Refrigerator

Abstract

The invention 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] As people's living standards improve, the preservation of food storage is gaining increasing attention, especially for high-end ingredients. Low-temperature storage, particularly below -50°C, can significantly improve food quality and shelf life. For example, wild yellow croaker, which loses its flavor after one month in a conventional refrigerator or freezer, retains its freshness after six months at -60°C.

[0003] A horizontal freezer is disclosed in the related art, which includes a high-temperature refrigeration cycle circuit, including a high-temperature compressor and an evaporator; a low-temperature refrigeration cycle circuit, including a low-temperature compressor and a condenser, and the evaporator and the condenser 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 laterally spaced apart, the first inner liner enclosing a first storage compartment, the second inner liner enclosing a second storage compartment, the first compressor compartment being located below the first inner liner, the high-temperature compressor being located in the first compressor compartment, the second compressor compartment being located below the second inner liner, the low-temperature compressor being located in the second compressor compartment, the high-temperature refrigeration cycle circuit supplies cooling to the first storage compartment, and the low-temperature refrigeration cycle circuit supplies cooling to the second storage compartment.

[0004] During the implementation of the embodiments of the present disclosure, it was found that at least the following problems exist in the related art:

[0005] The horizontal freezer in the related art is provided with two press compartments and two inner liners to achieve low-temperature storage of the freezer. However, the two press compartments occupy the storage space of the inner liners, which still causes the storage space of the inner liners to become smaller. Moreover, two press compartments are respectively provided for the two inner liners, 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 this application, and therefore may include information that does not constitute prior art known to ordinary technicians in this field. Summary of the Invention

[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 elements or delineate the scope of protection of these embodiments, but rather serves as a prelude to the detailed description that follows.

[0008] The embodiments of the present disclosure provide a refrigerator, which can realize 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 by the embodiments of the present disclosure can achieve the following technical effects:

[0011] In the refrigerator of the disclosed embodiment, the fifth and sixth compressors are both housed in the same compressor compartment. Depending on the size of the compressor compartment, the two compressors can be arranged side by side or crosswise. This does not increase the height of the compressor compartment and eliminates the need for two separate compressor compartments. This reduces the storage space occupied by the compressor compartment within the refrigerator liner and allows for the storage of larger items, thereby improving the storage space and overall 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. These exemplary descriptions and drawings do not limit the embodiments. Elements with the same reference numerals in the drawings are shown as similar elements. The drawings do not constitute a scale limitation. In addition,

[0014] Figure 1 is a structural 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 This is a schematic diagram of a partial structure of a refrigeration device provided by an embodiment of the present disclosure;

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

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

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

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

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

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

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

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

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

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

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

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

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

[0032] Figure 15 This 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] Figure 16 is a schematic diagram of the matching structure of another compressor base plate and compressor provided by an embodiment of the present disclosure;

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

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

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

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

[0038] Figure 21 is a structural schematic diagram of another cascade refrigeration system provided by an embodiment of the present disclosure;

[0039] Figure 22 This is a flow chart of a control method for a refrigeration device provided by an embodiment of the present disclosure;

[0040] Figure 23 This is a flow chart of a control method for refrigeration equipment provided by an embodiment of the present disclosure;

[0041] Figure 24 is a schematic diagram of another control method for refrigeration equipment provided by an embodiment of the present disclosure;

[0042] Figure 25 is a schematic diagram of another control method for refrigeration equipment provided by an embodiment of the present disclosure;

[0043] Figure 26 is a schematic diagram of another control method for refrigeration equipment provided by an embodiment of the present disclosure;

[0044] Figure 27 This is a flow chart of another control method for refrigeration equipment provided by an embodiment of the present disclosure;

[0045] Figure 28 This is a flow chart of another control method for refrigeration equipment provided by an embodiment of the present disclosure;

[0046] Figure 29 This is a flow chart of another control method for refrigeration equipment provided by an embodiment of the present disclosure;

[0047] Figure 30 This is a flow chart of another control method for refrigeration equipment provided by an embodiment of the present disclosure.

[0048] Reference numerals:

[0049] 10. High-temperature refrigeration cycle; 101. Evaporation unit; 102. High-temperature compressor; 103. First pipeline; 104. High-temperature condenser; 105. High-temperature throttling element; 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 drier; 306, second filter drier; 307 , third filter drier; 308, pre-cooling tube; 401, outer shell; 4011, first welding hole; 4012, air outlet; 402, liner; 403, compressor cabin; 50, reinforcement iron; 501, frame; 5011, first frame; 5012, second frame; 502, vertical beam; 503, first crossbeam; 504, second crossbeam; 60, compressor baseplate; 601, first baseplate; 6011, first reinforcement 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

[0050] In order to be able to understand the features and technical content 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 accompanying drawings are for reference only and are not used to limit the embodiments of the present disclosure. In the following technical description, for the sake of 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.

[0051] In the description and claims of the embodiments of the present disclosure, as well as in the accompanying drawings, the terms "first," "second," and the like are used to distinguish similar items and are not necessarily used to describe a particular order or precedence. It should be understood that such terms are interchangeable where appropriate to describe the embodiments of the present disclosure. Furthermore, the terms "including," "having," and any variations thereof are intended to cover non-exclusive inclusions.

[0052] 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 having 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.

[0053] Furthermore, the terms "disposed," "connected," and "fixed" should be interpreted broadly. For example, "connected" can mean a fixed connection, a removable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be a direct connection, an indirect connection through an intermediary, or an internal connection between two devices, elements, or components. Those skilled in the art will understand the specific meanings of these terms in the embodiments of this disclosure based on the specific circumstances.

[0054] Unless otherwise stated, the term "plurality" means two or more.

[0055] The term "and / or" describes an association between objects, indicating that three relationships can exist. For example, A and / or B means: A or B, or A and B.

[0056] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present disclosure can be combined with each other.

[0057] Combine Figures 1 to 21 As shown, the embodiments of the present disclosure provide a refrigeration device that can provide a low-temperature environment for low-temperature storage of food, medicine, or other items. For example, the refrigeration device can be a refrigerator, a freezer, a freezer, a biomedical refrigeration device, or other refrigeration equipment.

[0058] The refrigeration equipment includes a cascade refrigeration system. The cascade refrigeration system can be a two-stage cascade cycle system, a three-stage cascade cycle system, or a four-stage cascade cycle system. The number of cascade stages is not specifically limited. This embodiment uses a cascade refrigeration system having a two-stage cascade cycle system as an example. Those skilled in the art should be fully capable of expanding upon this.

[0059] like Figures 1 to 4As shown, an 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 within the high-temperature refrigeration cycle circuit 10, and a second refrigerant circulates within 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.

[0060] Optionally, the high-temperature refrigeration cycle 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.

[0061] 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.

[0062] In the disclosed embodiment, the evaporator 101 within the high-temperature refrigeration cycle 10 can exchange heat with the evaporator 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 evaporator 101 absorbs the heat of the second refrigerant in the condenser 201 to cool the second refrigerant. The cooled second refrigerant is then further cooled by the low-temperature refrigeration cycle 20, thereby achieving a low temperature for the refrigeration equipment. Both the low-temperature throttling element 206 and the high-temperature throttling element 105 can be capillaries or electronic expansion valves.

[0063] Optionally, the evaporation section 101 includes an evaporation tube, and the condensation section 201 includes a condensation tube, and the evaporation tube and the condensation tube are close to each other (fitting or close to each other) to achieve heat exchange between the evaporation tube and the condensation tube. Optionally, the evaporation section 101 and the condensation section 201 can also be in the form of a sleeve to achieve heat exchange.

[0064] Optionally, the high-temperature refrigeration cycle 10 further includes a third filter dryer 307, which is located between the high-temperature condenser 104 and the high-temperature throttle 105. The low-temperature refrigeration cycle 20 further includes a second filter dryer 306, which is located between the condensing section 201 and the low-temperature throttle 206, and is used to dry and filter the low-temperature refrigerant flowing out of the condensing section 201.

[0065] 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 condenser 104. In this state, the compressor lubricating oil and the refrigerant medium are better in mutual solubility, and the drying filter intercepts and adsorbs less compressor lubricating oil, so the risk of oil blockage is lower, and the drying filter has a better adsorption and interception effect on other impurities.

[0066] Alternatively, as Figure 1 As shown, the high-temperature throttling element 105 is connected to or in contact with the first pipeline 103 to form a return air pipe assembly 304. The return air pipe assembly 304 is used to exchange heat between the first refrigerant in the high-temperature throttling element 105 and the first refrigerant in the first pipeline 103. In this way, after the first refrigerant in the evaporator 101 and the condenser 201 have exchanged heat, it flows along the first pipeline 103 into the return air pipe assembly 304. There, the first refrigerant in the first pipeline 103 exchanges heat with the high-temperature throttling element 105 to become a low-pressure, room-temperature gaseous refrigerant, which then enters the high-temperature compressor 102 to complete the cycle. Here, the return air pipe assembly 304 can cool the first refrigerant flowing through the high-temperature throttling element 105, thereby lowering the temperature of the first refrigerant flowing into the evaporator 101 and improving the heat exchange efficiency within the evaporative condenser 30.

[0067] 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 energy. 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.

[0068] 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, high-pressure superheated gas. After passing through the third pipeline 203, it enters the evaporative condenser 30, where the condenser dissipates heat and becomes a subcooled liquid, a saturated liquid, or a gas-liquid two-phase. It then enters the low-temperature throttling device 206, where it is throttled to a low-temperature, low-pressure state and enters the low-temperature evaporator 204 for refrigeration, thus enabling low-temperature storage below -45°C. After absorbing heat in the low-temperature evaporator 204 and becoming a superheated gas, the second refrigerant is drawn into the low-temperature compressor 202 to complete the refrigeration cycle. Optionally, the high-temperature throttling device 105 and the first pipeline 103 exchange heat using contact heat exchange or a casing-in-tube method.

[0069] 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 , which is used to exchange heat between the second refrigerant in the third pipeline 203 and the second refrigerant in the fourth pipeline 205 .

[0070] In the embodiment of the present disclosure, 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, heat is dissipated in the first regenerator 301, and part of the second refrigerant becomes a gas-liquid two-phase state. The second refrigerant after heat dissipation then 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 state. Thereafter, it enters the low-temperature throttling device 206 to be throttled to a low-temperature and low-pressure state and enters the low-temperature evaporator 204 for refrigeration, thereby achieving low-temperature storage below -45°C. After absorbing heat in the low-temperature evaporator 204, the second refrigerant flows through the fourth pipe 205 to the cold end of the first regenerator 301. After absorbing heat from the hot end and becoming superheated gas, it is drawn into the low-temperature compressor 202, completing the refrigeration cycle. The provision of the first regenerator 301 reduces the temperature difference between the fourth pipe 205 and the ambient temperature, thereby resolving the issue of frosting on the fourth pipe 205 of the low-temperature refrigeration cycle 20, particularly within the compressor compartment 403.

[0071] Optionally, the third pipeline 203 and the fourth pipeline 205 perform heat exchange in a contact heat exchange or sleeve heat exchange manner.

[0072] Optionally, the cascade refrigeration system further includes a first filter dryer 305, which is disposed in the third pipeline 203 and 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 it flows into the evaporative condenser 30, thereby reducing impurities flowing into the condensing unit 201 and improving the heat exchange efficiency of the evaporative condenser 30.

[0073] like Figure 3 As shown, optionally, the low-temperature refrigeration cycle circuit 20 further includes a pre-cooling pipe 308, which is connected between the outlet of the third pipeline 203 and the inlet of the condensation part.

[0074] In the disclosed embodiment, the pre-cooling pipe 308 is used as a "condenser" 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 along the third pipeline 203 into the pre-cooling pipe 308 for pre-cooling. This reduces the temperature of the high-temperature and high-pressure superheated gas to a temperature close to the ambient temperature, thereby improving the subsequent heat exchange efficiency of the second refrigerant.

[0075] Alternatively, as Figure 3 As shown, the low-temperature refrigeration cycle 20 includes a precooling pipe 308, the hot end of the first regenerator 301, and a first filter drier 305, arranged sequentially along the flow direction of the second refrigerant. The precooling pipe 308 is located upstream of the first regenerator 301. The second refrigerant flowing through the precooling pipe 308, after passing through the third pipe 203 and entering the first regenerator 301, dissipates heat within the first regenerator 301, partially transforming into a gas-liquid two-phase state. The second refrigerant, after dissipating heat, is then filtered by the first filter drier 305 and flows into the evaporative condenser 30. After dissipating heat, the second refrigerant becomes a subcooled liquid, a saturated liquid, or a gas-liquid two-phase state. It then enters the low-temperature throttle 206, throttled to a low temperature and low pressure, and enters the low-temperature evaporator 204 for refrigeration, thus achieving low-temperature storage below -45°C. After absorbing heat in the low-temperature evaporator 204, the second refrigerant flows through the fourth pipe 205 to the cold end of the first regenerator 301. After absorbing heat from the hot end, it becomes a superheated gas and is then drawn into the low-temperature compressor 202, completing the refrigeration cycle.

[0076] 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 condenser through the precooling pipe 308. The improvement of locating the precooling pipe 308 in the middle of the third pipeline is the same as the improvement of locating the precooling pipe at the entrance of the third pipeline in this application, and will not be repeated.

[0077] 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 regenerator 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.

[0078] Here, the pre-cooling pipe 308 is arranged in a space such as the 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 pre-cooling 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.

[0079] Based on the various layout embodiments of the drying filters described above, the cascade refrigeration system provided in the present application can be provided with one or more drying filters, and the specific location of each drying filter can refer to any one of the embodiments shown above.

[0080] like Figure 4 As shown, in other optional embodiments, the second pipeline 106 is in contact with or connected to the fourth pipeline 205 to form a second regenerator 302, which is used to exchange heat between the first refrigerant in the second pipeline 106 and the second refrigerant in the fourth pipeline 205.

[0081] 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 subcooled liquid or a saturated liquid or a gas-liquid two-phase, then enters the second regenerator 302, exchanges heat with the second refrigerant in the fourth pipe 205 of the low-temperature refrigeration cycle 20, and then flows into the high-temperature throttling device 105. This can further reduce the condensation temperature of the second refrigerant or increase the degree of subcooling. After being cooled in the second regenerator 302, the second refrigerant flows through the return pipe group 304, passes through the high-temperature throttling device 105 for heat exchange, and becomes a low-pressure and normal-temperature refrigerant gas, and enters the high-temperature compressor 102 to complete the cycle.

[0082] Optionally, the second pipeline 106 and the fourth pipeline 205 exchange heat by contact or in a casing form.

[0083] Alternatively, as 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.

[0084] 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, high-pressure superheated gas. This gas then flows along the third pipeline 203 into the pre-cooling pipe 308 for pre-cooling. This reduces the temperature of the high-temperature, high-pressure superheated gas to near the ambient temperature. After dissipating heat, the second refrigerant enters the evaporative condenser 30, where it dissipates heat and becomes a subcooled liquid, a saturated liquid, or a gas-liquid two-phase gas. It then enters the second filter dryer 306 for filtration, before being throttled by the low-temperature throttle 206 to a low-temperature, low-pressure state and entering the low-temperature evaporator 204 for refrigeration. The second filter dryer 306 prevents clogging of the low-temperature throttle 206. This enables low-temperature storage below -45°C. After absorbing heat from the low-temperature evaporator 204, the second refrigerant flows through the fourth pipeline 205 into the cold end of the second regenerator 302. After absorbing heat from the hot end and becoming a superheated gas, this prevents frost formation on the fourth pipeline 205 within the compressor compartment 403. The second refrigerant is then drawn into the low-temperature compressor 202, completing the refrigeration cycle.

[0085] like Figure 21 As shown, in other optional embodiments, the cascade refrigeration system further includes a fifth pipeline 107 and a high-temperature evaporator 108. The fifth pipeline 107 is connected between the outlet of the high-temperature throttling member 105 and the inlet of the evaporation portion 101, and the high-temperature evaporator 108 is connected between the outlet of the high-temperature throttling member 105 and the first pipeline 103. Optionally, there are multiple high-temperature throttling members 105, each of which includes a first capillary tube 1051 and a second capillary tube 1052. 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 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. The solenoid valve 109 is used to control the communication 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 assembly 304.

