403 .

[0300] In the disclosed embodiment, the length direction of the low temperature compressor 202 is arranged along the width direction of the compressor, so as to facilitate welding of the low temperature compressor 202 and the inlet and outlet pipelines (ie, the third pipeline 203 and the fourth pipeline 205).

[0301] Optionally, the inlet and outlet of the low-temperature compressor are oriented toward the rear side, which can further improve the welding between the low-temperature compressor 202 and its inlet and outlet pipelines.

[0302] Alternatively, if Figure 1As shown, the shell 401 is provided with welding holes, and the low temperature compressor 202 and / or the high temperature compressor 102 are arranged corresponding to the welding holes. In the embodiment of the present disclosure, in order to facilitate the connection of the pipeline, the shell 401 is provided with welding holes to provide sufficient space for pipeline welding, so as to facilitate the connection of the pipeline and the compressor through the welding holes.

[0303] Alternatively, if Figure 1 As shown, the rear side wall of the housing 401 is provided with a first welding hole 4011, and the first welding hole 4011 corresponds to the low temperature compressor 202. The left side wall of the housing 401 is provided with an air port 4012, and the air port 4012 is provided with a grille for realizing ventilation in the compressor cabin 403. Among them, the inlet and outlet of the high temperature compressor 102 correspond to the air port 4012, so that the inlet and outlet pipes of the high temperature compressor 102 (that is, the first pipeline 103 and the second pipeline 106) can be welded at the air port 4012 in the high temperature compressor 102. Improve the pipeline connection of the high temperature refrigeration cycle 10. The inlet and outlet of the low temperature compressor 202 correspond to the first welding hole 4011, so that the inlet and outlet pipes of the low temperature refrigeration cycle 20 are welded to the low temperature compressor 202 through the first welding hole 4011. Optionally, a second welding hole is opened on the front side wall of the shell 401, and the second welding hole corresponds to the high-temperature compressor 102. The high-temperature compressor 102 can also be connected to the pipeline through the second welding hole.

[0304] Optionally, a first connecting hole and a second connecting hole are formed on the top wall of the partition 70, wherein the first connecting hole corresponds to the inlet and outlet of the low temperature compressor 202, and the first connecting hole facilitates the inlet and outlet pipes of the low temperature compressor 202 to enter the compressor cabin 403 and connect to the low temperature compressor 202. The second connecting hole corresponds to the inlet and outlet of the high temperature compressor 102, and the second connecting hole facilitates the inlet and outlet pipes of the high temperature compressor 102 to enter the compressor cabin 403 and connect to the low temperature compressor 202.

[0305] Alternatively, if Figure 8 As shown, the low-temperature evaporator 204 includes a low-temperature evaporation tube, which is located between the inner liner 402 and the outer shell 401, and the low-temperature evaporation tube is wound around the outer side of the inner liner 402 and arranged close to the side wall of the inner liner 402, so as to refrigerate the interior of the inner liner 402. Optionally, the high-temperature condenser 104 includes a high-temperature condensation tube, which is located between the inner liner 402 and the outer shell 401, and the high-temperature condensation tube is wound around the outer side of the inner liner 402, wherein the high-temperature condensation tube is located on the outer side of the low-temperature evaporation tube, and a foaming layer is provided between the high-temperature condensation tube and the low-temperature evaporation tube, thereby reducing the heat exchange between the high-temperature condensation tube and the low-temperature evaporation tube, and ensuring the refrigeration effect of the cascade refrigeration system.

[0306] Alternatively, if Fig.17 and Fig.18As shown, the compressor cabin 403 further includes a reinforcing iron 50, which is connected between the partition plate 70 and the compressor bottom plate. Specifically, the reinforcing iron 50 includes a frame 501 and a vertical beam 502, which is located at at least one end of the compressor cabin 403; the vertical beam 502 is located in the frame 501 and extends in the vertical direction, and the vertical beam 502 is connected between the upper end and the lower end of the frame 501.

[0307] In the disclosed embodiment, the vertical beam 502 is located in the frame 501 and supported between the upper end of the frame 501 and the lower end of the frame 501, which further increases the structural strength of the frame 501, thereby improving the structural strength of the frame 501. By adding the vertical beam 502 to the frame 501, the strength of the reinforcing iron 50 is improved, which can increase the bearing capacity of the compressor cabin 403 for the compressor, improve the reliability of the refrigeration equipment transportation, and avoid damage.

[0308] Optionally, the frame 501 is rectangular, which can play a role in reinforcing the foam layer and the press cabin 403. It can be understood that the frame can also be other shapes, such as polygonal.

[0309] Optionally, the frame 501 includes an upper beam, a lower beam, a left beam and a right beam, the upper beam extends in the horizontal direction, the lower beam is located below the upper beam and is arranged opposite to the upper beam, and the lower beam extends in the horizontal direction; the left beam extends in the vertical direction and is connected between one end of the upper beam and one end of the lower beam; the right beam extends in the vertical direction and is connected between the other end of the upper beam and the other end of the lower beam; the upper and lower ends of the vertical beam are connected between the upper beam and the lower beam, and the vertical beam is located side by side between the left beam and the right beam.

