Refrigerating system and refrigerating equipment

Abstract

The invention discloses a refrigerating system and refrigerating equipment, and the refrigerating system comprises a double-suction compressor, a first pipeline, a second pipeline, a third pipeline, a fourth pipeline, a condenser, a first assembly, a second assembly, a third assembly and a heat regenerator. The double-suction compressor is provided with a first suction port, a second suction port and an exhaust port, an inlet of the first pipeline is communicated with the exhaust port, an inlet of the second pipeline is communicated with an outlet of the first pipeline, an outlet of the second pipeline is communicated with the first suction port, and an inlet of the third pipeline is communicated with an outlet of the first pipeline. An outlet of the third pipeline communicates with the first air suction port or the second air suction port, the condenser is arranged on the first pipeline, the first assembly is arranged on the second pipeline, the second assembly is arranged on the third pipeline, and the heat regenerator is used for transmitting heat of a refrigerant flowing out of the exhaust port to at least one of the first air suction port and the second air suction port. The energy efficiency of the refrigerating system can be improved, heat and cold in the refrigerating system can be reasonably utilized, and cost is reduced.

Description

Technical Field

[0001] The present invention relates to the technical field of refrigeration systems, and in particular to a refrigeration system and a refrigeration device. Background Art

[0002] In the related art, refrigerators mainly use a single-suction compressor with one inlet and one outlet. At the same time, the rotary compressor only provides one compression ratio. The refrigerator controls the refrigeration by switching the refrigerant flow path through an electric valve for refrigeration and freezing. In fact, the evaporation temperatures required for refrigeration and freezing are different. Refrigeration only requires a smaller compression ratio, while freezing requires a larger compression ratio. The larger the compression ratio, the lower the efficiency of the compressor, and the heat and cold in the refrigeration system are not fully utilized. Due to the problem of low refrigeration efficiency, the current refrigeration system is difficult to provide a large cooling capacity, making it difficult to achieve a deep cooling effect. It should be noted that deep cooling generally refers to a temperature range of 233K (about -40°C) to 77K (about -196°C). Summary of the invention

[0003] The purpose of the present invention is to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides a refrigeration system that can improve the energy efficiency of the refrigeration system and can reasonably utilize the heat and cold in the refrigeration system to reduce costs.

[0004] The present invention also provides a refrigeration device having the above refrigeration system.

[0005] According to a first aspect of the present invention, a refrigeration system includes: a double-suction compressor, provided with a first suction port, a second suction port and an exhaust port; a first pipeline, the inlet of the first pipeline is connected to the exhaust port; a second pipeline, the inlet of the second pipeline is connected to the outlet of the first pipeline, and the outlet of the second pipeline is connected to the first suction port; a third pipeline, the inlet of the third pipeline is connected to the outlet of the first pipeline, and the outlet of the third pipeline is connected to the first suction port or the second suction port; a condenser, arranged in the first pipeline; a first component, arranged in the second pipeline, the first component includes a first throttling element and a first evaporator, the outlet of the first throttling element is connected to the inlet of the first evaporator; a second component A component is arranged in the third pipeline, the second component includes a second throttling element and a second evaporator, and the outlet of the second throttling element is connected to the inlet of the second evaporator; a third component is arranged in the second pipeline, the third component includes a gas-liquid separator and a third throttling element, the gas-liquid separator has an input port, a gas output port and a liquid output port, the outlet of the third throttling element is connected to the input port, and the liquid output port is connected to the inlet of the first throttling element; a fourth pipeline, the inlet of the fourth pipeline is connected to the gas output port, and the outlet of the fourth pipeline is connected to the second air intake port; a regenerator is used to transfer the heat of the refrigerant flowing out of the exhaust port to at least one of the first air intake port and the second air intake port.

[0006] According to the refrigeration system of the embodiment of the first aspect of the present invention, there are at least the following beneficial effects: by adopting a double suction compressor, and the refrigerant is diverted from the first pipeline to the second pipeline and the third pipeline, a first evaporator is provided in the second pipeline, and a second evaporator is provided in the third pipeline, thereby realizing double refrigeration. Specifically, the first suction port of the double suction compressor maintains the compression ratio of the original compressor, and the compression ratio of the second suction port of the double suction compressor is reduced, so that the overall compression ratio of the double suction compressor is reduced, thereby improving the coefficient of refrigeration (COP) of the refrigeration system, and improving the energy efficiency of the refrigeration system. Furthermore, by arranging the first throttling element and the third throttling element in the first pipeline, the refrigerant first passes through the third throttling element and the first throttling element to complete the secondary throttling, which can further reduce the pressure and temperature of the refrigerant, and then the refrigerant enters the first evaporator to complete evaporation, which can provide a larger cooling capacity and improve the deep cooling effect. In addition, a gas-liquid separator is arranged between the first throttling element and the third throttling element. After the refrigerant is throttled by the third throttling element, due to the reduction of pressure and boiling point, part of the refrigerant evaporates into gas. Therefore, the refrigerant flowing out of the third throttling element is in a gas-liquid mixed state. The gas-liquid separator separates the gaseous refrigerant and the liquid refrigerant, so that the gaseous refrigerant enters the second air intake port, which is conducive to the circulation of the refrigerant and improves the refrigeration efficiency. The liquid refrigerant enters the first throttling element to complete the secondary throttling. Due to the separation by the gas-liquid separator, the proportion of liquid refrigerant in the refrigerant before entering the first evaporator will be higher, and the liquid refrigerant has a better heat exchange effect, which is conducive to the refrigerant reaching a lower evaporation temperature, and can further improve the deep cooling effect. In addition, by arranging a regenerator in the refrigeration system, the regenerator can transfer the heat of the refrigerant flowing out of the exhaust port to at least one of the first air intake port and the second air intake port to achieve heat recovery, which can reasonably use the heat and cold capacity of the refrigeration system, improve the refrigeration capacity of the refrigeration system, further improve the energy efficiency of the refrigeration system, and reduce costs.