[0086] In the disclosed embodiment, the second refrigerant in the high-temperature refrigeration cycle 10 flows through the high-temperature condenser 104 to become a subcooled liquid, a saturated liquid, or a gas-liquid dual phase. It then enters the return pipe assembly 304 and enters the two parallel high-temperature throttling devices 105 in the return pipe assembly 304 to cool down. It then flows to the high-temperature evaporator 108 and the evaporation section 101, releasing its cooling capacity, before returning to the return pipe assembly 304. After heat exchange with the high-temperature throttling devices 105 in the return pipe assembly 304, it becomes a low-pressure, room-temperature refrigerant gas, which then enters the high-temperature compressor 102 to complete the cycle. The arrangement of the high-temperature evaporator 108, the solenoid valve 109, and the parallel high-temperature throttling devices 105 allows the high-temperature refrigeration cycle 10 to operate in either a cascade or standalone mode. This allows the flow path of the high-temperature refrigeration cycle 10 to be adjusted during startup of the cascade refrigeration system, improving startup stability and reducing noise. Using the cascade refrigeration system of the disclosed embodiment, if the actual temperature of the storage chamber meets the startup conditions, the low-temperature refrigeration cycle can be activated first to perform cooling. By repeatedly starting and stopping the low-temperature refrigeration cycle, the low-temperature refrigeration demand can be met. During the aforementioned time period when the low-temperature refrigeration cycle is operating, the high-temperature refrigeration cycle is temporarily shut down or operates independently without exchanging heat with the low-temperature refrigeration system. This greatly reduces the overall operating noise of the refrigeration equipment, making the refrigeration equipment more applicable in a variety of scenarios.

[0087] 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 element 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 function as described above and are not further described here.

[0088] Optionally, the evaporation section 101 and the condensation section 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 initially powered on, 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 pre-cooling capacity to ensure that the pressure is controllable.

[0089] Optionally, the first refrigerant and the second refrigerant are both hydrocarbons and / or hydrofluoroolefins with a critical pressure ≤ 4.7 MPa. Critical pressure refers to the pressure of a substance in its critical state, specifically the minimum pressure required to liquefy a gas at its critical temperature. This refers to the saturated vapor pressure of a liquid at its critical temperature. The molar volume of a substance at its critical temperature and pressure is called its critical molar volume. The state at this critical temperature and pressure is called its critical state.

[0090] In the embodiment of the present disclosure, the first refrigerant and the second refrigerant both use hydrocarbons and / or hydrofluoroolefin refrigerants with a critical pressure of ≤4.7 MPa. This type of refrigerant has a low critical pressure and can achieve gas-liquid state conversion when the system pressure is low. In this way, the system can operate at a lower pressure, reducing the operating noise. At the same time, the boiling point of hydrocarbons and / or hydrofluoroolefin refrigerants with a critical pressure of ≤4.7 MPa 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.

[0091] Optionally, the critical pressure of the first refrigerant is ≤4 MPa. This can further reduce the pressure in the high-temperature refrigeration cycle 10 and thus reduce noise.

[0092] 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 a mixture of 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.

[0093] It can be understood that the second refrigerant can be only R290 or R1270, a refrigerant mixed with R290 and R1270, a refrigerant mixed with R290 and one or more of R600, R1243zf, and R1234yf, or a refrigerant mixed with R1270 and one or more of R600, R1243zf, and R1234yf.

[0094] In the embodiment of the present disclosure, 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.

[0095] In the disclosed embodiment, as shown in Table 1, the critical pressure of each refrigerant is less than 4.7 MPa. The boiling point of the second refrigerant is less than or equal to the boiling point of the first refrigerant, thereby facilitating heat exchange between the first and second refrigerants in the evaporative condenser 30. Using the refrigerant type of the disclosed embodiment, when the cascade refrigeration system employs an R600a compressor, the operating noise of the entire system is between 30 and 38 dB(A), significantly reducing system operating noise.

[0096] Table 1

[0097]

[0098] 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.

[0099] For example, the first refrigerant in the high-temperature refrigeration cycle 10 may be any one of R600, R600a, R290, R1270, R1243zf, and R1234yf, and the second refrigerant in the low-temperature refrigeration cycle 20 may be any one of R290 and R1270.

[0100] Optionally, the first refrigerant in the high-temperature refrigeration cycle 10 is a mixed refrigerant, and / or the second refrigerant in the low-temperature refrigeration cycle 20 is a mixed refrigerant. When the second refrigerant in the low-temperature refrigeration cycle 20 is a mixed refrigerant, the proportion of R290 or R1270 is greater than 40%. This allows the system to operate at a lower operating pressure.

[0101] 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.

[0102] The high-pressure side of the low-temperature refrigeration cycle 20 refers to the portion between the discharge port of the low-temperature compressor 202 and the upstream portion of the suction port of the low-temperature throttle 206 within the low-temperature refrigeration cycle 20, in the flow direction of the second refrigerant. The low-pressure side of the low-temperature refrigeration cycle 20 refers to the portion between the discharge port of the low-temperature throttle 206 and the suction port of the low-temperature compressor 202, in the flow direction of the second refrigerant.

[0103] In the disclosed embodiment, the low-temperature refrigeration cycle 20 is configured with the aforementioned parameters to reduce the pressure ratio and pressure differential. When the low-temperature refrigeration cycle 20 is in operation, the low-temperature compressor 202 within the circuit can have lower suction and discharge pressures. This reduces compressor vibration and improves efficiency, thereby achieving low noise. The high-pressure side of the low-temperature refrigeration cycle 20 includes, among other things, the third pipeline 203, the condenser 201, and the first filter drier 305. As shown in Table 2, the high-pressure side pressure of the low-temperature refrigeration cycle in conventional external cascade refrigeration systems is often greater than 0.9 MPa, resulting in relatively high noise levels. In the disclosed embodiment, the second refrigerant within the low-temperature refrigeration cycle 20 utilizes R290, R1270, or a mixture of the two. After precooling through the evaporative condenser 30, the high- and low-pressure side pressures of the low-temperature cycle refrigeration circuit can be set within the aforementioned ranges. This reduces the operating pressure within the low-temperature refrigeration cycle, thereby enabling the noise level of the low-temperature compressor 202 to be controlled between 30 and 45 dB(A).

[0104] Table 2

[0105]

[0106] Optionally, the high-pressure side pressure range of the low-temperature refrigeration cycle loop 20 in a stable operating state is configured to be 0.2 MPa-0.9 MPa.

[0107] For example, the high-pressure side pressure range of the low-temperature refrigeration cycle loop 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.

[0108] 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 effect.

[0109] Optionally, the low-pressure side pressure range of the low-temperature refrigeration cycle 20 in a stable operating state is configured to be 0.02 MPa-0.05 MPa. This can further reduce the temperature in the box and improve the freshness of the stored food.

[0110] Table 3

[0111]

[0112] For example, the low-pressure side pressure range of the low-temperature refrigeration cycle loop 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.

[0113] 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 loop 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 loop 20 in a stable operating state is configured to be lower than one atmosphere.

[0114] In the embodiment of the present disclosure, the ambient atmospheric pressure is usually 0.101 MPa, the first refrigerant is R600a and / or and / or one or more of R600, R1243zf, and R1234yf, and 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 operated at negative pressure. In the refrigeration system, the lower the operating pressure, the lower the noise generated by the compressor and refrigerant, and the lower the operating pressure, the lower the condensing 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. This can achieve low-temperature storage below -45°C, while ensuring that the refrigeration equipment operates at a low noise level of less than 40dB(A).

[0115] 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 loop 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 loop 20 in a stable operating state is configured to be lower than one atmosphere.

[0116] 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).

[0117] In the related art, conventional single-stage refrigeration systems using R290 refrigerant have high operating pressures, with the high-pressure side pressure typically exceeding 1 MPa and the low-pressure side pressure typically between 0.08 MPa and 0.15 MPa. The compressor needs to operate at high pressure, and high requirements for starting performance and pressure resistance result in high compressor weight and high vibration. In contrast, systems using R600a refrigerant typically operate at high-pressure side pressures between 0.3 MPa and 0.6 MPa, and low-pressure side pressures between 0.04 MPa and 0.08 MPa. This results in low system operating pressures, a light compressor, and low vibration, but it cannot achieve low temperatures below -45°C. To achieve low temperatures around -60°C, low-temperature refrigeration systems typically use low-temperature refrigerants such as R170, R1150, R507, and R508B. These refrigerants operate at higher pressures than R290, achieving low temperatures but failing to address the noise issue. Therefore, the embodiment of the present disclosure uses 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, which can achieve low temperatures while ensuring noise.

[0118] Table 4 shows that when pressure drops below 0.01 MPa, conventional capillary throttling becomes difficult, resulting in very low refrigeration flow and a correspondingly low cooling capacity. When pressure exceeds 1.3 MPa, high compressor vibration and noise levels result. Therefore, R170 and R1150, as currently used in the industry, can achieve temperatures as low as -60°C, but their noise levels are uncontrollable. Therefore, choosing R290, R1270, or a mixture of the two as the second refrigerant can achieve both low noise and low temperatures.

[0119] Table 4

[0120]

[0121]

[0122] Preferably, when the third pipeline 203 and the fourth pipeline 205 are connected or in contact with each other to form the first regenerator 301, the first refrigerant is R600a, and / or the second refrigerant is R290. This can achieve low temperature and noise reduction at the same time.

[0123] 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.

[0124] In the disclosed embodiment, as shown in Table 5, the unit volume cooling capacity of R290 and R1270 refrigerants is 2.8 to 5.1 times that of R600 and R600a refrigerants. That is, to achieve the same cooling capacity, the exhaust volume of R290 and R1270 compressors is 2.8 to 5.1 times smaller than that of R600 and R600a. Therefore, when the high-temperature stage compressor 102 is an R600a compressor or an R600 compressor, 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. When the high-temperature stage compressor 102 is an R290 compressor or an R1270 compressor, 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.

[0125] Table 5

[0126]

[0127] Optionally, when the second refrigerant is R290 and / or R1270, the outlet temperature of the low-pressure pipe of the condensing portion 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.

[0128] 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.

[0129] The cascade refrigeration system provided by the embodiment of the present disclosure is adopted. By providing an evaporative condenser 30, the high-temperature refrigeration cycle 10 is used to cool the evaporative condenser 30. When the temperature of the evaporative condenser 30 drops, the low-temperature refrigeration cycle 20 is started to pre-cool the second refrigerant in the low-temperature refrigeration cycle 20 in advance. In the solution of the present application, the internal volume of the evaporation portion 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 internal volume of the condensation portion 201 is set to within 2% to 80% of the total volume of the low-temperature refrigeration cycle 20. This can maintain the cooling effect of the high-temperature refrigeration cycle 10 on the second refrigerant in the low-temperature refrigeration cycle 20, and control the cooling temperature of the second refrigerant 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.

[0130] It can be understood that the evaporator 101 and the condenser 201 are both refrigerant coils, wherein the internal volume of the evaporator 101 and the condenser 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 locations in the high-temperature refrigeration cycle 10 through which the first refrigerant flows, and the total volume of the low-temperature refrigeration cycle 20 refers to the sum of the volumes of all locations in the low-temperature refrigeration cycle 20 through which the second refrigerant flows.

[0131] Optionally, the ratio of the internal volume V1 of the evaporator 101 to the total volume Vh of the high-temperature refrigeration cycle 10 is set to: 10% Vh ≤ V1 ≤ 70% Vh. Thus, setting the volume of the evaporator 101 to between 10% and 70% of the total volume of the high-temperature refrigeration cycle 10 allows the evaporator 101 to fully utilize the first refrigerant in the high-temperature refrigeration cycle 10 for cooling. While generating sufficient cooling capacity at the evaporator 101, it also prevents excessive refrigerant pressure in the high-temperature refrigeration cycle 10, improves the refrigeration efficiency of the high-temperature refrigeration cycle 10, and reduces noise generated by the high-temperature refrigeration cycle 10.

[0132] Optionally, the ratio of the internal volume V1 of the evaporation section 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 section 101 to between 20% and 50% of the total volume of the high-temperature refrigeration cycle 10, the refrigeration capacity of the evaporation section 101 can be maintained to the maximum extent, the condensing section 201 can be better cooled, the minimum refrigeration temperature of the entire cascade refrigeration system can be lowered, and the speed of temperature drop can be increased, so that the refrigeration temperature reaches the minimum value in less time, energy consumption is reduced, and the speed of power-on startup into the low-temperature refrigeration working state is increased. At the same time, the noise level during the refrigeration process can be kept at a low level, effectively reducing refrigeration noise and facilitating the application of deep refrigeration technology in households.

[0133] 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.

[0134] Among them, when 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 15%, the ratio of the internal volume V1 of the evaporating part 101 to the total volume Vh of the high-temperature refrigeration cycle 10 is respectively 20%, 45% and 60% as comparative examples, the initial power-on pre-cooling 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 min, the 50kg high load cooling speed to -18°C h, the 50kg high load cooling maximum condensing pressure MPa, the power consumption kWh / 24h when the ambient temperature is 32°C and the noise dB (A) are verified, and the results shown in Table 6 below are obtained:

[0135] Table 6

[0136]

[0137]

[0138] By comparison, it can be seen that when the volume V1 of the evaporation part 101 accounts for 45% of the total volume Vh of the high-temperature refrigeration cycle 10, the empty box cooling depth is the lowest, the empty box is cooled to -60°C the fastest, and the power consumption is the lowest when the ambient temperature is 32°C and the temperature drops to -60°C. In addition, 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 a quiet effect. Accordingly, when the volume V1 of the evaporation part 101 accounts for 45% of the total volume Vh of the high-temperature refrigeration cycle 10, a better effect is achieved.

[0139] 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 mixes with the high-temperature portion of the second refrigerant, lowering the temperature of the entire refrigerant, thereby avoiding the condensation pressure in the low-temperature circulation pipeline, maintaining the temperature of the second refrigerant within a reasonable range, and thus preventing excessive pressure fluctuations in the low-temperature circulation pipeline, while maintaining refrigeration efficiency and effectively reducing the increase in noise caused by excessive pressure and excessive flow rate of the second refrigerant.

[0140] Optionally, the ratio of the internal volume V2 of the condensing section 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 section 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 condensing pressure of the low-temperature refrigeration cycle 20 can be prevented from being too high, so that the minimum refrigeration temperature of the entire cascade refrigeration system is lower, and the speed of temperature drop is increased, so that the time required for the refrigeration temperature to reach the minimum value is shortened, energy consumption is reduced, and the speed of power-on startup into the low-temperature refrigeration working state is increased. At the same time, the noise level during the refrigeration process can be kept at a low level, effectively reducing the refrigeration noise, and facilitating the application of deep refrigeration technology in households.

[0141] 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 can also be set to: V2 = 5% Vc or V2 = 35% Vc.

[0142] Among them, when the ratio of the internal volume V1 of the evaporation part 101 to the total volume Vh of the high-temperature refrigeration cycle loop 10 is 45%, the ratio of the internal volume V2 of the condensation part 201 to the total volume Vc of the low-temperature refrigeration cycle loop 20 is 5%, 15% and 35% respectively as comparative examples, and the initial power-on pre-cooling 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 min, the 50kg high load cooling speed to -18°C h, the 50kg high load cooling maximum condensing pressure MPa, the power consumption kWh / 24h from an ambient temperature of 32°C to -60°C, and the noise dB (A) are verified, and the results shown in Table 7 below are obtained:

[0143] Table 7

[0144]

[0145]

[0146] 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 cooling depth is the lowest, the empty box is cooled to -60°C the fastest, and the power consumption is the lowest when the ambient temperature is 32°C and the temperature drops to -60°C. In addition, 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 a quiet effect. Accordingly, 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.

[0147] 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.

[0148] Optionally, an expansion tank is provided at the exhaust port of the low-temperature compressor 202. Since the exhaust port of the low-temperature compressor 202 discharges high-pressure refrigerant, excessively high pressure and high flow rate can increase noise. Therefore, by providing 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, thereby effectively reducing noise.

[0149] 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. Thus, 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, the pressure and flow rate of the second refrigerant can be reduced while maintaining sufficient pressure at the point where the second refrigerant enters the evaporative condenser 30, thereby improving heat exchange efficiency. Furthermore, the noise within the low-temperature refrigeration cycle 20 can be reduced while maintaining the cooling effect of the low-temperature refrigeration cycle 20.

[0150] 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. Thus, 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, thereby reducing noise while maintaining the cooling effect of the low-temperature refrigeration cycle 20.

[0151] 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. Thus, setting the internal volume of the expansion tank to 5% of the total volume of the low-temperature refrigeration cycle 20 can minimize noise within the low-temperature refrigeration cycle 20 while maintaining the cooling effect of the low-temperature refrigeration cycle 20.