[0310] Optionally, the vertical beam 502 is located between the left beam and the right beam, and the distance between the vertical beam 502 and the right beam is greater than the distance between the vertical beam 502 and the left beam.

[0311] In the disclosed embodiment, the vertical beam 502 is at different distances from the left beam and the right beam, so that the reinforcing iron 50 can provide sufficient space to facilitate the installation, disassembly and pipeline connection of the compressor in the compressor cabin 403.

[0312] Optionally, when a welding hole is provided in the outer shell 401 , the welding hole corresponds to the gap between the vertical beam 502 and the right beam, so that it is convenient to weld, repair and replace the compressor in the compressor cabin 403 .

[0313] Optionally, there are multiple frames 501, and the multiple frames 501 include a first frame 5011 and a second frame 5012, the first frame 5011 is located at one end of the press cabin 403, and the second frame 5012 is located at the other end of the press cabin 403; the reinforcing iron 50 also includes a first beam 503, and the first beam 503 is connected between the first frame 5011 and the second frame 5012.

[0314] In the disclosed embodiment, the first frame 5011 and the second frame 5012 are relatively arranged on both sides of the press cabin 403, and the first crossbeam 503 connects the two frames 501, further improving the structural strength of the reinforcing iron 50.

[0315] Optionally, the first cross beam 503 is located at the bottom of the reinforcing iron 50 , that is, the first cross beam 503 is connected between the bottom of the first frame 5011 and the bottom of the second frame 5012 .

[0316] Optionally, the partition plate 70 is disposed on the top of the reinforcing iron 50 , and one end of the partition plate 70 extends downward and is connected to the first crossbeam 503 .

[0317] In the disclosed embodiment, the partition 70 is connected to the top of the reinforcing iron 50, and the partition 70 is located above the compressor, and the reinforcing iron 50 supports and reinforces the partition 70. The partition 70 is L-shaped, which can improve the supporting strength of the partition 70 on the compressor cabin 403, thereby improving the reliability of refrigeration equipment transportation.

[0318] Optionally, the partition plate 70 is connected to the upper end of the frame 501 by welding. The partition plate 70 is connected to the first cross beam 503 by welding to ensure the strength of the structure.

[0319] Optionally, the first cross beam 503 is located on a side of the compressor cabin 403 away from the air outlet 4012, so that the partition plate 70 can also separate the compressor and the inner liner 402 to protect the inner liner 402 and the compressor.

[0320] Optionally, the compressor bottom plate 60 is disposed at the bottom of the reinforcing iron 50 and connected to the lower end of the frame 501. In the disclosed embodiment, the compressor bottom plate 60 is used to bear the weight of the compressor, and the lower end of the frame 501 is connected to the compressor bottom plate 60, which can further improve the bearing capacity of the compressor bottom plate for the compressor.

[0321] Optionally, the compressor bottom plate 60 is detachably connected to the frame 501. This facilitates replacement and maintenance of the compressor bottom plate 60. For example, the compressor bottom plate 60 and the lower end of the frame 501 can be detachably connected using screws.

[0322] Optionally, the compressor base plate 60 includes a plurality of base plates, and the plurality of base plates are sequentially spaced from the first frame 5011 to the second frame 5012. In this way, the compressor base plate 60 is not a whole, and when a plurality of compressors are provided, the compressors can be provided on different base plates, thereby reducing the occurrence of resonance and reducing noise.

[0323] In some optional embodiments, such as Fig.19As shown, the compressor base plate 60 includes a first base plate 601 and a second base plate 602, wherein the first base plate 601 is located below one of the high temperature stage compressor 102 and the low temperature stage compressor 202; and the second base plate 602 is located below the other of the high temperature stage compressor 102 and the low temperature stage compressor 202. The first base plate 601 and the second base plate 602 are located at the bottom of the same compressor cabin 403. For ease of description, one of the high temperature stage compressor 102 and the low temperature stage compressor 202 above the first base plate 601 is defined as the first compressor, and the other of the high temperature stage compressor 102 and the low temperature stage compressor 202 above the second base plate 602 is defined as the second compressor.

[0324] In the embodiment of the present disclosure, the high-temperature compressor 102 and the low-temperature compressor 202 are respectively arranged above the first bottom plate 601 and the second bottom plate 602, that is, the bottom plates of the two compressors in the same compressor compartment 403 are separated. This can avoid resonance between the two compressors when they are working, resulting in excessive noise, thereby reducing the noise of the refrigeration equipment when it is working and improving the user experience.

[0325] Optionally, a portion of the first bottom plate 601 protrudes upward to form a first reinforcing rib 6011 , and a portion of the second bottom plate 602 protrudes upward to form a second reinforcing rib 6021 .

[0326] In the disclosed embodiment, the first reinforcing rib 6011 and the second reinforcing rib 6021 respectively increase the strength of the first bottom plate 601 and the second bottom plate 602, and can increase the bending strength in the convex direction, improve the anti-deformation ability, so as to better fix the two compressors. In addition, this can change the natural frequency of the two bottom plates, avoid resonance between the compressor and the corresponding bottom plate, and thus reduce noise.

[0327] Optionally, the first reinforcing rib 6011 and the second reinforcing rib 6021 are both rib-like structures protruding from the surface of the first bottom plate 601 or the second bottom plate 602 toward the corresponding compressor. They may be formed by a partial protrusion of the first bottom plate 601 or the second bottom plate 602 toward the corresponding compressor, or by the upper surface of the first bottom plate 601 or the second bottom plate 602 protruding toward the compressor.

[0328] Optionally, there are multiple first reinforcing ribs 6011, and multiple first reinforcing ribs 6011 enclose a first installation area 6012, and the first installation area 6012 is used for the first compressor; there are multiple second reinforcing ribs 6021, and multiple second reinforcing ribs 6021 enclose a second installation area 6022, and the second installation area 6022 is used to install a second compressor.

[0329] In the disclosed embodiment, the multiple first reinforcing ribs 6011 can not only increase the strength of the first base plate 601, but also improve the strength of the base plate from multiple directions, reduce the probability of deformation of the first base plate 601, and further improve the natural frequency of the first base plate 601, reduce the resonance of the first base plate 601 and its corresponding compressor, and reduce noise. In addition, the multiple first reinforcing ribs 6011 enclose the first installation area 6012, that is, the first reinforcing ribs 6011 are arranged around the first installation area 6012, which can further increase the strength of the first base plate 601 and improve the noise reduction effect. Similarly, the multiple second reinforcing ribs 6021 of the second base plate 602 can also increase the strength in multiple directions and reduce noise. Their functions are the same as those of the multiple first reinforcing ribs 6011, and will not be repeated here.

[0330] Optionally, the plurality of first reinforcing ribs 6011 include a first convex rib and a second convex rib, the first convex rib is annular and located on one side of the first installation area 6012; the second convex rib is located on the other side of the first installation area 6012; wherein the first convex rib and the second convex rib are suitable for being spaced apart along the width direction of the compressor chamber 403.

[0331] In the disclosed embodiment, a plurality of first reinforcing ribs 6011 are respectively arranged on both sides of the first installation area 6012, wherein the first convex rib is annular, so that the first convex rib is not a whole convex surface, but forms a positive and negative pressure type, which can better improve the strength of the first bottom plate 601.

[0332] Optionally, the multiple second reinforcement ribs 6021 include a third rib, a fourth rib and a fifth rib, the third rib extends in the depth direction of the press chamber 403 and is located on one side of the second installation area 6022; the fourth rib is arranged opposite to the third rib and is located on the other side of the second installation area 6022; the fifth rib is connected to one end of the third rib away from the first bottom plate 601, and is suitable for extending in the width direction of the press chamber 403.

[0333] In the disclosed embodiment, a plurality of second reinforcing ribs 6021 are arranged around the second installation area 6022 , which can increase the strength of the second bottom plate 602 in multiple directions.

[0334] Optionally, the first bottom plate 601 and the second bottom plate 602 are spaced apart in the depth direction of the compressor cabin, and the length direction of the first installation area 6012 is perpendicular to the length direction of the second installation area 6022. In the embodiment of the present disclosure, the first installation area 6012 and the second installation area 6022 are vertically arranged, that is, the high-temperature compressor 102 and the low-temperature compressor 202 are vertically arranged, so that the space of the compressor cabin 403 can be effectively utilized and the two compressors can be reasonably arranged without increasing the size of the compressor cabin 403. Fig.15As shown, the length direction of the first mounting area 6012 refers to the length along the X-axis direction, and the length direction of the second mounting area 6022 refers to the length along the Y-axis direction.

[0335] Optionally, the length direction of the first installation area 6012 extends along the depth direction of the press chamber 403, and the length of the second installation area 6022 extends along the width direction of the press chamber 403, wherein the projection area of ​​the first bottom plate 601 on the horizontal plane is greater than or equal to the projection area of ​​the second bottom plate 602 on the horizontal plane.

[0336] In the embodiment of the present disclosure, the first installation area 6012 extends along the depth direction of the compressor chamber 403, and the length of the second installation area 6022 extends along the width direction of the compressor chamber 403. Therefore, the area of ​​the first bottom plate 601 is greater than or equal to the area of ​​the second bottom plate 602. This can ensure the setting stability of the two compressors and can reduce the noise of the two compressors separately.