[0152] Optionally, the evaporative condenser 30 further includes a heat exchange unit. The evaporating unit 101 and the condensing unit 201 are connected to the same heat exchange unit. This improves the heat exchange efficiency between the evaporating unit 101 and the condensing unit 201, thereby better utilizing the cooling capacity generated by the high-temperature refrigeration cycle 10 to cool the refrigerant in the low-temperature refrigeration cycle 20, thereby improving the cooling efficiency of the entire cascade refrigeration system. Furthermore, through the rapid heat exchange between the two, the low-temperature refrigeration cycle 20 can achieve a rapid cooling effect, thereby increasing the overall cooling speed.

[0153] The heat exchange portion can be a single metal heat exchange medium, with the evaporation portion 101 and the condensation portion 201 interlaced and inserted into the metal heat exchange medium. Alternatively, the heat exchange portion can be a liquid heat exchange medium enclosed in an insulated box, with the evaporation portion 101 and the condensation portion 201 interlaced and submerged in the liquid heat exchange medium.

[0154] 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. Thus, in order to reduce the maximum condensing pressure of the low-temperature refrigeration cycle 20, the volume of the first regenerator 301 relative to the total volume of the low-temperature refrigeration cycle 20 needs to be set as small as possible. However, if the volume of the first regenerator 301 is set too small as a ratio of the total volume of the low-temperature cycle filter, the temperature of the return air pipe at the return air port of the low-temperature compressor 202 will be too low, leading to the risk of frost formation 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 excessively high maximum condensing pressure in the low-temperature refrigeration cycle 20 and preventing the risk of frost formation and compressor shutdown due to excessively low temperature of the return air pipe of the low-temperature compressor 202.

[0155] 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. Thus, 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 can better maintain the condensing pressure within the low-temperature refrigeration cycle 20, prevent the maximum condensing pressure from being too high, and minimize the risk of frost on the return air pipe (fourth pipe) of the low-temperature compressor 202, as well as the risk of compressor shutdown.

[0156] 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, by setting the internal volume of the first regenerator 301 to within 5% to 40% of the total volume of the low-temperature refrigeration cycle 20, the first regenerator 301 can better transfer heat from the high-temperature refrigerant at the exhaust port of the low-temperature compressor 202 to the low-temperature refrigerant at its return port, thereby preventing frost on the return air pipe of the return air port of the low-temperature compressor 202 and preventing excessive condensation pressure in the low-temperature refrigeration cycle 20.

[0157] 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 between the air inlet of the low-temperature compressor 202 and the evaporator of the low-temperature evaporator 204 can be increased to avoid frost 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, avoiding waste. While maintaining a good effect of avoiding frost, it can also avoid the increase in the maximum condensation pressure in the low-temperature refrigeration cycle 20. Maintain a good quiet effect.

[0158] 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.

[0159] 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.

[0160] Among them, when the ratio of the internal volume V1 of the evaporator 101 to the total volume Vh of the high-temperature refrigeration cycle 10 is 45% and the ratio of the internal volume V2 of the condenser 201 to the total volume Vc of the low-temperature refrigeration cycle 20 is 15%, 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 5%, 10%, and 30% as comparative examples, the initial power-on pre-cooling time min, 32°C ambient temperature, maximum condensing pressure MPa, 32°C ambient temperature, low-temperature return air temperature °C at the same refrigerant filling amount, empty tank refrigeration depth °C, and noise db (A) were verified, and the results shown in Table 8 below were obtained:

[0161] Table 8

[0162]

[0163] 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%, the low-temperature return air temperature ℃ is moderate under the ambient temperature of 32℃ and the same refrigerant filling amount, and 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.

[0164] Optionally, the content of R290 or R1270 in the second refrigerant is greater than 50%.

[0165] In the related art, in the field of household appliances, R290 is generally used in combination with conventional refrigerants. For example, R290 is matched with 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 R290 content 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%. In combination with the above-mentioned parameter settings such as the volume ratio of the evaporative condenser and the various parameter settings of the first regenerator, it can reduce the pressure difference, reduce noise, and achieve low-noise operation of the refrigeration equipment.

[0166] Generally, the compressor startup sequence of a 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 throttled by the high-temperature throttling device will accumulate in the evaporating part of the evaporative condenser. The accumulation amount can even reach 70% to 80% of the total refrigerant in the high-temperature circulation loop. After the low-temperature compressor is started, a large amount of heat is transferred from the condensing part to the evaporating part, causing the high-temperature refrigerant stored in the evaporating part to evaporate rapidly and a large amount of gaseous high-temperature refrigerant to be generated, which makes it difficult to control the temperature and pressure of the evaporating part of the evaporative condenser.

[0167] Optionally, the high-temperature circulation loop further includes a high-temperature liquid reservoir, which can be used to store a portion of the high-temperature refrigerant and release the stored high-temperature refrigerant to the high-temperature circulation loop. This allows the high-temperature circulation loop to partially store the liquid refrigerant generated by the compressor during initial startup in the high-temperature circulation loop in the high-temperature liquid reservoir, reducing the amount of refrigerant accumulated in the evaporative condenser 30 and, in turn, reducing the peak pressure of the evaporation section 101 during the process of generating a large amount of gaseous refrigerant through evaporation, thereby achieving a buffering and stabilizing effect.

[0168] 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 medium 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 medium on the liquid inlet side of the high-temperature compressor 102. This arrangement can also reduce the risk of "liquid hammer".

[0169] Tables 9 and 10 show the experimental test results of two prototypes, A and B, at ambient temperatures of 25°C and 32°C, respectively. Prototype A is a model without a high-temperature liquid storage tank, while prototype B is a model equipped with a high-temperature liquid storage tank according to the previous embodiment.

[0170] Table 9

[0171]

[0172] Table 10

[0173]

[0174] Combining Tables 9 and 10, it can be seen that compared with Model A, Model B, which is equipped with a high-temperature liquid storage tank, not only increases the mass of the cold medium in the high-temperature circulation loop by approximately 50%, but also reduces its peak pressure by approximately 0.1 MPa at an ambient temperature of 25°C and by approximately 0.22 MPa at an ambient temperature of 32°C. This model withstands less peak pressure shock and has more stable system operation.

[0175] In some alternative 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 defined respectively, thereby testing the corresponding displacement of the high-temperature compressor 102 and the low-temperature compressor 202. As shown in Table 11 below:

[0176] Table 11

[0177]

[0178] In conjunction with Table 11, to ensure that the low-temperature storage temperature and system temperature are controllable, the high-temperature compressor 102 and the low-temperature compressor 202 meet the following displacement relationship:

[0179] 1.5:1≤CC 高温级 :CC 低温级 ≤1:1.5,

[0180] 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.

[0181] From Table 11, it can be seen that by setting the displacement CChighstage of the high-temperature stage compressor 140 and the displacement CClowstage of the low-temperature stage compressor 250 within the above-mentioned displacement range, not only can the low-temperature stage condensing temperature and the high-temperature stage evaporating temperature 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, thereby reducing the probability of safety problems of the entire machine caused by high heat load and excessively high exhaust temperature.

[0182] Furthermore, this application also tested the corresponding exhaust gas temperature and chamber temperature for different low-temperature compressor 202 displacements when the high-temperature compressor 102 displacement was fixed, as shown in Table 12-1; and the corresponding exhaust gas temperature and chamber temperature for different high-temperature compressor 102 displacements when the low-temperature compressor 202 displacement was fixed, as shown in Table 12-2. In both sets of test data, the displacement of the high-temperature compressor 102 and the low-temperature compressor 202 were each set to 9cc.

[0183] Table 12-1

[0184] 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 inside the box ℃ -62.6 -63.1 -64.1 -64.6 -65 -65.2

[0185] Table 12-2

[0186] High temperature stage 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 inside the box ℃ -65.3 -65.4 -65.3 -65.1 -64.7 -64.2 -63.5 -62.5

[0187] As can be seen from Table 12-1, when the displacement of high-temperature compressor 102 is set to 9cc, and the displacement of low-temperature compressor 202 is also 9cc (i.e., a ratio of 1:1), the exhaust temperature is relatively reasonable, and the compressor matching is relatively reasonable. Furthermore, as can be seen from Table 12-2, when the displacement of low-temperature compressor 202 is set to 9cc, and the displacement of high-temperature compressor 102 is also 9cc (i.e., a ratio of 1:1), the exhaust temperature is relatively reasonable, and the compressor matching is relatively reasonable.

[0188] Therefore, in the embodiment of the present application, the displacement ratio of the high-temperature stage compressor 102 displacement CC high-temperature stage and the low-temperature stage compressor 202 displacement CC low-temperature stage is preferably 1:1.

[0189] In some optional embodiments, such as Figures 6 to 13a As shown, the high-temperature stage throttling element 105, the evaporation portion 101, the first pipeline 103 and the condensation portion 201 are integrated into one.

[0190] In the disclosed embodiment, the high-temperature throttling element 105, evaporator 101, first pipeline 103, and condenser 201 of the cascade refrigeration system are integrated into a single unit. This means that the connection of these pipelines is removed from the assembly process of the refrigeration equipment. This allows the integrated pipelines to be directly assembled into the housing during assembly, reducing welding and other work during assembly, optimizing the assembly process, and improving production efficiency. Furthermore, the parallel arrangement of the pipelines reduces the overall footprint, making transportation easier and reducing potential transport issues.

[0191] In some optional embodiments, such as Figures 6 to 13a As shown, 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.

[0192] In the disclosed embodiment, the high-temperature throttling device 105, evaporator 101, first pipeline 103, condenser 201, third pipeline 203, and fourth pipeline 205 of the cascade refrigeration system are integrated into one body. This increases the number of integrated pipelines and components, further improving the integration of the pipelines. When assembling the refrigeration equipment, the integrated pipelines can be directly assembled into the cabinet, reducing welding and other work during the assembly process, optimizing the assembly process, and improving production efficiency. The parallel pipelines occupy a small overall volume, further improving transportation convenience and reducing adverse conditions that may occur during transportation.

[0193] In other optional embodiments, the high-temperature stage condenser and the high-temperature stage throttling device are connected through the second pipeline, and the low-temperature stage evaporator and the low-temperature stage compressor are connected through 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.

[0194] In the embodiment of the present disclosure, the second pipeline and the fourth pipeline of the cascade refrigeration system can also be integrated into one with other components. In actual applications, different pipelines can be integrated with the high-temperature throttling device, the evaporation part, the first pipeline and the condensation part according to different pipeline settings of the cascade refrigeration system.

[0195] Optionally, the high-temperature stage throttling element 105, the evaporation portion 101, the first pipeline 103 and the condensation portion 201 are welded together.

[0196] In the embodiment of the present disclosure, 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.

[0197] Optionally, the high-temperature throttling element 105, the evaporation portion 101, the first pipeline 103, the condensation portion 201, the third pipeline 203, and the fourth pipeline 205 are welded together. Alternatively, the high-temperature throttling element, the evaporation portion, the first pipeline, the condensation portion, the second pipeline, and the fourth pipeline are welded together.

[0198] In practical applications, the integrated pipes and components are welded through multiple welding points to strengthen the connection stability between the pipes.

[0199] 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.

[0200] The refrigeration equipment provided by the embodiments 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.

[0201] The following description uses a refrigerator as the refrigeration equipment, specifically a horizontal refrigerator:

[0202] 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 enclosing panels, and the plurality of enclosing panels enclose a storage cavity, which is constructed as a low-temperature storage space that can accommodate items. The plurality of enclosing 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 arranged in sequence 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.

[0203] Optionally, the press cabin 403 can be located at least one position in the left side of the casing, the right side of the casing and the rear side of the casing. In actual application, the position of the press cabin can be set according to the size of the casing and use requirements.

[0204] 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 liner 402 occupied by the compressor cabin 403 and increase the storage capacity of the inner liner 402.

[0205] For ease of description, Figure 6 As shown, when the press cabin is located on the left 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 .

[0206] Optionally, the fifth compressor and the sixth compressor are arranged side by side in the compressor cabin 403, or the length direction of the fifth compressor and the length direction of the sixth compressor are arranged to cross each other.

[0207] In the disclosed embodiment, the fifth and sixth compressors are both located within the same compressor compartment 403. Depending on the size of the compressor compartment 403, the two compressors can be arranged side by side or crosswise. This does not increase the height of the compressor compartment 403, nor does it require two compressor compartments 403, each housing a separate compressor. This reduces the storage space occupied by the compressor compartment 403 within the inner liner 402, thereby improving the storage space and storage experience of the refrigeration equipment.

[0208] Specifically, when the depth of the compression chamber 403 is sufficiently large, the two compressors can be arranged side by side along the depth direction of the compression chamber 403. When the depth of the compression chamber 403 is relatively small, the two compressors can be staggered. When the width of the compression chamber 403 in the left-right direction is sufficiently large, the two compressors can also be arranged side by side along the left-right direction of the compression chamber 403.

[0209] 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. 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 is understood that both arrangements of arranging two compressors in one compressor cabin are optional embodiments of the present application.

[0210] Optionally, the fifth compressor and the sixth compressor are located in the same horizontal plane, which facilitates the installation of the two compressors and 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.

[0211] 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, the compressors of two independent refrigeration systems can also be set up using the setting method of the fifth compressor and the sixth compressor of the present application.

[0212] like Figure 15 As shown, for the high-temperature stage 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 stage 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.

[0213] The following description is made by taking the fifth compressor as a high-temperature compressor and the sixth compressor as a low-temperature compressor as an example:

[0214] Optionally, when the width direction of the compressor cabin 403 is larger, the fifth compressor and the sixth compressor can be arranged side by side along the width direction of the compressor cabin 403.

[0215] Optionally, 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°.

[0216] 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°.

[0217] Optionally, when the length direction of the fifth compressor intersects the length direction of the sixth compressor, an angle α between the length direction of the fifth compressor and the length direction of the sixth compressor is in a range of 50°≤α≤130°. In the embodiment of the present disclosure, when the angle between the two is between 50° and 130°, the compressor structure in the compressor compartment is more compact.

[0218] For example, α can be 10°, 20°, 30°, 40°, 50°, 60°, 70°, 80°, 90°, 100°, 110°, 120°, 140°, 150°, 170°, etc.

[0219] In a specific embodiment, the length direction of at least one of the fifth compressor and the sixth compressor is inclined relative to the depth direction of the compressor chamber 403 to facilitate the arrangement of the two compressors.

[0220] In another specific embodiment, Figure 15 and Figure 16 As shown, the fifth compressor and the sixth compressor are arranged vertically.

[0221] In the disclosed embodiment, the two compressors are arranged vertically, which effectively utilizes 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.

[0222] Optionally, the length direction of one of the fifth compressor and the sixth compressor extends along the depth direction of the compressor cabin, and the length direction of the other of the fifth compressor and the sixth compressor extends along the width direction of the compressor cabin.

[0223] Optionally, the fifth compressor and the sixth compressor are arranged in sequence along the depth direction of the compressor cabin, which facilitates the coordination of the low-temperature stage pipeline and the high-temperature stage pipeline with the compressors.

[0224] It should be noted that the sixth compressor and the fifth compressor can also be arranged sequentially along the depth direction of the compressor compartment. In actual application, the arrangement directions of the fifth compressor and the sixth compressor can be set according to the arrangement of the refrigeration equipment pipelines.

[0225] In this embodiment, the outer shell 401 is wrapped around the outer side of the inner liner 402, and an interlayer space is formed between the outer shell 401 and the inner liner 402. 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 device 105, and the high-temperature evaporator 108. Alternatively, the heat exchange part of the low-temperature refrigeration cycle 20 includes but is not limited to the aforementioned condensing part 201, the low-temperature evaporator 204, and the low-temperature throttling device 206. The interlayer space can also be used to accommodate the aforementioned regenerators (including the first regenerator 301, the second regenerator 302, and / or the third regenerator 303), the return air pipe group 304, the pre-cooling pipe 308, etc.

[0226] Optionally, the evaporative condenser 30 is located between the inner container 402 and the outer shell 401, as shown in FIG. 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 FIG. Figures 9 to 13a As shown, the evaporative condenser 30 is located below the step.

[0227] In the embodiment of the present disclosure, 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. Moreover, the evaporative condenser 30 is arranged below the step, which makes rational use of the space of the refrigeration equipment, 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 production costs. 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.

[0228] 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 .

[0229] Optionally, when the evaporator condenser is arranged 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 .