[0337] Optionally, the first installation area 6012 is provided with a first installation through hole, the first installation through hole is in a cross shape, the bottom of the compressor above the first bottom plate 601 is in a spherical structure, extending from the bottom to the surroundings and gradually increasing the distance from the first bottom plate 601, the bottom of the compressor above the first bottom plate 601 is arranged above the first installation through hole, and the first installation area 6012 is surrounded by a first reinforcing rib 6011, so that when the compressor above the first bottom plate 601 vibrates during operation, the bottom of the compressor above the first bottom plate 601 can be prevented from directly contacting the first bottom plate 601, reducing the compressor above the first bottom plate 601 from transmitting vibration to the first bottom plate 601, thereby achieving the effect of reducing noise. Similarly, the second installation area 6022 is provided with a second installation through hole, the second installation through hole is in a cross shape, and its effect is the same as the first installation through hole, which will not be repeated here.

[0338] Optionally, a ratio a of a projection area of ​​the first bottom plate 601 on a horizontal plane to a projection area of ​​the second bottom plate 602 on a horizontal plane is in a range of 1≤a≤3.

[0339] In the embodiment of the present disclosure, when the projection area of ​​the first bottom plate 601 on the horizontal plane is smaller than the projection area of ​​the second bottom plate 602 on the horizontal plane, it is not possible to fully damp the compressor in the first installation area 6012. When the projection area of ​​the first bottom plate 601 is too large, the area of ​​the second bottom plate 602 is too small, and it is not possible to fully damp the compressor in the second installation area 6022. For example, a can be 1, 1.5, 2, 2.5, 3, etc.

[0340] Optionally, the ratio b of the area of ​​the top of the first reinforcing rib 6011 to the area of ​​the first bottom plate 601 is in the range of 20%≤b≤25%. In the disclosed embodiment, the area of ​​the first reinforcing rib 6011 is too small to play a role in reinforcing strength, and the first bottom plate 601 is easily deformed. The area of ​​the first reinforcing rib 6011 is too large to provide enough space to install the compressor. For example, b can be 20%, 21%, 22%, 23%, 24%, 25%, etc. Preferably, b is 22%.

[0341] Optionally, the ratio c of the area of ​​the top of the second reinforcing rib 6021 to the area of ​​the second bottom plate 602 is in the range of 10%≤b≤16%. In the disclosed embodiment, the area of ​​the second reinforcing rib 6021 is too small to play a role in reinforcing strength, and the second bottom plate 602 is easily deformed. The area of ​​the second reinforcing rib 6021 is too large to provide enough space to install the compressor. For example, c can be 10%, 11%, 12%, 13%, 14%, 15%, 16%, etc. Preferably, c is 24%.

[0342] Optionally, the height of the first reinforcing rib 6011 is greater than or equal to 6 mm and less than or equal to 15 mm. The height of the second reinforcing rib 6021 is greater than or equal to 6 mm and less than or equal to 15 mm.

[0343] Optionally, the height of the first reinforcing rib 6011 is greater than or equal to 9 mm and less than or equal to 11 mm. The height of the second reinforcing rib 6021 is greater than or equal to 9 mm and less than or equal to 11 mm.

[0344] In the embodiment of the present disclosure, compared with the reinforcing rib 80 with a height in the range of 3.5-5 mm, after simulation tests, the first reinforcing rib 6011 and the second reinforcing rib 6021 within the scope of the embodiment of the present disclosure have a better effect in improving the stiffness of the corresponding bottom plate, and can well improve the natural frequency of the first bottom plate 601 and the second bottom plate 602.

[0345] For example, the height of the first reinforcing rib 6011 is 9 mm, 9.5 mm, 10 mm, 10.5 mm, 11 mm, etc., among which 10 mm is preferred.

[0346] For example, the height of the second reinforcing rib 6021 is 9 mm, 9.5 mm, 10 mm, 10.5 mm, 11 mm, etc., among which 10 mm is preferred.

[0347] Optionally, a first pressing edge is provided at the outer edge of the first bottom plate 601, and the first pressing edge is pressed against the upper surface of the first bottom plate 601, so that the strength of the first bottom plate 601 can be strengthened and the natural frequency of the first bottom plate 601 can be changed. At the same time, the first pressing edge can fill the gap between the first bottom plate 601 and the reinforcing iron 50, so as to facilitate the fixing of the first bottom plate 601.

[0348] Optionally, the first bottom plate 601 is rectangular, and three sides of the first bottom plate 601 are connected to the reinforcing iron 50 to improve the connection strength of the first bottom plate 601. The remaining side of the first bottom plate 601 is spaced apart from the second bottom plate 602.

[0349] Optionally, the outer edge of the second bottom plate 602 is provided with a second pressing edge, and the second pressing edge is pressed against the upper surface of the second bottom plate 602, so that the strength of the second bottom plate 602 can be strengthened and the natural frequency of the second bottom plate 602 can be changed. At the same time, the second pressing edge can fill the gap between the second bottom plate 602 and the reinforcing iron 50, so as to facilitate the fixing of the second bottom plate 602.