[0230] Optionally, when the refrigeration device includes a first reheater 301, the evaporative condenser 30 and the first reheater 301 are both located between the inner liner 402 and the outer shell 401, and the evaporative condenser 30 and the first reheater 301 are located on the outside of at least one enclosed plate; or, when the refrigeration device includes a first reheater 301 and a return air pipe group 304, the evaporative condenser 30, the first reheater 301, and the return air pipe group 304 are all located between the inner liner 402 and the outer shell 401, and the evaporative condenser 30, the first reheater 301, and the return air pipe group 304 are located on the outside of at least one enclosed plate. Optionally, when the refrigeration device includes a first reheater 301, the evaporative condenser 30 and the first reheater 301 are located on the outside of the same enclosed plate; or, when the refrigeration device includes a first reheater 301 and a return air pipe group 304, the evaporative condenser 30, the first reheater 301, and the return air pipe group 304 are located on the outside of the same enclosed plate. In the disclosed embodiment, the evaporative condenser 30, the first regenerator 301 and the return air pipe group 304 can be respectively arranged on different enclosure panels or on the same enclosure panel, so that the pipelines can be rationally arranged and the storage capacity of the refrigeration equipment can be increased.

[0231] In some optional embodiments, the evaporative condenser 30, the first regenerator 301, and the return air pipe assembly 304 are located on the same side wall of the inner liner 402. This makes the multiple pipelines more compact and facilitates the connection of the pipelines to the corresponding compressors. For example, the evaporative condenser 30, the first regenerator 301, and the return air pipe assembly 304 can all be located on the front side wall of the inner liner 402, the rear side wall of the inner liner 402, the left side wall of the inner liner 402, or the right side wall of the inner liner 402.

[0232] 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.

[0233] In the embodiment of the present disclosure, the first 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 communication between the pipeline and the corresponding compressor.

[0234] Optionally, the first heat regenerator 301 and the return air pipe group 304 are arranged in sequence from the inside to the outside.

[0235] In the embodiment of the present disclosure, the first heat regenerator 301 and the return air pipe group 304 are stacked and spaced apart, which further reduces the space occupied by the first heat regenerator 301 and the return air pipe group 304.

[0236] For example, Figure 8 As shown, the first regenerator 301 matches the return air pipe assembly 304. That is, the first regenerator 301 and the return air pipe assembly 304 have the same or similar shapes and dimensions. This facilitates the placement of the first regenerator 301 and the return air pipe assembly 304. Optionally, the first regenerator 301 and the return air pipe assembly 304 are curved, which ensures the length of the first regenerator 301 and the return air pipe assembly 304.

[0237] Optionally, the refrigeration device further includes a connector connected between the first regenerator 301 and the return air pipe assembly 304. There are multiple connectors, which are spaced apart along the extension direction of the first regenerator 301 or the return air pipe assembly 304. One end of the connector is connected to the inner tank 402, thereby increasing the stability of the return air pipe assembly 304 and the first regenerator 301.

[0238] Alternatively, as Figures 6 to 8 As shown, when the evaporative condenser 30 , the first regenerator 301 and the return air pipe group 304 are arranged on the same side wall, the first regenerator 301 and the return air pipe group 304 are located on the side of the evaporative condenser 30 close to the compressor cabin 403 .

[0239] 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 liner 402. In this way, more pipelines are integrated on the same side wall of the inner liner 402. This can provide sufficient space to set up 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 connection with the corresponding compressor.

[0240] Preferably, if Figure 6 As shown, the evaporative condenser 30 , the first regenerator 301 and the return air pipe group 304 are all arranged on the rear side wall of the inner tank 402 .

[0241] 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 outside the evaporative condenser 30 .

[0242] In the disclosed embodiment, the low-temperature throttling element 206 is also provided on the side wall of the inner tank 402 , which facilitates the connection of the low-temperature throttling element 206 with other pipelines and can provide sufficient space to ensure the length of the low-temperature throttling element 206 .

[0243] Preferably, if Figure 6As 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 .

[0244] It can be understood that the first regenerator 301, the return air pipe group 304, the evaporative condenser 30 and the low-temperature stage throttling device 206 can also be set 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.

[0245] Alternatively, as Figure 6 and Figure 17 As shown, the compressor cabin 403 includes a partition 70 and a compressor base plate 60. The compressor base plate 60 is located at the bottom of the compressor cabin 403, and the partition 70 is at least partially located at the upper portion of the compressor cabin 403. The partition 70 is spaced below the step. Optionally, the compressor base plate 60 is a 1.5 mm thick galvanized sheet.

[0246] In the disclosed embodiment, the partition 70 is located above the compressor cabin 403. The partition 70 can support the compressor and protect it. The compressor base plate 60 is located below the compressor to support the compressor and provide shock absorption for the compressor.

[0247] Optionally, when the evaporative condenser 30 is located below the step or on the upper part of the compressor cabin 403 , it can be understood that the evaporative condenser 30 is located between the partition 70 and the step.

[0248] 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.

[0249] In the disclosed embodiments, 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 a partition and the inner container, such as between a partition and a 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.

[0250] Optionally, the return air pipe group 304 or the first regenerator can also be located between the inner container and the outer shell or between the partition and the inner container. The specific location is the same as that described for the evaporator and condenser, and will not be repeated here.

[0251] In 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 outside of the side wall of the inner liner 402 .

[0252] In the disclosed embodiment, the return air duct assembly 304 can be positioned below the step or outside the sidewall of the inner liner 402. The return air duct assembly 304 is curved to provide sufficient space to ensure the length of the return air duct assembly 304 and heat exchange efficiency. Optionally, when the return air duct assembly 304 is positioned below the step, the return air duct assembly 304 is positioned between the partition 70 and the step.

[0253] Optionally, the first heat regenerator 301 is disposed below the step or on the outside of the side wall of the inner tank 402 .

[0254] In the disclosed embodiment, the first regenerator 301 can also be located below the step or outside the sidewall of the inner tank 402, with the return air pipe assembly 304 curved. This provides sufficient space to ensure the length of the first regenerator 301 and heat exchange efficiency. Optionally, when the first regenerator 301 is located below the step, it is located between the partition 70 and the step.

[0255] In a specific embodiment, Figure 9 and Figure 10 As shown, the evaporative condenser 30 and the return air pipe assembly 304 are both located below the step. Specifically, the evaporative condenser 30 and the return air pipe assembly 304 are both located between the step and the partition 70. This ensures that the evaporative condenser 30 and the return air pipe assembly 304 have sufficient contact length, allowing the evaporation section 101 to fully dissipate heat to the condensation section 201, while also achieving noise reduction and energy conservation. Optionally, the first regenerator 301 is located outside the side wall of the inner tank 402, thereby ensuring the heat exchange length of the first regenerator.

[0256] 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 regenerator 301 are both located on the rear side wall of the inner tank 402, so that the pipelines are arranged in parallel, further reducing the space occupied by the pipelines.

[0257] Optionally, the evaporative condenser 30 and the return air pipe group 304 are spaced apart below the step in the vertical direction. 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.

[0258] For example, Figure 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 all filled with a foam layer to achieve thermal insulation and heat preservation.

[0259] In another specific embodiment, Figure 11 and Figure 12As 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.

[0260] In the embodiment of the present disclosure, 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 transportation costs.

[0261] Optionally, the evaporative condenser 30 is located between the return air pipe assembly 304 and the first regenerator 301. Specifically, from top to bottom, the first regenerator 301, the evaporative condenser 30, and the return air pipe assembly 304 are sequentially spaced apart. The first regenerator 301 is spaced apart from the bottom of the step, and the return air pipe assembly 304 is spaced apart from the partition 70. A foam layer is filled between the bottom of the step, the first regenerator 301, the evaporative condenser 30, the return air pipe assembly 304, and the partition 70 to achieve thermal insulation.

[0262] 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. 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. Those skilled in the art should be fully capable of expanding upon this, and this application will not elaborate further.

[0263] In another specific embodiment, Figure 13 and Figure 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 , which 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 .

[0264] In the embodiment of the present disclosure, 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 .

[0265] Optionally, the fourth pipeline 205 is in contact with the return air pipe group 304 to achieve heat exchange. Specifically, the fourth pipeline 205 is in contact with the upper part of the return air pipe group 304.

[0266] Optionally, the condenser section 201 includes a first condenser section and a second condenser section, and the evaporator section 101 is located between the first condenser section and the second condenser section, and the evaporator section 101 is in contact with both the first condenser section and the second condenser section. In the embodiment of the present disclosure, there are multiple condenser sections 201, and the evaporator section 101 is located between two condenser sections 201. This can increase the contact length between the condenser section 201 and the evaporator section 101, thereby improving the heat exchange effect of the evaporative condenser 30.

[0267] 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.

[0268] In the embodiment of the present disclosure, the third regenerator 303 and the evaporative condenser 30 are arranged at intervals in the vertical direction. In this way, the cascade refrigeration system does not need to be equipped with the first regenerator 301. The first regenerator 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.

[0269] 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 foam layer to achieve thermal insulation and heat preservation.

[0270] In some alternative embodiments, combined with Figures 14 to 14c As shown, the at least two heat exchange units in the aforementioned embodiment are arranged side by side from the inside out in the interlayer space formed by the inner liner 402 and the outer shell 401. Here, 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, the operating temperature of the heat exchange unit located in the inner liner layer is lower than that of the heat exchange unit located on the outer shell side, thereby forming a temperature gradient with increasing temperature from the inside out.

[0271] The operating temperatures of the heat exchange parts of the cascade refrigeration system using the above arrangement are different. For example, the operating temperature of the evaporation part 101 of the evaporative condenser 30 during steady-state operation is approximately -35°C; the operating temperature of the condensation part 201 of the evaporative condenser 30 during steady-state operation is approximately -18 to -30°C; the refrigerant temperature at the cold end of the first regenerator 301 gradually rises from -60°C to 30°C during steady-state operation, and the refrigerant temperature at the hot end gradually drops 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.

[0272] Therefore, under the above 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 farther apart, which can reduce the heat conduction speed between each other and slow 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 inside 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.

[0273] In some embodiments, the heat exchange portion using the above arrangement includes two or more of the following types:

[0274] The first heat exchange unit is configured to exchange heat with the low-temperature storage space on the inner liner side. For example, the first heat exchange unit can be the low-temperature evaporator 204 or the fourth pipeline 205. The refrigerant flowing through the low-temperature evaporator 204 and the fourth pipeline 205 is relatively low in temperature and is arranged close to the inner liner, and can be used to cool the inner liner 402.

[0275] The second heat exchange part is configured to exchange heat with the external environment on the side of the shell 401. For example, the second heat exchange part is a pre-cooling pipe 308 or a high-temperature condenser 104.

[0276] The third heat exchange section is configured to provide intermediate heat exchange between two heat exchange tube groups with different operating temperatures. For example, the third heat exchange section is an evaporative condenser 30, with its two heat exchange tube groups being the evaporator 101 and the condenser 201. Alternatively, the third heat exchange section is a regenerator, which can be the first regenerator 301, the second regenerator 302, or the third regenerator 303 in the above embodiments. Taking the first regenerator 301 as an example, its two heat exchange tube groups are the first regenerator tube group 3011 and the second regenerator tube group 3012.

[0277] Here, the two heat exchange tube groups in 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.

[0278] Optionally, the interlayer space formed by the inner liner 402 and the outer shell 401 is sequentially arranged with a first heat exchange portion and a second heat exchange portion 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 a first heat exchange portion and a third heat exchange portion 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 a second heat exchange portion and a third heat exchange portion 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 a first heat exchange portion, a second heat exchange portion, and a third heat exchange portion from the inside to the outside, and so on. This application does not impose any restrictions on this.

[0279] In some optional embodiments, at least two heat exchange parts are arranged in the first arrangement. Figure 14b and 14c As shown, the first arrangement is constructed by sequentially arranging the low-temperature stage evaporator 204, the evaporation portion 101 of the evaporation condenser 30, the condensation portion 201 of the evaporation condenser 30 and the pre-cooling pipe 308 from the inner tank side to the outer shell side.

[0280] In this embodiment, the operating temperatures of each heat exchange unit are, in order: inner liner 402 - low-temperature evaporator 204 (-65°C) - evaporation section 101 of evaporative condenser 30 (-48--35°C) - condensation section 201 of evaporative condenser 30 (-45~30°C) - pre-cooling pipe 308 (34~45°C). It can be seen that the operating temperatures of the heat exchange units increase from the inner liner side to the outer shell side. The heat exchange unit with a lower temperature is located on the inner liner side, and the heat exchange unit with a higher temperature is located on the outer shell side. This can not only reduce the conduction of cold energy from the former to the outer shell 401 side, so that the cold energy is more concentratedly supplied to the inner liner 402, but also make it easier for the latter to dissipate heat to the external environment where the outer shell 401 is located, reducing the transfer of heat to the inner liner 402 side. At the same time, the temperature ranges between adjacent heat exchange units are closer, and the temperature difference is smaller, which can slow down the conduction of cold energy to the outer shell 401 side or heat to the inner liner 402 side.

[0281] Optional, such as Figure 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:

[0282] δ / 6≤H≤δ / 2,

[0283] Wherein, H is the distance between the low-temperature evaporator 204 and the evaporative condenser 30, and δ is the thickness of the interlayer space.

[0284] In this optional embodiment, the spacing between the low-temperature evaporator 204 and the evaporative condenser 30 is determined based on the temperature of the foam layer at different thickness locations. Here, the closer the foam layer is to the inner liner 402, the lower its temperature; conversely, the farther the foam layer is from the inner liner 402, the higher its temperature. In this embodiment, the evaporative condenser 30 is positioned at a thickness of the foam layer that is close to its own temperature, effectively reducing heat loss.

[0285] 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. Through experimental calculations and other methods, it can be known 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.

[0286] It should be noted that in this embodiment, the low-temperature evaporator 204 and the inner liner 402 are placed in close contact with each other through the aluminum foil, with no gap between them. Furthermore, it is assumed that the thickness of the heat exchange tubes of the low-temperature evaporator 204 is negligible. Therefore, the location 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.

[0287] In an optional embodiment, at least two heat exchange units are arranged in a second arrangement. Specifically, the second arrangement is configured to sequentially arrange the low-temperature evaporator 204, the first heat recovery pipe group 3011, the second heat recovery pipe group 3012, and the pre-cooling pipe 308 from the inner tank side to the outer shell side.

[0288] In this embodiment, the operating temperatures of the various heat exchange components are as follows: inner liner 402 - low-temperature evaporator 204 (-65°C) - first reheat pipe group 3011 (-60 to 30°C) - second reheat pipe group 3012 (-30 to 34°C) - precooling pipe 308 (34 to 45°C). As can be seen, the operating temperatures of the low-temperature evaporator 204, reheat pipe, and precooling pipe 308 increase from the inner liner 402 side to the outer shell 401 side. This also serves to slow the transfer of cooling energy to the outer shell or heat to the inner liner side. Different from the previous embodiment, the previous embodiment focuses on the arrangement of the evaporative condenser 30 in conjunction with the low-temperature evaporator 204 and the pre-cooling tube 308 to reduce the adverse effects of the heat exchange tube group of the evaporative condenser 30 on the inner tank 402, while this embodiment focuses on the arrangement of the regenerator in conjunction 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.

[0289] In some alternative embodiments, the heat exchange unit disposed in the interlayer space between the inner liner 402 and the outer shell 401 further includes a fourth heat exchange unit, which includes a return air pipe assembly 304 connected to the compressor return air. Optionally, the compressor is the high-temperature compressor or the low-temperature compressor described above.

[0290] Here, take the return air pipe group of the low temperature compressor as an example. Figure 14a As shown, the refrigerant flowing through the return air pipe group 304 originates from the second reheat pipe group 3012 of the first reheater 301, and its refrigerant temperature is approximately -25°C to 30°C. For the return air pipe group within this temperature range, this embodiment utilizes the third arrangement. Specifically, the third arrangement comprises, from the inner liner side to the outer shell side, the low-temperature evaporator 204, the first reheat pipe group 3011, the second reheat pipe group 3012, the return air pipe group 304, and the pre-cooling pipe 308, arranged in this order.

[0291] Thus, the operating temperatures of the heat exchange components in this embodiment are as follows: inner liner 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) - pre-cooling pipe 308 (34-45°C). As can be seen, the temperature of the return air pipe group 304 is relatively close to that of the adjacent second heat return pipe group 3012 and pre-cooling pipe 308 on both sides, thereby reducing the heat transfer of the return air refrigerant to the inner liner 402.

[0292] In the foregoing embodiments, at least part of the heat exchange tubes of the low-temperature 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 liner 402 to ensure that the low-temperature evaporator 204 and the enclosure plate have sufficient thermal contact area, thereby ensuring the cooling effect on the inner liner 402.