[0350] Optionally, the second bottom plate 602 is rectangular, and three sides of the second bottom plate 602 are connected to the reinforcing iron 50 to improve the connection strength of the second bottom plate 602. The remaining side of the second bottom plate 602 is spaced apart from the second bottom plate 602.

[0351] Optionally, when there are multiple bottom plates, and the multiple bottom plates extend in the direction from the first frame 5011 to the second frame 5012, the reinforcing iron 50 further includes a second crossbeam 504, the second crossbeam 504 is connected between the first frame 5011 and the second frame 5012, and the second crossbeam 504 is arranged opposite to the first crossbeam 503; wherein the second crossbeam 504 is connected to the multiple bottom plates. In the embodiment of the present disclosure, when there are multiple bottom plates, the second crossbeam 504 connects the multiple bottom plates, further improving the bearing capacity of the bottom plates for the compressor.

[0352] Optionally, the refrigeration device further includes a first universal wheel and a second universal wheel, wherein the first universal wheel is located at the bottom of the first base plate 601, and the second universal wheel is located at the bottom of the second base plate 602. The first base plate 601 is also configured with a first mounting hole, and the first mounting hole is used to mount the first universal wheel. The second base plate 602 is configured with a second mounting hole, and the second mounting hole is used to mount the second universal wheel. The movement of the refrigeration device is achieved through the first universal wheel and the second universal wheel.

[0353] Optionally, the first bottom plate 601 partially protrudes upward to form a first mounting protrusion, the first mounting protrusion is provided with a first mounting hole, and the first mounting protrusion is provided with at least two slots. The refrigeration device also includes a first connecting plate, the first connecting plate is connected above the first universal wheel, and the first connecting plate is inserted into the slot to fix the first universal wheel to the first bottom plate 601.

[0354] Optionally, the second bottom plate 602 partially protrudes upward to form a second mounting protrusion, the second mounting protrusion is provided with a second mounting hole, and the second mounting protrusion is provided with at least two slots. The refrigeration device further includes a second connecting plate, the second connecting plate is connected above the second universal wheel, and the second connecting plate is inserted into the slot to fix the second universal wheel to the second bottom plate 602. Optionally, the center of the first universal wheel and the center of the second universal wheel are on the same straight line along the depth direction of the compressor cabin 403.

[0355] Optionally, a first notch is present at one end of the first convex rib and the second convex rib away from the second bottom plate 602, and the first mounting protrusion is disposed at the first notch. Optionally, a second notch is present between the fifth convex rib and the fourth convex rib, and the second mounting protrusion is disposed at the second notch. Here, the first notch and the second notch facilitate the installation of the universal wheel. At the same time, the first mounting protrusion and the second mounting protrusion can also increase the strength of the first bottom plate 601 and the second bottom plate 602.

[0356] In some other optional embodiments, Fig. 20 As shown, there is only one compressor base plate 60 , and both the high-temperature stage compressor 102 and the low-temperature stage compressor 202 are disposed above the one compressor base plate 60 .

[0357] The compressor bottom plate 60 partially protrudes upward to form a reinforcing rib 80, and the reinforcing rib 80 includes a first rib segment 801 and a second rib segment 802, the second rib segment 802 is connected to the first rib segment 801 and a fold is formed at the connection, and the first rib segment 801 and the second rib segment 802 jointly define a first placement position 809 for placing a third compressor. For ease of description, the high-temperature compressor 102 or the low-temperature compressor placed in the first placement position 809 is defined as the third compressor, and the high-temperature compressor 102 or the low-temperature compressor placed in the second placement position 810 is defined as the fourth compressor.

[0358] According to the embodiment of the present disclosure, the first rib segment 801 and the second rib segment 802 are respectively located in two directions of the compressor bottom plate 60, and together define a first placement position 809, and the third compressor is placed in the first placement position 809, thereby defining the position of the third compressor. The first rib segment 801 and the second rib segment 802 can increase the rigidity of the compressor bottom plate 60 in different directions, reduce the deformation of the compressor bottom plate 60, increase the natural frequency of the compressor bottom plate 60, reduce the resonance between the compressor bottom plate 60 and the third compressor, and thus reduce the noise generated when the third compressor is working.

[0359] Optionally, two connecting components are provided at the bottom end of the third compressor, and the two connecting components are arranged opposite to each other. One end of the connecting component is fixedly connected to the third compressor, and the other end is fixedly connected to the compressor base plate 60, so that the third compressor is fixed to the compressor base plate 60. The connecting component is arranged higher than the compressor base plate 60, so that there is a gap between the bottom of the third compressor and the compressor base plate 60, which can avoid direct contact between the bottom of the third compressor and the compressor base plate 60.