[0293] Similarly, in order to avoid local overheating and other problems 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 pipe layout planes, and the pipe layout planes of adjacent heat exchange parts are arranged parallel to each other.

[0294] For example, Figure 14b and 14c As shown, taking the first arrangement as an example, the plane where the low-temperature evaporator 204 is located is defined as the first pipe layout plane, the plane where the evaporator section 101 of the evaporative condenser 30 is located is defined as the second pipe layout plane, the plane where the condenser section 201 of the evaporative condenser 30 is located is defined as the third pipe layout plane, and the plane where the pre-cooling tube 308 is located is defined as the fourth pipe layout plane. In this embodiment, the first, second, third, and fourth pipe layout planes are arranged parallel to each other. By adopting this arrangement, the heat exchange tubes of each heat exchange section can be relatively evenly distributed within the foam layer, and the spacing between each heat exchange tube of a heat exchange section and adjacent heat exchange sections is substantially equal.

[0295] In some other embodiments, for horizontal freezer models, the heat load at the open top and the bottom of the freezer is relatively large. Therefore, in order to ensure the cooling effect of the horizontal freezer, the heat exchange tube arrangement density corresponding to these two positions of the low-temperature evaporator 204 is greater than the heat exchange tube arrangement density at other positions, so as to increase the cooling capacity at the top and bottom positions by increasing the number of refrigeration tubes.

[0296] Similarly, the compressor arranged in the compressor compartment 403 will also emit a large amount 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.

[0297] In addition, in the cascade refrigeration system, both the evaporative condenser 30 and the regenerator (first regenerator 301) cool the refrigerant (refrigerant) in the low-temperature refrigeration cycle 20. The evaporative condenser 30 absorbs the latent heat of the refrigerant, while the regenerator absorbs the sensible heat of the refrigerant. Therefore, to improve the heat recovery efficiency of the system, in some embodiments, the evaporative condenser 30 and the regenerator satisfy the following relationship:

[0298] 7 / 2.2≤L1 / L2≤7 / 2.1,

[0299] 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.

[0300] After testing, it was found that when the effective heat exchange pipe lengths of the evaporator condenser 30 and the regenerator meet the above-mentioned numerical range, the sensible heat energy recovery of the refrigerant output by the low-temperature evaporator 204 can be effectively increased, and the occurrence of frost and condensation inside the compressor cabin caused by the excessively low return air temperature of the low-temperature compressor 202 can be reduced.

[0301] For example, in a certain model, the refrigerant circulation rate of the evaporative condenser 30 is approximately 0.202 g / s, the heat load is approximately 78.12 W, and the heat transfer coefficient is 3.7 W / m / °C. The calculated effective pipe length of the evaporative condenser 30 is approximately 7.06 m. Furthermore, 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, meaning that the effective pipe length of the regenerator is set to 2.13 m. When meeting this regenerator pipe length requirement, the temperature rise ΔT1 of the cold fluid in the test regenerator can reach approximately 40°C, and the temperature drop ΔT2 of the hot fluid is approximately 3°C. This shows that the above parameter settings can achieve excellent heat recovery results.

[0302] Optionally, the high temperature stage compressor 102 is located in front of the low temperature stage compressor 202 .

[0303] In the disclosed embodiment, the low-temperature compressor 202 is located at the rear, facilitating connection between the low-temperature compressor 202 and the pipeline located 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 a step or on the back panel, the low-temperature compressor 202 is located at the rear, facilitating connection between the evaporative condenser 30 and the low-temperature compressor 202. In addition, when the first regenerator 301 is located under the back panel or under the step, this also facilitates connection between the first regenerator 301 and the low-temperature compressor 202.

[0304] 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. This can rationally utilize the space in the compressor cabin 403, reduce the size of the compressor cabin 403, and ensure the storage capacity of the refrigeration equipment.

[0305] 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 .

[0306] In the embodiment of the present disclosure, the length direction of the low-temperature compressor 202 is arranged along the width direction of the compressor, which facilitates welding of the low-temperature compressor 202 and the inlet and outlet pipelines (that is, the third pipeline 203 and the fourth pipeline 205).

[0307] Optionally, the inlet and outlet of the low-temperature stage compressor are oriented toward the rear side, which can further improve the welding between the low-temperature stage compressor 202 and its inlet and outlet pipelines.

[0308] Alternatively, as Figure 1 As shown, the housing 401 is provided with welding holes, and the low-temperature stage compressor 202 and / or the high-temperature stage compressor 102 are provided corresponding to the welding holes. In the embodiment of the present disclosure, to facilitate the connection of pipelines, the housing 401 is provided with welding holes, providing sufficient space for pipeline welding, thereby facilitating the connection of the pipelines and the compressors through the welding holes.

[0309] Alternatively, as Figure 1 As shown, the rear side wall of the housing 401 is provided with a first welding hole 4011, which corresponds to the low-temperature compressor 202. The left side wall of the housing 401 is provided with an air vent 4012, which is provided with a grille for ventilation within the compressor compartment 403. The inlet and outlet of the high-temperature compressor 102 correspond to the air vent 4012, so that the inlet and outlet pipes of the high-temperature compressor 102 (that is, the first pipe 103 and the second pipe 106) can be welded to the high-temperature compressor 102 at the air vent 4012. This improves 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.

[0310] Optionally, a first communication hole and a second communication hole are formed in the top wall of the partition 70. The first communication hole corresponds to the inlet and outlet of the low-temperature compressor 202, and the first communication 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 communication hole corresponds to the inlet and outlet of the high-temperature compressor 102, and the second communication 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.

[0311] Alternatively, as Figure 8As 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. The low-temperature evaporation tube is wound around the outside of the inner liner 402 and is arranged against the side wall of the inner liner 402, so as to cool 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. The high-temperature condensation tube is wound around the outside of the inner liner 402, wherein the high-temperature condensation tube is located outside 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, thereby ensuring the cooling effect of the cascade refrigeration system.

[0312] Alternatively, as Figure 17 and Figure 18 As shown, the compressor compartment 403 further includes a reinforcement iron 50, which is connected between the partition plate 70 and the compressor bottom plate. Specifically, the reinforcement iron 50 includes a frame 501 and a vertical beam 502, which is located at at least one end of the compressor compartment 403. The vertical beam 502 is located within the frame 501 and extends vertically, connecting between the upper and lower ends of the frame 501.

[0313] In the disclosed embodiment, vertical beams 502 are located within frame 501 and supported between the upper and lower ends of frame 501. This further increases the structural strength of frame 501, thereby enhancing the structural strength of frame 501. By adding vertical beams 502 to frame 501, the strength of reinforcing iron 50 is increased, thereby increasing the load-bearing capacity of compressor cabin 403 for the compressor, improving the reliability of refrigeration equipment transportation, and preventing damage.

[0314] Optionally, the frame 501 is rectangular, which can play the role of reinforcing the foam layer and the press cabin 403. It is understood that the frame can also be other shapes, such as polygonal.

[0315] 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.

[0316] 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.

[0317] 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 operations such as installation, disassembly, and pipe connection of the compressor in the compressor cabin 403.

[0318] Optionally, when the outer shell 401 is provided with welding holes, the welding holes correspond to the gap between the vertical beam 502 and the right beam, so as to facilitate welding, maintenance and replacement of the compressor in the compressor cabin 403.

[0319] 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.

[0320] In the embodiment of the present disclosure, 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.

[0321] Optionally, the first crossbeam 503 is located at the bottom of the reinforcing iron 50 , that is, the first crossbeam 503 is connected between the bottoms of the first frame 5011 and the second frame 5012 .

[0322] 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 .

[0323] In the disclosed embodiment, the partition 70 is connected to the top of the reinforcement iron 50. The partition 70 is located above the compressor, and the reinforcement iron 50 supports and reinforces the partition 70. The partition 70 is L-shaped, which can improve the support strength of the partition 70 on the compressor compartment 403, thereby improving the reliability of the refrigeration equipment transportation.

[0324] 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 crossbeam 503 by welding to ensure the strength of the structure.

[0325] Optionally, the first crossbeam 503 is located on the side of the compressor cabin 403 away from the air outlet 4012, so that the partition 70 can also separate the compressor and the inner liner 402 to protect the inner liner 402 and the compressor.

[0326] Optionally, a compressor base plate 60 is provided at the bottom of the reinforcing iron 50 and connected to the lower end of the frame 501. In the disclosed embodiment, the compressor base plate 60 is used to bear the weight of the compressor, and the lower end of the frame 501 is connected to the compressor base plate 60, which can further improve the load-bearing capacity of the compressor base plate for the compressor.

[0327] Optionally, the compressor base plate 60 is detachably connected to the frame 501. This facilitates replacement and maintenance of the compressor base plate 60. For example, the compressor base plate 60 and the lower end of the frame 501 can be detachably connected using screws.

[0328] Optionally, the compressor baseplate 60 includes multiple baseplates, and the multiple baseplates are sequentially spaced apart in the direction from the first frame 5011 to the second frame 5012. This makes the compressor baseplate 60 not a single unit. When multiple compressors are installed, the compressors can be placed on different baseplates, thereby reducing the occurrence of resonance and lowering noise.

[0329] In some optional embodiments, such as Figure 19 As shown, the compressor baseplate 60 includes a first baseplate 601 and a second baseplate 602. The first baseplate 601 is located below one of the high-temperature stage compressor 102 and the low-temperature stage compressor 202; the second baseplate 602 is located below the other of the high-temperature stage compressor 102 and the low-temperature stage compressor 202. The first baseplate 601 and the second baseplate 602 are spaced apart and located at the bottom of the same compressor cabin 403. For ease of description, the one of the high-temperature stage compressor 102 and the low-temperature stage compressor 202 above the first baseplate 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 baseplate 602 is defined as the second compressor.

[0330] In the embodiment of the present disclosure, the high-temperature stage compressor 102 and the low-temperature stage compressor 202 are respectively arranged above the first base plate 601 and the second base plate 602, that is, the base 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.

[0331] 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 .

[0332] In the disclosed embodiment, the provision of first reinforcing ribs 6011 and second reinforcing ribs 6021 increases the strength of first and second bottom plates 601, 602, respectively. This also increases the bending strength in the convex direction, improving deformation resistance and thereby better securing the two compressors. Furthermore, this alters the natural frequencies of the two bottom plates, preventing resonance between the compressors and their corresponding bottom plates, thereby reducing noise.

[0333] Optionally, the first reinforcing rib 6011 and the second reinforcing rib 6021 are both rib-like structures protruding from the surface of the first base plate 601 or the second base plate 602 toward the corresponding compressor. They can be formed by a partial protrusion of the first base plate 601 or the second base plate 602 toward the corresponding compressor, or by the upper surface of the first base plate 601 or the second base plate 602 protruding toward the compressor.

[0334] Optionally, there are multiple first reinforcing ribs 6011, and multiple first reinforcing ribs 6011 enclose a first installation area 6012, which 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, which is used to install the second compressor.

[0335] In the embodiment of the present disclosure, 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 increase the natural frequency of the first base plate 601, reduce the resonance between 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.

[0336] Optionally, the multiple first reinforcing ribs 6011 include a first convex rib and a second convex rib, the first convex rib is annular and is 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 cabin 403.

[0337] In the embodiment of the present disclosure, multiple 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 base plate 601.

[0338] Optionally, the multiple second reinforcement ribs 6021 include a third rib, a fourth rib and a fifth rib, the third rib extends along the depth direction of the press cabin 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 base plate 601, and is suitable for extending along the width direction of the press cabin 403.

[0339] In the embodiment of the present disclosure, a plurality of second reinforcing ribs 6021 are arranged around the second installation area 6022 , which can increase the strength of the second base plate 602 in multiple directions.

[0340] 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 arranged vertically, that is, the high-temperature stage compressor 102 and the low-temperature stage compressor 202 are arranged vertically, which can effectively utilize the space of the compressor cabin 403 and reasonably arrange the two compressors without increasing the size of the compressor cabin 403. Figure 15 As shown, the length direction of the first mounting area 6012 refers to the length along the X-axis, and the length direction of the second mounting area 6022 refers to the length along the Y-axis.

[0341] Optionally, the length direction of the first installation area 6012 extends along the depth direction of the press cabin 403, and the length of the second installation area 6022 extends along the width direction of the press cabin 403, wherein the projection area of the first base plate 601 on the horizontal plane is greater than or equal to the projection area of the second base plate 602 on the horizontal plane.

[0342] In the embodiment of the present disclosure, the first installation area 6012 extends along the depth direction of the compressor cabin 403, and the length of the second installation area 6022 extends along the width direction of the compressor cabin 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.

[0343] Optionally, the first mounting area 6012 is provided with a first mounting hole, which is cross-shaped. The bottom of the compressor above the first base plate 601 is a spherical structure, extending from the bottom to the surrounding areas and gradually increasing in distance from the first base plate 601. The bottom of the compressor above the first base plate 601 is located above the first mounting hole, and a first reinforcing rib 6011 is provided around the first mounting area 6012. In this way, when the compressor above the first base plate 601 vibrates during operation, the bottom of the compressor above the first base plate 601 can be prevented from directly contacting the first base plate 601, reducing the vibration transmitted from the compressor above the first base plate 601 to the first base plate 601, thereby achieving the effect of reducing noise. Similarly, the second mounting area 6022 is provided with a second mounting hole, which is cross-shaped and has the same effect as the first mounting hole, and will not be repeated here.

[0344] Optionally, a ratio a of a projected area of the first bottom plate 601 on a horizontal plane to a projected area of the second bottom plate 602 on a horizontal plane is in a range of 1≤a≤3.

[0345] In the disclosed embodiment, if the horizontal projection area of the first base plate 601 is smaller than the horizontal projection area of the second base plate 602, the compressor in the first installation area 6012 cannot be adequately damped. If the horizontal projection area of the first base plate 601 is too large, the area of the second base plate 602 is too small, and the compressor in the second installation area 6022 cannot be adequately damped. For example, a can be 1, 1.5, 2, 2.5, 3, etc.

[0346] 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 provide a reinforcement effect, and the first bottom plate 601 is easily deformed. The area of the first reinforcing rib 6011 is too large to provide sufficient space for installing the compressor. For example, b can be 20%, 21%, 22%, 23%, 24%, 25%, etc. Preferably, b is 22%.

[0347] 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 provide a reinforcement effect, and the second bottom plate 602 is easily deformed. The area of the second reinforcing rib 6021 is too large to provide sufficient space for installing the compressor. For example, c can be 10%, 11%, 12%, 13%, 14%, 15%, 16%, etc. Preferably, c is 24%.

[0348] 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.

[0349] 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.

[0350] 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 base plate, and can well improve the natural frequency of the first base plate 601 and the second base plate 602.

[0351] 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.

[0352] 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.

[0353] Optionally, a first pressing edge is provided on the outer edge of the first bottom plate 601, and the first pressing edge abuts against the upper surface of the first bottom plate 601. This can strengthen the strength of the first bottom plate 601 and change the natural frequency of the first bottom plate 601. At the same time, the first pressing edge can fill the gap between the first bottom plate 601 and the reinforcing iron 50, thereby facilitating the fixation of the first bottom plate 601.

[0354] 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.

[0355] Optionally, a second pressure edge is provided on the outer edge of the second bottom plate 602, and the second pressure edge abuts against the upper surface of the second bottom plate 602. This can strengthen the second bottom plate 602 and change the natural frequency of the second bottom plate 602. At the same time, the second pressure edge can fill the gap between the second bottom plate 602 and the reinforcing iron 50, thereby facilitating the fixing of the second bottom plate 602.

[0356] 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.

[0357] Optionally, when there are multiple bottom plates, and the multiple bottom plates extend from the first frame 5011 to the second frame 5012, the reinforcing iron 50 further includes a second crossbeam 504, which is connected between the first frame 5011 and the second frame 5012 and is disposed opposite the first crossbeam 503; wherein the second crossbeam 504 is connected to each of the multiple bottom plates. In the disclosed embodiment, when there are multiple bottom plates, the second crossbeam 504 connects the multiple bottom plates, further improving the bottom plates' load-bearing capacity for the compressor.

[0358] Optionally, the refrigeration device further includes a first universal wheel and a second universal wheel. 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 further configured with a first mounting hole for mounting the first universal wheel. The second base plate 602 is configured with a second mounting hole for mounting the second universal wheel. The first and second universal wheels enable movement of the refrigeration device.

[0359] Optionally, a portion of the first base plate 601 protrudes upward to form a first mounting protrusion, the first mounting protrusion being provided with a first mounting hole and at least two slots. The refrigeration device further includes a first connecting plate connected above the first universal wheel and inserted into the slots to secure the first universal wheel to the first base plate 601.

[0360] Optionally, a portion of the second base plate 602 protrudes upward to form a second mounting protrusion, which is provided with a second mounting hole and at least two slots. The refrigeration equipment further includes a second connecting plate connected above the second universal wheel and inserted into the slots to secure the second universal wheel to the second base plate 602. Optionally, the centers of the first universal wheel and the second universal wheel are aligned along a straight line along the depth direction of the compressor chamber 403.

[0361] Optionally, a first notch is formed between the ends of the first and second ribs facing away from the second base plate 602, and the first mounting protrusion is located in the first notch. Optionally, a second notch is formed between the fifth and fourth ribs, and the second mounting protrusion is located in the second notch. Here, the first and second notches facilitate the installation of the universal wheel. Furthermore, the first and second mounting protrusions also increase the strength of the first and second base plates 601, 602.

[0362] In other optional embodiments, such as Figure 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 .

[0363] A portion of the compressor baseplate 60 protrudes upward to form reinforcing ribs 80. Ribs 80 include a first rib segment 801 and a second rib segment 802. Second rib segment 802 is connected to first rib segment 801 at a folded angle. First and second rib segments 801, 802, together define a first placement position 809 for a third compressor. For ease of description, a high-temperature compressor 102 or a low-temperature compressor placed in first placement position 809 is defined as the third compressor, and a high-temperature compressor 102 or a low-temperature compressor placed in second placement position 810 is defined as the fourth compressor.

[0364] In the disclosed embodiment, first rib segment 801 and second rib segment 802 are located in two directions of compressor baseplate 60, collectively defining a first placement position 809. The third compressor is placed in first placement position 809, thereby defining the position of the third compressor. First rib segment 801 and second rib segment 802 can increase the stiffness of compressor baseplate 60 in different directions, reduce deformation of compressor baseplate 60, increase the natural frequency of compressor baseplate 60, reduce resonance between compressor baseplate 60 and the third compressor, and thus reduce noise generated by the third compressor during operation.

[0365] 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, thereby fixing the third compressor to the compressor base plate 60. The connecting component is set 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.

[0366] Optionally, the first rib segment 801 is provided along the length direction of the compressor base plate 60 , and the second rib segment 802 is provided along the width direction of the compressor base plate 60 .

[0367] 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, which can preliminarily define the position of the first placement position 809. Furthermore, the first rib segment 801 can increase the rigidity of the compressor baseplate 60 along the length direction, and the second rib segment 802 can increase the rigidity of the compressor baseplate 60 along the width direction, thereby increasing the overall rigidity of the compressor baseplate 60, reducing resonance between the compressor baseplate 60 and the third compressor, and achieving a noise reduction effect.

[0368] 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.

[0369] By providing 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 of the compressor baseplate 60, thereby enhancing the bending strength of the compressor baseplate 60 along the length at the first placement position 809 and improving its deformation resistance. This increases the rigidity of the compressor baseplate 60 at this location, confining the third compressor to the first placement position 809, and reducing the resonant frequency of the compressor baseplate 60 at this location with the third compressor, thereby reducing the resonance between the third compressor and the compressor baseplate 60 and achieving a noise reduction effect.

[0370] Optionally, the 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, and 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, and the third mounting protrusion is provided at the third notch. The first mounting protrusion is used to install the third universal wheel.

[0371] 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, 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.

[0372] 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.

[0373] In this way, the second rib segment 802, the fourth rib segment 804 and the fifth rib segment 805 jointly define the 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.

[0374] 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 base plate 60 along the length direction can be further enhanced, the anti-deformation capability of the compressor base plate 60 is improved, and the rigidity of the compressor base plate 60 is increased.

[0375] Optionally, the reinforcing rib 80 also includes a sixth rib segment 806, which is connected to the side of the fourth rib segment 804 facing away from the second rib segment 802 and forms a fold 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.

[0376] 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 deformation resistance, thereby enhancing the rigidity of the compressor base plate 60 at this location, limiting the fourth compressor to 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.

[0377] Optionally, a fourth notch is provided in the second placement position 810, and a fourth mounting protrusion is provided in the fourth notch for securing a fourth universal wheel. The fourth universal wheel is mounted in the same manner as the third universal wheel and is not described in detail here. The fourth universal wheel is disposed opposite the third universal wheel and, together with the third universal wheel, drives the compressor base plate 60 to move, thereby facilitating the movement of the refrigeration equipment.

[0378] 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).

[0379] In this way, the longer end of the third compressor can be arranged along the length direction of the compressor base plate 60, and the longer end of the fourth compressor can be arranged along the width direction of the compressor base plate 60. Alternatively, the longer end of the third compressor can be arranged along the width direction of the compressor base plate 60, and the longer end of the fourth compressor can be arranged along the length direction of the compressor base plate 60, so that the layout of the third and fourth compressors on the compressor base 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 base plate 60, and the other extends along the width direction of the compressor base plate 60. This increases the bending strength of the compressor base plate 60 in the length and width directions, improves the deformation resistance of the compressor base plate 60 in the length and width directions, increases the rigidity of the compressor base plate 60 in the length and width directions, reduces the resonance between the third and fourth compressors and the compressor base plate 60, and achieves the effect of reducing noise.

[0380] 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.

[0381] 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.

[0382] 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. 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. 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.

[0383] 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 baseplate 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 baseplate 60. The width of the reinforcing rib 80 refers to the width of a rib segment, such as the width of any one of the first to eighth rib segments 808. Optionally, the widths of the first to eighth rib segments 808 are equal; and the area of the reinforcing rib 80 refers to the total area of the orthographic projections of all rib segments (the first to eighth rib segments 808) on the compressor baseplate 60.

[0384] 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%.

[0385] A vibration simulation test of the compressor base plate 60 was carried out, and the ratio range of the width of the reinforcing rib 80 to the width of the first placement position 809 was 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, it can be seen that 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 conducive to reducing resonance and reducing noise.

[0386] 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%.

[0387] Vibration simulation tests show that a ratio of the rib 80 width to the compressor baseplate 60 width in the range of 7%-20% achieves greater results in improving the stiffness of the compressor baseplate 60. Alternatively, the rib 80 height can be 9mm, 10mm, or 11mm. Simulation tests show that increasing the rib 80 height to 9mm-11mm achieves greater results in improving the stiffness of the compressor baseplate 60, compared to a rib 80 height in the range of 3.5-5mm, effectively raising the natural frequency of the compressor baseplate 60.

[0388] Optionally, the area of the reinforcing rib 80 accounts for 23%, 25%, or 27% of the area of the compressor base plate 60 .

[0389] According to simulation tests, the area of the reinforcing rib 80 accounts for 20%-30% of the area of the compressor base plate 60, which has a greater effect of improving the stiffness. When the ratio range of the area of the reinforcing rib 80 to the area of the compressor base plate 60 is less than 20%, the effect of improving the stiffness of the compressor base plate 60 is not obvious, and the compressor base plate 60 is easy to deform; when the area of the reinforcing rib 80 accounts for the area of the compressor base plate 60 More than 30%, the first placement position 809 and the second placement position 810 are squeezed out, causing the compressor base plate 60 to lose effective loading space.

[0390] In some embodiments, a control device for refrigeration equipment is provided, comprising a processor and a memory storing program instructions, wherein the processor is configured to execute the control method for the refrigeration equipment as described in the above embodiments when running the program instructions.

[0391] like Figure 22 As shown, the embodiment of the present disclosure also provides a control method for a refrigeration device, including:

[0392] S11, when the actual temperature of the storage cavity reaches the shutdown condition of the cascade refrigeration system, the processor shuts down the high-temperature refrigeration cycle loop and the low-temperature refrigeration cycle loop;

[0393] S12, when the actual temperature reaches the start-up condition of the cascade refrigeration system, the processor starts the low-temperature refrigeration cycle loop; when the low-temperature cycle refrigeration loop meets the refrigeration requirements, the low-temperature refrigeration cycle loop is cyclically shut down and started; the refrigeration requirement is that the actual temperature at the current moment is less than or equal to the actual temperature at the previous moment.

[0394] In the embodiment of the present disclosure, after the system is shut down, if it is determined that the actual temperature of the storage chamber meets the startup conditions, and if the low-temperature circulating refrigeration circuit meets the refrigeration requirements, the low-temperature refrigeration circulating circuit is started for refrigeration, and the low-temperature refrigeration demand can be met by repeatedly starting and stopping the low-temperature refrigeration circulating circuit. During the above-mentioned time period when the low-temperature refrigeration circulating circuit is operating, the high-temperature refrigeration circulating circuit is temporarily in a shutdown state. Therefore, the overall operating noise of the refrigeration equipment is greatly reduced. When only the low-temperature refrigeration circulating system is running, the noise is 2 to 3 dB(A) lower, thereby making the refrigeration equipment have a wider range of applicable scenarios.

[0395] Optionally, when the low-temperature circulating refrigeration circuit does not meet the refrigeration requirements, the high-temperature circulating refrigeration circuit is turned on; when the actual temperature meets the shutdown conditions, the high-temperature circulating refrigeration circuit and the low-temperature circulating refrigeration circuit are returned to be shut down.

[0396] In the disclosed embodiments, if the actual temperature of the storage chamber is determined to meet startup conditions but the low-temperature refrigeration circuit does not meet the refrigeration requirements, activating both the high- and low-temperature refrigeration circuits simultaneously will place higher demands on the startup performance of the cascade refrigeration device. Therefore, the high-temperature refrigeration circuit may be activated first for a predetermined period of time before the low-temperature refrigeration circuit is activated, thereby reducing the startup performance requirements of the cascade refrigeration device.

[0397] After the refrigeration equipment is turned on and the cascade refrigeration system has completed the energy temperature reduction, the cascade refrigeration device may not need to continue to operate. When the actual temperature of the storage chamber has reached the shutdown condition of the cascade refrigeration device, the cascade refrigeration device can stop operating.

[0398] The storage chamber of the refrigeration device may be provided with a temperature sensor, through which the actual temperature of the storage chamber of the refrigeration device may be acquired. The temperature sensor may send the acquired actual temperature to the processor of the refrigeration device.

[0399] Optionally, the refrigeration start condition may be that the actual temperature is greater than the sum of the user-set temperature and the temperature threshold, or the refrigeration start condition may be that the cascade refrigeration device is shut down for more than a preset time.

[0400] It should be noted that setting the temperature threshold too high may cause the actual temperature of the storage chamber to differ significantly from the user-set temperature, making the refrigeration unit's performance less than the user's expectations. Setting the temperature threshold too low may cause the cascade refrigeration unit to repeatedly shut down and start up, affecting the unit's startup performance.

[0401] Alternatively, as Figure 23 As shown, the embodiment of the present application provides another control method for a refrigeration device, including:

[0402] S501, the processor confirms that the actual temperature in the storage chamber meets the startup conditions of the cascade refrigeration device;

[0403] S502, the processor starts the low-temperature refrigeration cycle when the user-set temperature is greater than the first temperature;

[0404] S503: The processor cyclically shuts down and starts up the low-temperature refrigeration cycle according to the shutdown condition and the startup condition of the cascade refrigeration device.

[0405] The first temperature is used to indicate a refrigeration capacity threshold of the cascade refrigeration device.

[0406] In this embodiment, after the refrigeration equipment is turned on and the cascade refrigeration device has completed the energy temperature reduction, the cascade refrigeration device may not need to continue to operate. If the actual temperature inside the storage chamber has reached the shutdown condition of the cascade refrigeration device, the cascade refrigeration device can stop operating.

[0407] After the cascade refrigeration device stops operating, the actual temperature inside the storage chamber will rise for a period of time. When the actual temperature meets the startup conditions of the cascade refrigeration device again, the cascade refrigeration device needs to be started again to allow the cascade refrigeration equipment to perform heat exchange with the storage chamber so that the temperature inside the storage chamber meets the cooling requirements set by the user.

[0408] A temperature sensor may be provided in the storage chamber of the refrigeration device, and the actual temperature in the storage chamber of the refrigeration device may be acquired through the temperature sensor. The temperature sensor may send the acquired actual temperature to the processor of the refrigeration device.

[0409] Optionally, the startup condition may be that the actual temperature is greater than the sum of the user-set temperature and the temperature threshold, or the startup condition may be that the cascade refrigeration device has been shut down for more than a preset time.

[0410] It should be noted that setting the temperature threshold too high may cause a significant difference between the actual temperature in the storage chamber and the user-set temperature, making it difficult for the refrigeration equipment to meet user expectations. Setting the temperature threshold too low may cause the cascade refrigeration equipment to repeatedly shut down and start up, affecting the cascade refrigeration unit's startup performance.

[0411] Optionally, the temperature threshold value in the embodiment of the present application may be in the range of 1°C to 3°C.

[0412] Optionally, the shutdown condition may be that the actual temperature is less than or equal to the difference between the user-set temperature and the temperature threshold, or the startup condition may be that the cascade refrigeration device is started for more than a preset time.

[0413] Optionally, the processor may cyclically shut down and start up the low-temperature refrigeration cycle according to the shutdown condition and the startup condition of the cascade refrigeration device, specifically including:

[0414] S5031, the processor determines whether the actual temperature is less than or equal to the difference between the user-set temperature and the temperature threshold. If so, execute S5032; if not, execute S5034;

[0415] S5032, the processor sends a shutdown instruction to the controller of the low-temperature refrigeration cycle loop;

[0416] S5033, the processor determines whether the actual temperature is greater than or equal to the sum of the user-set temperature and the temperature threshold. If so, execute S5034; if not, execute S5032.

[0417] S5034: The processor sends a power-on instruction to the controller of the low-temperature refrigeration cycle loop to execute S5031.

[0418] After the refrigeration device completes its temperature reduction, the lowest refrigeration temperature that the low-temperature refrigeration cycle can achieve operating alone can be used as the limit temperature. If the user-set temperature is higher than this limit temperature, the refrigeration device's processor can activate the low-temperature refrigeration cycle. If the user-set temperature is lower than this limit temperature, the refrigeration device's processor may not be able to meet the user's cooling expectations by activating the low-temperature refrigeration cycle alone. Considering the long-term and stable operation of cascade refrigeration equipment, the first temperature in the embodiment of the present application can be selected above this limit temperature.

[0419] Optionally, when the refrigeration temperature range of the low-temperature refrigeration cycle loop when working alone is -5°C to -45°C, the value of the above-mentioned first boundary temperature is selected and pre-set between -35°C and -40°C.

[0420] After powering on the refrigeration equipment and completing the temperature pull-down, the cascade refrigeration device needs to be started again. When the user sets the temperature higher than the first temperature, the processor of the refrigeration equipment can send a power-on instruction to the controller of the low-temperature refrigeration system to start the low-temperature circulating refrigeration circuit in the cascade refrigeration device separately. After the low-temperature refrigeration circulation circuit starts working, the processor can send a shutdown instruction to the controller of the low-temperature refrigeration circulation circuit based on the actual temperature changes in the storage cavity when the shutdown conditions are met, so as to shut down the low-temperature refrigeration circulation circuit; when the startup conditions are met, the processor sends a power-on instruction to the controller of the low-temperature refrigeration circulation circuit, and the low-temperature refrigeration circulation circuit is started again, and the cycle repeats. By supplying cooling to the storage cavity through the low-temperature refrigeration circulation circuit, the temperature in the storage cavity will be maintained within a range centered on the user-set temperature and bounded by the temperature threshold, thereby meeting the user's cooling needs.

[0421] As can be understood, since the high-temperature refrigeration circuit remains shut down while the low-temperature refrigeration circuit operates independently, this not only saves energy but also significantly reduces the operating noise of the refrigeration equipment. Experiments have shown that when the low-temperature refrigeration circuit operates independently, noise can be reduced by 2dB(A) to 3dB(A) compared to when the high- and low-temperature refrigeration circuits operate simultaneously.

[0422] It should be noted that the processor for executing the control method for the refrigeration equipment may be configured in the refrigeration equipment or in a server that is in communication with the refrigeration equipment, which is not specifically limited in the present embodiment.

[0423] Thus, the control method for refrigeration equipment provided in an embodiment of the present application enables, when the cascade refrigeration device needs to be restarted, to start the low-temperature refrigeration cycle circuit for refrigeration if the user sets the temperature to be greater than the first temperature. The low-temperature refrigeration cycle circuit is repeatedly started and stopped to meet the low-temperature refrigeration demand. During the aforementioned time period when the low-temperature refrigeration cycle circuit is operating, the high-temperature refrigeration cycle circuit is temporarily shut down. As a result, the overall operating noise of the refrigeration equipment is greatly reduced, making the refrigeration equipment applicable in a wider range of scenarios.