[0360] Optionally, the first rib segment 801 is arranged along the length direction of the compressor base plate 60 , and the second rib segment 802 is arranged along the width direction of the compressor base plate 60 .

[0361] Optionally, the first rib segment 801 and the second rib segment 802 are perpendicular to each other. The first rib segment 801 and the second rib segment 802 are vertically connected, and the position of the first placement position 809 can be preliminarily defined. In addition, the first rib segment 801 can improve the rigidity of the compressor bottom plate 60 along the length direction, and the second rib segment 802 can improve the rigidity of the compressor bottom plate 60 along the width direction, thereby improving the overall rigidity of the compressor bottom plate 60, reducing the resonance between the compressor bottom plate 60 and the third compressor, and achieving the effect of reducing noise.

[0362] Optionally, the reinforcing rib 80 also includes a third rib segment 803, which is connected to the second rib segment 802 and forms a folded angle at the connection; the third rib segment 803 is arranged opposite to the first rib segment 801 and is located on the same side of the second rib segment 802; the third rib segment 803, the first rib segment 801 and the second rib segment 802 jointly define a first placement position 809.

[0363] By setting the third rib segment 803, the third rib segment 803 can further define the first placement position 809 together with the first rib segment 801 and the second rib segment 802. The third rib segment 803 extends along the length direction of the compressor bottom plate 60, enhances the bending strength of the compressor bottom plate 60 at the first placement position 809 along the length direction, improves the anti-deformation capability, thereby enhancing the rigidity of the compressor bottom plate 60 at this location, limits the third compressor at the first placement position 809, reduces the resonance frequency of the compressor bottom plate 60 at this location and the third compressor, reduces the resonance of the third compressor and the compressor bottom plate 60, and achieves the effect of reducing noise.

[0364] Optionally, a first placement position 809 defined by the first rib segment 801, the second rib segment 802 and the third rib segment 803 is provided with a third notch, the third notch is provided in the gap between the first rib segment 801 and the third rib segment 803, the compressor base plate 60 also includes a third mounting protrusion, the third mounting protrusion is provided at the third notch, and the first mounting protrusion is used to install a third universal wheel.

[0365] Optionally, the refrigeration equipment also includes a fourth compressor, and the reinforcing rib 80 also includes a fourth rib segment 804 and a fifth rib segment 805, the fourth rib segment 804 is arranged on the side of the second rib segment 802 away from the first rib segment 801; the fifth rib segment 805 and the fourth rib segment 804 are arranged on the same side of the second rib segment 802 and are arranged opposite to the fourth rib segment 804, and the second rib segment 802, the fourth rib segment 804 and the fifth rib segment 805 jointly define a second placement position 810 for placing the fourth compressor.

[0366] Optionally, one end of the second rib segment 802 is connected to the first rib segment 801, and the angle formed at the connection between the second rib segment 802 and the first rib segment 801 is 90 degrees, and the other end of the second rib segment 802 is connected to the fifth rib segment 805, and the angle formed at the connection between the second rib segment 802 and the fifth rib segment 805 is 90 degrees.

[0367] In this way, the second rib segment 802, the fourth rib segment 804 and the fifth rib segment 805 jointly define a second placement position 810, and the fourth compressor is arranged at the second placement position 810, thereby enhancing the stiffness of the compressor base plate 60 at the second placement position 810, reducing the resonance between the fourth compressor and the compressor base plate 60, and achieving the effect of reducing noise.

[0368] Optionally, the third rib segment 803 and the fifth rib segment 805 are located on the same straight line. In this way, the bending strength of one side of the compressor bottom plate 60 along the length direction can be further enhanced, the anti-deformation capability of the compressor bottom plate 60 can be improved, and the rigidity of the compressor bottom plate 60 can be increased.

[0369] Optionally, the reinforcing rib 80 further includes a sixth rib segment 806, which is connected to the side of the fourth rib segment 804 away from the second rib segment 802 and forms a folded angle at the connection; the second rib segment 802, the fourth rib segment 804, the fifth rib segment 805 and the sixth rib segment 806 jointly define a second placement position 810.

[0370] By setting the sixth rib segment 806, the sixth rib segment 806 can be used together with the second rib segment 802, the fourth rib segment 804 and the fifth rib segment 805 to enclose a second placement position 810, thereby enhancing the bending strength of the compressor base plate 60 at the second placement position 810 in all directions and improving the anti-deformation ability, thereby enhancing the rigidity of the compressor base plate 60 at this location, limiting the fourth compressor at the second placement position 810, reducing the resonance between the fourth compressor and the compressor base plate 60, and achieving the effect of reducing noise.

[0371] Optionally, the second placement position 810 is provided with a fourth notch, and a fourth mounting protrusion is provided at the fourth notch for fixing a fourth universal wheel. The mounting method of the fourth universal wheel is the same as that of the third universal wheel, and will not be described in detail here. The fourth universal wheel is arranged opposite to the third universal wheel, and the fourth universal wheel and the third universal wheel jointly drive the compressor base plate 60 to move, thereby facilitating the movement of the refrigeration equipment.

[0372] Optionally, one of the first placement position 809 and the second placement position 810 extends along the length direction of the compressor base plate 60 (equivalent to the depth direction of the compressor chamber 403), and the other of the first placement position 809 and the second placement position 810 extends along the width direction of the compressor base plate 60 (equivalent to the width direction of the compressor chamber 403).

[0373] In this way, the longer end of the third compressor can be arranged along the length direction of the compressor bottom plate 60, and the longer end of the fourth compressor can be arranged along the width direction of the compressor bottom plate 60, or the longer end of the third compressor can be arranged along the width direction of the compressor bottom plate 60, and the longer end of the fourth compressor can be arranged along the length direction of the compressor bottom plate 60, so that the layout of the third compressor and the fourth compressor on the compressor bottom plate 60 is more compact. In addition, one of the first placement position 809 and the second placement position 810 extends along the length direction of the compressor bottom plate 60, and the other extends along the width direction of the compressor bottom plate 60, thereby increasing the bending strength of the compressor bottom plate 60 in the length direction and the width direction, improving the anti-deformation ability of the compressor bottom plate 60 in the length direction and the width direction, increasing the rigidity of the compressor bottom plate 60 in the length direction and the width direction, reducing the resonance between the third compressor and the fourth compressor and the compressor bottom plate 60, and achieving the effect of reducing noise.

[0374] Optionally, the reinforcing rib 80 also includes a seventh rib segment 807, which is arranged on the side of the first rib segment 801 away from the first placement position 809 and is arranged opposite to the first rib segment 801, one end of the seventh rib segment 807 is connected to the first rib segment 801, and the other end of the seventh rib segment 807 is connected to the second rib segment 802.

[0375] Optionally, the seventh rib segment 807 and the fourth rib segment 804 are located on the same straight line, which can further enhance the rigidity of the other side of the compressor base plate 60 along the length direction.

[0376] Optionally, the reinforcing rib 80 also includes an eighth rib segment 808, which is arranged between the first rib segment 801 and the seventh rib segment 807, one end of the eighth rib segment 808 is connected to the first rib segment 801, and a fold angle is formed at the connection, and the other end of the eighth rib segment 808 is connected to the seventh rib segment 807, and a fold angle is formed at the connection, and the eighth rib segment 808 is used to connect the first rib segment 801 and the seventh rib segment 807; the eighth rib segment 808 creates a gap between the first rib segment 801 and the seventh rib segment 807, so that the distribution of the reinforcing rib 80 on the compressor base plate 60 is more reasonable.

[0377] Optionally, the ratio of the width of the reinforcing rib 80 to the width of the first placement position 809 is in the range of 20%-40%; and / or the ratio of the width of the reinforcing rib 80 to the width of the compressor base plate 60 is in the range of 7%-20%; and / or the height of the reinforcing rib 80 is in the range of 9mm-11mm; and / or the area of ​​the reinforcing rib 80 accounts for 20%-30% of the area of ​​the compressor base plate 60. The width of the reinforcing rib 80 refers to the width of a rib segment, such as the width of any rib segment from the first to the eighth rib segments 808, and optionally, the widths of the first to the eighth rib segments 808 are equal; the area of ​​the reinforcing rib 80 refers to the total area of ​​the orthographic projection of all rib segments (the first to the eighth rib segments 808) on the compressor base plate 60.

[0378] Optionally, the ratio of the width of the reinforcing rib 80 to the width of the first placement position 809 is 25%, 30%, or 35%.

[0379] A vibration simulation test of the compressor base plate 60 is carried out, and the ratio range of the width of the reinforcing rib 80 to the width of the first placement position 809 is set to 20%-40%. Compared with setting the ratio range of the width of the reinforcing rib 80 to the width of the first placement position 809 to less than 20%, or setting the ratio range of the width of the reinforcing rib 80 to the width of the first placement position 809 to greater than 40%, according to the test results, when the ratio range of the width of the reinforcing rib 80 to the width of the first placement position 809 is set to 20%-40%, the effect of improving the stiffness of the compressor base plate 60 is better, which is beneficial to reducing resonance and reducing noise.

[0380] Optionally, the ratio of the width of the reinforcing rib 80 to the width of the compressor base plate 60 is 10%, 13%, or 16%.

[0381] According to the vibration simulation test, when the ratio of the width of the reinforcing rib 80 to the width of the compressor base plate 60 is set to 7%-20%, the effect of improving the stiffness of the compressor base plate 60 is better. Optionally, the height of the reinforcing rib 80 is 9mm, 10mm, and 11mm. When the height of the reinforcing rib 80 is increased to 9mm-11mm, compared with the height of the reinforcing rib 80 in the range of 3.5-5mm, the simulation test shows that the effect of improving the stiffness of the compressor base plate 60 is better, and the natural frequency of the compressor base plate 60 is effectively increased.