[0424] Combine Figure 24 , an embodiment of the present application provides another control method for a refrigeration device, comprising:

[0425] S601, the processor confirms that the actual temperature in the storage chamber meets the startup conditions of the cascade refrigeration device;

[0426] S602, the processor starts the low-temperature refrigeration cycle when the user-set temperature is greater than the first temperature;

[0427] S603, the processor cyclically shuts down and starts up the low-temperature refrigeration cycle according to the shutdown conditions and startup conditions of the cascade refrigeration device;

[0428] S604: When the user-set temperature is less than or equal to the first temperature, the processor starts the low-temperature refrigeration cycle after starting the high-temperature refrigeration cycle for a first preset time.

[0429] S605: When the actual temperature meets the shutdown condition, shut down the high-temperature refrigeration cycle loop and the low-temperature refrigeration cycle loop in operation.

[0430] In this embodiment, after the refrigeration device is powered on and the temperature is pulled down, if the user-set temperature is less than or equal to the first temperature, the low-temperature cycle alone may not be able to maintain the cooling effect. Therefore, the refrigeration device needs to make the high- and low-temperature refrigeration cycles work together, with the high-temperature refrigeration cycle exchanging heat with the low-temperature refrigeration cycle, so that the low-temperature refrigeration cycle can provide lower temperature cooling capacity for the storage chamber.

[0431] Specifically, after the refrigeration equipment is powered on and the temperature is pulled down, the cascade refrigeration device needs to be started again. When the user-set temperature is less than or equal to the first temperature, the processor of the refrigeration equipment can send a power-on command to the controller of the high-temperature refrigeration cycle circuit to start the high-temperature circulation refrigeration circuit alone first. After the high-temperature refrigeration cycle circuit has been working for a first preset period of time, the processor again sends a power-on command to the controller of the low-temperature refrigeration cycle circuit to start the low-temperature refrigeration cycle circuit. When the shutdown conditions are met, the processor sends shutdown commands to the controller of the high-temperature refrigeration cycle circuit and the controller of the low-temperature refrigeration cycle circuit respectively to shut down the high-temperature refrigeration cycle circuit and the low-temperature refrigeration cycle circuit; when the power-on conditions are met again, the processor can return to determine the relationship between the user-set temperature and the first temperature, so that when the first temperature is adjusted and increased, the high-temperature circulation refrigeration circuit can be shut down in time to achieve a noise reduction effect, and so on.

[0432] It is understood that if the high-temperature refrigeration cycle and the low-temperature refrigeration cycle are started simultaneously, higher startup performance requirements will be imposed on the cascade refrigeration device. Therefore, the high-temperature refrigeration cycle can be started first for a first preset time period before the low-temperature refrigeration cycle is started, thereby reducing the startup performance requirements of the cascade refrigeration device.

[0433] Optionally, the first preset duration can be selected within 2 minutes to 4 minutes.

[0434] As previously mentioned, the refrigeration equipment provided in the embodiments of the present application includes a first regenerator separately provided in the low-temperature refrigeration cycle and / or a second regenerator provided between the high-temperature refrigeration cycle and the low-temperature cycle, and uses a refrigerant that meets the requirements to reduce the operating pressure of the cascade refrigeration device. Therefore, when the high-temperature refrigeration cycle and the low-temperature refrigeration cycle of the cascade refrigeration device operate together, the operating noise of the entire cascade refrigeration device is between 30dB(A) and 38dB(A), greatly reducing the operating noise of the refrigeration device.

[0435] Thus, the control method for a refrigeration device provided in the embodiments of the present application can determine, based on the user's cooling needs, whether to activate the low-temperature refrigeration cycle or to determine whether the high-temperature refrigeration cycle and the low-temperature refrigeration cycle work together. This not only enables the refrigeration device to meet the cooling needs, but also reduces the noise generated by the refrigeration device during use, allowing the refrigeration device to meet the noise requirements of household use.

[0436] In practical applications of the above embodiment, the control method for refrigeration equipment specifically performs the following steps:

[0437] S6001: The processor confirms that the actual temperature in the storage chamber meets the startup conditions of the cascade refrigeration device.

[0438] S6002, the processor determines whether the user-set temperature is greater than the first temperature; if so, execute S6003; if not, execute S6007;

[0439] S6003, the processor sends a power-on instruction to the controller of the low-temperature refrigeration cycle loop;

[0440] S6004: The processor determines whether the actual temperature is less than or equal to the difference between the user-set temperature and the temperature threshold. If so, the processor executes S6005; if not, the processor executes S6003.

[0441] S6005, the processor sends a shutdown instruction to the controller of the low-temperature refrigeration cycle loop;

[0442] S6006: The processor determines whether the actual temperature is greater than or equal to the sum of the user-set temperature and the temperature threshold. If so, execute S6003; if not, execute S6005.

[0443] S6007: The processor sends a power-on instruction to the controller of the high-temperature refrigeration cycle loop.

[0444] S6008, after the first preset time, the processor sends a power-on instruction to the controller for starting the low-temperature refrigeration cycle;

[0445] S6009: The processor determines whether the actual temperature is less than or equal to the difference between the user-set temperature and the temperature threshold. If so, the processor executes S6010; if not, the processor executes S6001.

[0446] S6010: The processor sends a shutdown instruction to the controller of the high-temperature refrigeration cycle loop and the controller of the low-temperature refrigeration cycle loop.

[0447] An embodiment of the present application provides another method for a refrigeration device. Before the processor confirms that the actual temperature in the storage chamber meets the startup conditions of the cascade refrigeration device and before the cascade refrigeration system is powered on, the control method further includes:

[0448] S401, receiving a power-on instruction;

[0449] S402: Determine an initial startup strategy for the cascade refrigeration device according to a relationship between the ambient temperature of the cascade refrigeration device and the first temperature range.

[0450] In this embodiment, the refrigeration device may be provided with a temperature sensor outside the cascade refrigeration equipment or the storage chamber to obtain the ambient temperature of the environment in which the refrigeration device is located, and send the ambient temperature to the processor of the refrigeration device.

[0451] Ambient temperature affects the actual temperature within the refrigeration unit's storage chamber. Higher ambient temperatures increase the actual temperature within the storage chamber, while lower ambient temperatures decrease it. Accordingly, depending on the actual temperature within the storage chamber, cascade refrigeration units can use different startup strategies to reduce the temperature upon receiving a power-on command. This saves energy while also reducing the operating noise of the refrigeration unit.

[0452] In this way, when the refrigeration equipment is powered on, the startup strategy of the cascade refrigeration device is determined according to the ambient temperature, thereby improving the intelligence of the refrigeration equipment in adapting to the environment.

[0453] Optionally, determining an initial startup strategy for the cascade refrigeration device based on a relationship between the ambient temperature of the cascade refrigeration device and the first temperature range includes:

[0454] S4021: When the ambient temperature is within the first temperature range, the processor starts the high-temperature refrigeration cycle.

[0455] S4022, the processor starts the low-temperature refrigeration cycle after the second preset time period;

[0456] S4023: When the actual temperature meets the shutdown condition, the processor shuts down the high-temperature refrigeration cycle loop and the low-temperature refrigeration cycle loop in operation.

[0457] In this embodiment, when the ambient temperature is within a first temperature range, the processor of the refrigeration device may activate the high-temperature refrigeration cycle. After the high-temperature refrigeration cycle has been activated for a second preset period of time, the low-temperature refrigeration cycle may be activated, allowing the refrigeration device to quickly warm up and enter a stable operation phase. After the refrigeration device enters the stable operation phase, if the actual temperature within the storage chamber meets the shutdown conditions, the high-temperature and low-temperature refrigeration cycles may be shut down.

[0458] When the actual temperature rises again, or the cascade refrigeration device is shut down for more than a preset time, the processor of the refrigeration equipment has determined that the actual temperature in the storage chamber meets the startup conditions of the cascade refrigeration device again, and the cascade refrigeration device can be started again by the control method in the above embodiment of the present application.

[0459] Optionally, the first temperature interval may be a temperature interval of 16°C to 32°C.

[0460] Optionally, the second preset duration can be selected between 10 minutes and 15 minutes.

[0461] In this way, the specific startup strategy of the cascade refrigeration device can be determined according to the actual situation of the use environment of the refrigeration equipment, so as to improve the intelligence of the refrigeration equipment in adjusting the control strategy according to the environment.

[0462] Combine Figure 25 When the refrigeration device receives a power-on instruction and the ambient temperature is within the first temperature range, the method for the refrigeration device provided in the embodiment of the present application includes:

[0463] S701, the processor receives a power-on instruction;

[0464] S702, when the ambient temperature is within the first temperature range, the processor starts a high-temperature refrigeration cycle;

[0465] S703, the processor starts the low-temperature refrigeration cycle after the second preset time;

[0466] S704: If the actual temperature meets the shutdown condition, the processor shuts down the high-temperature refrigeration cycle and the low-temperature refrigeration cycle in operation.

[0467] S705 , the processor confirms that the actual temperature in the storage chamber meets the startup conditions of the cascade refrigeration device;

[0468] S706, the processor starts the low-temperature refrigeration cycle when the user-set temperature is greater than the first temperature;

[0469] S707, the processor cyclically shuts down and starts up the low-temperature refrigeration cycle according to the shutdown conditions and startup conditions of the cascade refrigeration device;

[0470] S708, when the user-set temperature is less than or equal to the first temperature, the processor starts the low-temperature refrigeration cycle after starting the high-temperature refrigeration cycle for a first preset time;

[0471] S709: When the actual temperature meets the shutdown conditions, shut down the high-temperature refrigeration cycle loop and the low-temperature refrigeration cycle loop in operation.

[0472] In this way, when the refrigeration equipment is at a relatively normal ambient temperature, the high- and low-temperature refrigeration circuits can be used to lower the temperature. After the temperature is lowered, if the actual temperature reaches the shutdown condition, the high- and low-temperature refrigeration circuits are shut down. A restart strategy for the cascade refrigeration device is then determined based on the relationship between the user-set temperature and the first temperature. If the cooling demand can be met by activating the low-temperature refrigeration circuit alone, the low-temperature refrigeration circuit can be used to provide independent cooling, thereby reducing the operating noise of the entire refrigeration equipment.

[0473] Combine Figure 26 In practical applications, the control method for refrigeration equipment in the above embodiment specifically performs the following steps:

[0474] S801, the processor receives a power-on instruction;

[0475] S802: When the ambient temperature is within the first temperature range, the processor sends a power-on instruction to the controller of the high-temperature refrigeration cycle and counts a second preset time.

[0476] S803, the processor sends a power-on instruction to the controller of the low-temperature refrigeration cycle loop;

[0477] S804, the processor determines whether the actual temperature is less than or equal to the difference between the user-set temperature and the temperature threshold. If so, execute S805; if not, execute S803;

[0478] S805, the processor sends a shutdown instruction to the controller of the high-temperature refrigeration cycle loop and the controller of the low-temperature refrigeration cycle loop;

[0479] S806: The processor determines whether the actual temperature is greater than or equal to the sum of the user-set temperature and the temperature threshold; if so, execute S807; if not, execute S805;

[0480] S807, the processor determines whether the user-set temperature is greater than the first temperature; if so, execute S808; if not, execute S812;

[0481] S808, the processor sends a power-on instruction to the controller of the low-temperature refrigeration cycle circuit;

[0482] S809, the processor determines whether the actual temperature is less than or equal to the difference between the user-set temperature and the temperature threshold. If so, execute S810; if not, execute S808;

[0483] S810, the processor sends a shutdown instruction to the controller of the low-temperature refrigeration cycle loop;

[0484] S811, the processor determines whether the actual temperature is greater than or equal to the sum of the user-set temperature and the temperature threshold. If so, execute S808; if not, execute S810;

[0485] S812, the processor sends a power-on instruction to the controller of the high-temperature refrigeration cycle loop;

[0486] S813: After the first preset time, the processor sends a power-on instruction to the controller of the low-temperature refrigeration cycle loop and returns to execute S804.

[0487] Optionally, determining an initial startup strategy for the cascade refrigeration device based on a relationship between the ambient temperature of the cascade refrigeration device and the first temperature range includes:

[0488] S4024, when the ambient temperature is lower than the minimum value in the first temperature range, starting the low-temperature refrigeration cycle;

[0489] S4025, according to the shutdown conditions and startup conditions, cyclically shut down and start the low-temperature refrigeration cycle.

[0490] In this embodiment, if the ambient temperature of the refrigeration device is relatively low, such as when the refrigeration device is used in a relatively cold region, and the ambient temperature is already below the lower limit of the first temperature range, the actual temperature in the storage chamber is also relatively low. Activating only the low-temperature refrigeration cycle can reduce the temperature of the storage chamber, thereby allowing the cascade refrigeration device to enter a stable operating state.

[0491] After the cascade refrigeration unit enters a stable operating state, since the ambient temperature is in a relatively low range, the controller of the refrigeration equipment can start or stop the entire process through the low-temperature refrigeration cycle according to the relationship between the user-set temperature and the actual temperature, thereby meeting the refrigeration needs while saving energy and reducing noise.

[0492] In this way, when the ambient temperature is at a relatively low temperature, only the low-temperature circulating refrigeration circuit can be started, and the refrigeration work can be completed throughout the process through the low-temperature refrigeration circulating circuit, thereby saving energy and reducing noise.

[0493] In practical applications of the above embodiment, when the ambient temperature is lower than the minimum value in the first temperature range, the control method for the refrigeration equipment specifically performs the following steps:

[0494] S901, the processor sends a signal to the controller of the refrigeration cycle loop to start refrigeration at the low temperature stage.

[0495] S902, the processor determines whether the actual temperature is less than or equal to the difference between the user-set temperature and the temperature threshold. If so, execute S903; if not, execute S901;

[0496] S903, the processor sends a shutdown instruction to the controller of the low-temperature refrigeration cycle loop;

[0497] S904, the processor determines whether the actual temperature is greater than or equal to the sum of the user-set temperature and the temperature threshold. If so, execute S901; if not, execute S903.

[0498] Optionally, determining an initial startup strategy for the cascade refrigeration device based on a relationship between the ambient temperature of the cascade refrigeration device and the first temperature range includes:

[0499] S4026: When the ambient temperature is greater than the maximum value in the first temperature range, the processor starts the low-temperature refrigeration cycle after starting the high-temperature refrigeration cycle for a third preset time period.

[0500] S4027: The processor cyclically stops and starts the high-temperature refrigeration cycle loop and the low-temperature refrigeration cycle loop according to the shutdown condition and the startup condition.

[0501] In this embodiment, if the ambient temperature of the refrigeration device is relatively high, such as a refrigeration device used in a tropical region, and the ambient temperature is already higher than the upper limit of the first temperature range, indicating that the actual temperature in the storage chamber is also relatively high, starting only the low-temperature refrigeration cycle cannot complete the temperature reduction, and the high-temperature refrigeration cycle needs to be started first. To avoid simultaneous startup, the low-temperature refrigeration cycle can be started after a third preset time to participate in the temperature reduction. When the temperature reduction is completed, the cascade refrigeration device enters a stable operating state.

[0502] After the cascade refrigeration unit enters a stable operating state, due to the relatively high ambient temperature, the refrigeration equipment controller can, based on the relationship between the user-set temperature and the actual temperature, operate the high-temperature and low-temperature refrigeration cycles together throughout the entire process, using a cyclic start-stop method to meet cooling needs. Since the operating noise of the entire cascade refrigeration unit is between 30dB(A) and 38dB(A), the operating noise of the refrigeration equipment has been greatly reduced. Therefore, even if the high-temperature and low-temperature refrigeration cycles are operating together, the refrigeration equipment can still be used in home life scenarios.

[0503] In this way, the refrigeration equipment provided in the embodiment of the present application can not only meet the refrigeration needs according to the ambient temperature, but also reduce the noise of the refrigeration equipment during use, so that the refrigeration equipment can meet the noise requirements of household use.

[0504] In practical applications, when the ambient temperature of the processor is greater than the maximum value in the first temperature range, the control method for the refrigeration device specifically performs the following steps:

[0505] S1001, the processor starts the high-temperature refrigeration cycle and counts the third preset time period;

[0506] S1002, the processor sends a power-on instruction to the controller of the low-temperature refrigeration cycle loop;

[0507] S1003, the processor determines whether the actual temperature is less than or equal to the difference between the user-set temperature and the temperature threshold. If so, execute S1004; if not, execute S1002;

[0508] S1004, the processor shuts down the high-temperature refrigeration cycle loop and the low-temperature refrigeration cycle loop;

[0509] S1005, the processor determines whether the actual temperature is greater than or equal to the sum of the user-set temperature and the temperature threshold. If so, execute S1006; if not, execute S1004;

[0510] S1006, the processor starts the high-temperature refrigeration cycle;

[0511] S1007: After a fourth preset time period, the processor starts the low-temperature refrigeration cycle and executes S1003.

[0512] Optionally, the third preset duration may be selected from 10 minutes to 15 minutes.

[0513] Optionally, the fourth preset duration may be selected from 2 minutes to 5 minutes.

[0514] By using the control device for refrigeration equipment provided in an embodiment of the present application, when the cascade refrigeration device needs to be restarted after the refrigeration device is electrically heated, if the user sets a temperature greater than the first temperature, the low-temperature refrigeration cycle loop is started for refrigeration, and the low-temperature refrigeration cycle loop is repeatedly started and stopped to meet the low-temperature refrigeration demand. During the above-mentioned time period when the low-temperature refrigeration cycle loop is operating, the high-temperature refrigeration cycle loop is temporarily in a shutdown state. Therefore, the overall operating noise of the refrigeration equipment is greatly reduced, thereby making the refrigeration equipment have a wider range of applicable scenarios.

[0515] The beneficial effects of various implementations in this embodiment can be specifically referred to the beneficial effects of the corresponding implementations in the above control method embodiment. To avoid repetition, they will not be described here.

[0516] like Figure 21 As shown, the high-temperature evaporator 108 and the second capillary tube 1052 are connected in series to form a first branch, the first capillary tube 1051 and the evaporation part of the evaporative condenser 30 are connected in series to form a second branch, and the first branch and the second branch are connected in parallel and connected between the high-temperature compressor and the high-temperature condenser. In other embodiments, the present disclosure provides another control method for a refrigeration device, combined with Figure 27 The control method includes:

[0517] S1302: The processor obtains the chamber temperature Tc and the target temperature To of the storage chamber.

[0518] S1304: When Tc≥T1 and To>Tr, the processor controls the low-temperature refrigeration cycle to start.

[0519] S1306, when Tc≥T1 and To≤Tr, the processor controls the second branch of the high-temperature refrigeration cycle to be turned on, delays for a first time period, and controls the low-temperature refrigeration cycle to start.

[0520] S1308: When Tc≤T2, the processor controls the low-temperature refrigeration cycle and the high-temperature refrigeration cycle to stop running.

[0521] Wherein, T1>T2, T1 is the first temperature threshold, T2 is the second temperature threshold, and Tr is the reference temperature threshold.

[0522] The control method provided by the embodiment of the present disclosure is applied to the refrigeration equipment of any of the above embodiments. Among them, the low-temperature evaporator is used to cool the inside of the box. The control method includes: after the refrigeration equipment is turned on, after the cascade refrigeration system has completed the energy temperature pull-down, the cascade refrigeration system may not need to continue to operate. When the chamber temperature of the storage chamber has reached the shutdown condition of the cascade refrigeration system, the cascade refrigeration system stops running. And the chamber temperature Tc of the storage chamber is continuously or periodically obtained to monitor the chamber temperature. In the case of Tc≥T1, it means that the current chamber temperature Tc rises above the first temperature threshold, and then the cascade refrigeration system needs to be turned on to cool down the inside of the box. Further, the target temperature To is compared with the reference temperature threshold Tr to determine the operation strategy of the high-temperature refrigeration cycle loop and the low-temperature refrigeration cycle loop. Among them, the reference temperature threshold Tr indicates the refrigeration capacity demarcation value of the cascade refrigeration equipment.

[0523] In the case of To>Tr, the low-temperature refrigeration cycle can be started to meet the refrigeration demand, 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. Therefore, the overall working noise of the refrigeration equipment is greatly reduced, so that the refrigeration equipment has more diverse application scenarios. It can be understood that since the high-temperature refrigeration cycle remains in a shutdown state during the period when the low-temperature refrigeration cycle is working alone, not only energy saving is achieved, but the working noise of the refrigeration equipment is also greatly reduced. Experiments have shown that during the period when the low-temperature refrigeration cycle is operating alone, the noise can be reduced by 2dB(A) to 3dB(A) relative to the simultaneous operation of the high-temperature refrigeration cycle and the low-temperature refrigeration cycle.

[0524] If To ≤ Tr, the second branch of the high-temperature refrigeration cycle must be activated first to cool the refrigerant in the low-temperature refrigeration cycle to improve cooling efficiency within the cabinet. After this activation continues for a first duration, the low-temperature refrigeration cycle is activated. It is understood that activating both the high-temperature and low-temperature refrigeration cycles simultaneously places higher demands on the startup performance of the cascade refrigeration system. Therefore, the high-temperature refrigeration cycle can be activated first for a predetermined duration before the low-temperature refrigeration cycle is activated, reducing the startup performance requirements of the cascade refrigeration system.

[0525] Optionally, the first duration can be selected within 2 minutes to 4 minutes.

[0526] During the operation of the cascade refrigeration system, the storage chamber temperature Tc is continuously or periodically acquired to monitor the chamber temperature. If Tc ≤ T2, indicating that the storage chamber temperature has dropped, the cascade refrigeration system is shut down. This reduces energy consumption and noise.

[0527] Optionally, the value of T1 is the sum of the target temperature To and the temperature threshold. The value of T2 is the difference between the target temperature To and the temperature threshold. Setting the temperature threshold too high may result in a significant difference between the storage chamber temperature and the user-set temperature, making it difficult for the refrigeration device to meet user expectations. Setting the temperature threshold too low may cause the cascade refrigeration system to repeatedly shut down and start up, affecting the startup performance of the cascade refrigeration device.

[0528] Optionally, the temperature threshold value in the embodiment of the present application may be in the range of 1°C to 3°C.

[0529] Optionally, the first temperature interval may be a temperature interval of 16°C to 32°C.

[0530] Combine Figure 28 In some embodiments, the control method for a refrigeration device includes:

[0531] S1401: In response to an initial power-on request, the processor obtains the ambient temperature Ta of the refrigeration device.

[0532] S1402: The processor determines a startup strategy for a high-temperature refrigeration cycle loop and a low-temperature refrigeration cycle loop according to the ambient temperature Ta.

[0533] S1403: The processor controls the cascade refrigeration system to start according to the startup strategy.

[0534] In this embodiment, the refrigeration device may be provided with a temperature sensor outside the cascade refrigeration system or the storage chamber to obtain the ambient temperature of the environment in which the refrigeration device is located, and send the ambient temperature to the processor of the refrigeration device.

[0535] Ambient temperature affects the temperature of the storage chamber of a refrigeration unit. Higher ambient temperatures increase the storage chamber temperature accordingly; lower ambient temperatures decrease it. Accordingly, depending on the varying storage chamber temperatures, a cascade refrigeration unit can use different startup strategies to reduce the temperature upon receiving a power-on command. This saves energy while also reducing operating noise. In this way, when the refrigeration unit is powered on, the startup strategy is determined based on the ambient temperature, enhancing its intelligent adaptability to the environment.

[0536] Optionally, the steps of determining the startup strategies of the high-temperature refrigeration cycle and the low-temperature refrigeration cycle based on the ambient temperature Ta include: when Ta≥Ta1, first controlling the startup of the high-temperature refrigeration cycle, and then controlling the startup of the low-temperature refrigeration cycle; when Ta<Ta1, controlling the startup of the high-temperature refrigeration cycle; when the chamber temperature Tc of the storage chamber meets the shutdown conditions, controlling the cascade refrigeration system to shut down; wherein Ta1 is the first ambient temperature threshold.

[0537] In this embodiment, when Ta≥Ta1, the processor of the refrigeration equipment can start the high-temperature refrigeration cycle circuit, and after the high-temperature refrigeration cycle circuit has been started for a period of time, start the low-temperature refrigeration cycle circuit, so that the refrigeration equipment can quickly heat up and enter the stable operation stage. After the refrigeration equipment enters the stable operation stage, when the chamber temperature of the storage chamber meets the shutdown conditions, the high-temperature refrigeration cycle circuit and the low-temperature refrigeration cycle circuit in operation can be shut down. In the case of Ta<Ta1, it means that the ambient temperature is relatively low. By turning on the high-temperature refrigeration cycle circuit, the refrigeration demand of the first evaporator is met. At the same time, by monitoring the changes in the chamber temperature of the storage chamber, it is determined whether the low-temperature refrigeration cycle circuit needs to be turned on. In this way, the refrigeration needs of at least two chambers can be met, and the energy consumption of the entire machine can be reduced.

[0538] When the chamber temperature of the storage chamber rises again, the processor of the refrigeration device has determined that the chamber temperature of the storage chamber meets the startup conditions of the cascade refrigeration device again, and the cascade refrigeration device can be started again by the control method in the above embodiment of the present application.

[0539] In some embodiments, combined Figure 29 As shown, the control method for the refrigeration equipment includes:

[0540] S1501: In response to an initial power-on request, the processor obtains the ambient temperature Ta of the refrigeration device.

[0541] S1502: When Ta≥Ta2, the processor controls the first branch to be turned on and delays for a second time period.

[0542] S1503, the processor controls the second branch to be turned on, and controls the low-temperature refrigeration cycle to start.

[0543] S1504: When Ta2>Ta≥Ta1, the processor first controls the first branch to be turned on and delays for a third time period.

[0544] S1505, the processor controls the second branches to be turned on, and controls the low-temperature refrigeration cycle to start.

[0545] S1506: When Ta is less than Ta1, the processor first controls the first branch to be turned on and delays for a fourth time period.

[0546] S1507, the processor controls the second branch to be turned on, and controls the low-temperature refrigeration cycle to start.

[0547] Among them, Ta2 is the second ambient temperature threshold, Ta2>Ta1, the second time length is greater than or equal to the third time length, and the third time length is greater than or equal to the fourth time length.

[0548] In this embodiment, during initial power-up, the first branch of the high-temperature refrigeration cycle is activated to allow refrigerant to flow through the first evaporator and rapidly raise the temperature within the chamber corresponding to the first evaporator. After the first branch remains activated for a period of time, the second branch of the low-temperature refrigeration cycle is activated to raise the temperature of the storage chamber, thereby reducing the startup performance requirements of the cascade refrigeration equipment.

[0549] Furthermore, the on-time of the first branch can be set differently for different ambient temperature ranges. When the ambient temperature is relatively high, the on-time of the first branch is longer; when the ambient temperature is relatively low, the on-time of the first branch can be shortened. In this way, by appropriately setting the on-time of the first branch according to the ambient temperature, energy consumption can be reduced.

[0550] In some embodiments, combined Figure 30 As shown, the control method for the refrigeration equipment includes:

[0551] S1601: In response to an initial power-on request, the processor obtains the ambient temperature Ta of the refrigeration device.

[0552] S1602: When Ta≥Ta2, the processor controls the first branch to be turned on and delays for a second time period.

[0553] S1603, the processor controls the second branch to be turned on, and controls the low-temperature refrigeration cycle to start.

[0554] S1604: The processor continuously obtains the chamber temperature Tc of the storage chamber.

[0555] S1605, the processor determines whether Tc is less than or equal to T2. If the result is yes, it proceeds to S606; if the result is no, it returns to S1603.

[0556] S1606: The processor controls the low-temperature refrigeration cycle and the high-temperature refrigeration cycle to stop running.

[0557] S1607, the processor determines whether Tc is greater than or equal to T1, and if the result is yes, proceeds to S608; if the result is no, returns to S1606.

[0558] S1608, the processor controls the second branch of the high-temperature refrigeration cycle to be turned on, and delays for a fifth time period to control the low-temperature refrigeration cycle to start.

[0559] S1609: When Ta2>Ta≥Ta1, the processor first controls the first branch to be turned on and delays for a third time period.

[0560] S1610, the processor controls the second branches to be turned on, and controls the low-temperature refrigeration cycle to start.

[0561] S1611: The processor continuously obtains the chamber temperature Tc of the storage chamber.

[0562] S1612, the processor determines whether Tc is less than or equal to T2. If the result is yes, it goes to S1613; if the result is no, it returns to S1611.

[0563] S1613, the processor controls the low-temperature refrigeration cycle loop and the high-temperature refrigeration cycle loop in operation to stop operation.

[0564] S1614: The processor obtains the chamber temperature Tc and the target temperature To of the storage chamber.

[0565] S1615: The processor determines whether Tc is greater than or equal to T1. If the result is yes, the process proceeds to S1616. If the result is no, the process proceeds to S1613.

[0566] In step S1616, the processor determines whether To is greater than or equal to Tr. If the result is yes, the processor proceeds to step S1617; if the result is no, the processor proceeds to step S1618.

[0567] S1617, the processor controls the low-temperature refrigeration cycle to start;

[0568] S1618: The processor controls the second branch of the high-temperature refrigeration cycle to be turned on, and delays the first time period to control the low-temperature refrigeration cycle to start.

[0569] S1619: When Ta is less than Ta1, the processor first controls the first branch to be turned on and delays for a fourth time period.

[0570] S1620, the processor controls the second branch to be turned on, and controls the low-temperature refrigeration cycle to start.

[0571] S1621: The processor obtains the chamber temperature Tc of the storage chamber.

[0572] S1622, the processor determines whether Tc is less than or equal to T2. If the result is yes, it proceeds to S1623; if the result is no, it returns to S1621.

[0573] S1623, the processor controls the low-temperature refrigeration cycle loop and the high-temperature refrigeration cycle loop in operation to stop operation.

[0574] S1624, the processor determines whether Tc is greater than or equal to T1. If the result is yes, it proceeds to S1625; if the result is no, it returns to S1623.

[0575] S1625, the processor controls the second branch of the high-temperature refrigeration cycle to be turned on, and delays for a sixth time period to control the low-temperature refrigeration cycle to start.

[0576] Wherein, Ta2 is the second ambient temperature threshold, Ta2>Ta1, the second duration is greater than or equal to the third duration, and the third duration is greater than or equal to the fourth duration. In the embodiment of the present disclosure, when the power is first turned on, the first branch of the high-temperature refrigeration cycle is first controlled to be turned on, so that refrigerant flows through the first evaporator and the temperature in the chamber corresponding to the first evaporator can be quickly increased. After the first branch is controlled to be turned on for a period of time, the low-temperature refrigeration cycle and the second branch are controlled to be turned on to increase the chamber temperature of the storage chamber, thereby reducing the startup performance requirements for the cascade refrigeration equipment.

[0577] Furthermore, the on-time of the first branch can be set differently for different ambient temperature ranges. When the ambient temperature is relatively high, the on-time of the first branch is longer; when the ambient temperature is relatively low, the on-time of the first branch can be shortened. In this way, by appropriately setting the on-time of the first branch according to the ambient temperature, energy consumption can be reduced.

[0578] Furthermore, after the initial power-up, the system enters a stable operation phase, monitoring changes in the storage chamber temperature to determine whether the high- and low-temperature refrigeration cycles need to be restarted. When the storage chamber temperature rises again, the refrigeration unit's processor has determined that the storage chamber temperature again meets the cascade refrigeration unit's startup conditions, and can restart the cascade refrigeration unit using the control method described in the aforementioned embodiments of the present application. This allows the cooling needs of at least two chambers to be met while reducing overall system energy consumption.

[0579] Furthermore, during the stable operation phase of the refrigeration equipment, the corresponding control logic may be selected in combination with the ambient temperature so that the control of the cascade refrigeration system is combined with the ambient temperature to achieve energy saving and consumption reduction.

[0580] 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 expressly 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 compartment; 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 to intersect.

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 included 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°; or, 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 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 cabin, and the length direction of the other of the fifth compressor and the sixth compressor extends in the width direction of the compressor cabin.

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 cabin.

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 evaporator, and a first refrigerant flows through 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: An inner liner, wherein a bottom wall portion of the inner liner is raised upward to form a step; The outer shell is located outside the inner tank, and the outer shell and the steps enclose the compressor cabin; a partition 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; 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 portion; 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 regenerator is located between the inner container and the outer shell or between the partition and the inner container.

9. The refrigerator according to claim 1, characterized in that: Also includes: The compressor base plate includes a first base plate and a second base plate, wherein the first base plate and the second base plate are spaced apart and arranged at the bottom of the compressor cabin; One of the fifth compressor and the sixth compressor is located above the first base plate, and the other of the fifth compressor and the sixth compressor is located above the second base plate.

10. The refrigerator according to any one of claims 1 to 9, 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 compressor cabin is located at at least one of a left side of the box body, a right side of the box body, and a rear side of the box body.

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