[0382] Optionally, the area of ​​the reinforcing rib 80 accounts for 23%, 25%, or 27% of the area of ​​the compressor base plate 60 .

[0383] Through simulation test, the area of ​​reinforcing rib 80 accounts for 20%-30% of the area of ​​compressor base plate 60, which has a great effect of improving stiffness. When the area of ​​reinforcing rib 80 accounts for less than 20% of the area of ​​compressor base plate 60, the effect of improving stiffness of compressor base plate 60 is not obvious, and compressor base plate 60 is easy to deform. When the area of ​​reinforcing rib 80 accounts for more than 30% of the area of ​​compressor base plate 60, the first placement position 809 and the second placement position 810 are occupied, so that compressor base plate 60 loses effective loading space.

[0384] The above description and the accompanying drawings sufficiently illustrate the embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations. Unless explicitly required, individual components and functions are optional, and the order of operations may vary. Portions and features of some embodiments may be included in or replace portions and features of other embodiments. The embodiments of the present disclosure are not limited to the structures described above and shown in the accompanying drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A refrigerator, characterized in that: include: A box body, defining a compressor cabin; A refrigeration system, comprising a fifth compressor and a sixth compressor, wherein the fifth compressor and the sixth compressor are located in the compressor cabin; The compressor bottom plate comprises a first bottom plate and a second bottom plate, wherein the first bottom plate and the second bottom plate are spaced apart and arranged at the bottom of the compressor cabin; Among them, the fifth compressor and the sixth compressor are arranged side by side in the compressor cabin, or the length direction of the fifth compressor and the length direction of the sixth compressor are arranged crosswise, one of the fifth compressor and the sixth compressor is located above the first bottom plate, and the other of the fifth compressor and the sixth compressor is located above the second bottom plate.

2. The refrigerator according to claim 1, characterized in that: When the length direction of the fifth compressor and the length direction of the sixth compressor are arranged to intersect, the range of the angle α between the length direction of the fifth compressor and the length direction of the sixth compressor is 10°≤α≤170°; or, When the length direction of the fifth compressor and the length direction of the sixth compressor are arranged to cross each other, the range of the angle α between the length direction of the fifth compressor and the length direction of the sixth compressor is 50°≤α≤130°.

3. The refrigerator according to claim 2, characterized in that: The fifth compressor and the sixth compressor are arranged vertically.

4. The refrigerator according to claim 2, characterized in that: The length direction of one of the fifth compressor and the sixth compressor extends in the depth direction of the compressor chamber, and the length direction of the other of the fifth compressor and the sixth compressor extends in the width direction of the compressor chamber.

5. The refrigerator according to claim 2, characterized in that: The fifth compressor and the sixth compressor are arranged sequentially along the depth direction of the compressor chamber.

6. The refrigerator according to claim 1, characterized in that: The refrigeration system includes: A high-temperature refrigeration cycle circuit includes a fifth compressor and an evaporation portion, and a first refrigerant flows inside the high-temperature refrigeration cycle circuit; The low-temperature refrigeration cycle circuit includes a sixth compressor and a condensing part, and a second refrigerant circulates inside the low-temperature refrigeration cycle circuit. The second refrigerant in the condensing part can exchange heat with the first refrigerant in the evaporating part, and the evaporating part and the condensing part form an evaporative condenser.

7. The refrigerator according to claim 6, characterized in that: The box also includes: The inner container has a bottom wall portion that protrudes upward to form a step; The outer shell is located outside the inner tank, and the outer shell and the step enclose the compressor cabin; a partition plate located at an upper portion of the compressor cabin and below the step, the fifth compressor and the sixth compressor being located below the partition plate; The evaporative condenser is located between the inner container and the outer shell or between the partition and the inner container.

8. The refrigerator according to claim 7, characterized in that: The low temperature refrigeration cycle also includes: a third pipeline connected between the outlet of the sixth compressor and the inlet of the condensing part; A low temperature stage evaporator, the inlet of which is connected to the outlet of the condensation section; a fourth pipeline connected between the outlet of the low temperature stage evaporator and the inlet of the sixth compressor; The third pipeline and the fourth pipeline are connected or in contact with each other and form a first regenerator, and the first regenerator is used to exchange heat between the second refrigerant in the third pipeline and the second refrigerant in the fourth pipeline; The first heat regenerator is located between the inner container and the outer shell or between the partition plate and the inner container.

9. The refrigerator according to any one of claims 1 to 8, characterized in that: Also includes: The box body is further provided with welding holes, and the fifth compressor and / or the sixth compressor are arranged corresponding to the welding holes; and / or, The press cabin is located at at least one of the left side of the box body, the right side of the box body, and the rear side of the box body.

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