[0007] According to some embodiments of the present invention, the second pipeline includes a first section and a second section, the first section is connected to the inlet of the first throttling element, and the second section is connected to the outlet of the first evaporator, and the third pipeline includes a third section and a fourth section, the third section is connected to the inlet of the second throttling element, and the fourth section is connected to the outlet of the second evaporator.

[0008] According to some embodiments of the present invention, at least one of the second section and the fourth section exchanges heat with the first section through the regenerator.

[0009] According to some embodiments of the present invention, at least one of the second section and the fourth section exchanges heat with the third section through the regenerator.

[0010] According to some embodiments of the present invention, the third section exchanges heat with the fourth pipeline through the regenerator.

[0011] According to some embodiments of the present invention, at least one of the second section, the fourth section and the fourth pipeline exchanges heat with the first pipeline through the regenerator.

[0012] According to some embodiments of the present invention, the first pipeline includes a fifth section, the fifth section is connected to the outlet of the condenser, and at least one of the second section, the fourth section and the fourth pipeline exchanges heat with the fifth section through the regenerator.

[0013] According to some embodiments of the present invention, the second pipeline includes a sixth section, the sixth section is connected to the inlet of the third throttling element, and at least one of the second section, the fourth section and the fourth pipeline exchanges heat with the sixth section through the regenerator.

[0014] According to some embodiments of the present invention, the outlet of the third pipeline is connected to the second air intake port, the outlet of the third pipeline is connected to the outlet of the fourth pipeline, the fourth pipeline is provided with a one-way valve, the inlet of the one-way valve is connected to the gaseous output port, and the outlet of the one-way valve is connected to the second air intake port.

[0015] According to some embodiments of the present invention, the first pipeline is provided with a control valve, and the control valve connects the second pipeline and the third pipeline to control the refrigerant flow from the first pipeline to the second pipeline or the third pipeline.

[0016] According to some embodiments of the present invention, the first evaporator is a freezing chamber evaporator, and the second evaporator is a refrigerating chamber evaporator.

[0017] A refrigeration device according to an embodiment of the second aspect of the present invention includes a refrigeration system according to an embodiment of the first aspect.

[0018] The refrigeration device according to the second embodiment of the present invention comprises the refrigeration system of the first embodiment and therefore has at least the above-mentioned beneficial effects, which will not be described in detail herein.

[0019] Additional aspects and advantages of the present invention will be given in part in the following description and in part will be obvious from the following description, or will be learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] The present invention will be further described below with reference to the accompanying drawings and embodiments, wherein:

[0021] Figure 1 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0022] Figure 2 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0023] Figure 3 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0024] Figure 4 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0025] Figure 5 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0026] Figure 6 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0027] Figure 7 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0028] Figure 8 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0029] Fig. 9 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0030] Fig.10 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0031] Fig.11 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0032] Fig.12 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0033] Fig.13 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0034] Fig.14 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0035] Fig.15 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0036] Fig.16 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0037] Fig.17 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0038] Fig.18 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0039] Fig.19is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0040] Fig. 20 is a schematic diagram of a refrigeration system according to some embodiments of the present invention;

[0041] Fig.21 Schematic diagram of a refrigeration system according to some embodiments of the present invention.

[0042] Reference numerals:

[0043] Refrigeration system 1000;

[0044] Double suction compressor 100, first suction port 110, second suction port 120, exhaust port 130;

[0045] Condenser 200;

[0046] A first throttling element 300, a first evaporator 310;

[0047] A second throttling element 400, a second evaporator 410;

[0048] First pipeline 500, fifth section 510;

[0049] The second pipeline 600, the first section 610, the second section 620, and the sixth section 630;

[0050] The third pipeline 700, the third section 710, and the fourth section 720;

[0051] Fourth pipeline 800;

[0052] Gas-liquid separator 900 , input port 910 , gas output port 920 , liquid output port 930 , third throttling element 940 , regenerator 950 , control valve 960 , and one-way valve 970 . DETAILED DESCRIPTION

[0053] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0054] Reference Figure 1As shown, the refrigeration system 1000 provided in an embodiment of the present invention includes a double suction compressor 100, a first pipeline 500, a second pipeline 600, a third pipeline 700, a fourth pipeline 800, a condenser 200, a first component, a second component, a third component and a regenerator 950. Since the double suction compressor 100 is included, the refrigeration system 1000 of this embodiment can be understood as a double suction system. It should be noted that the double suction compressor 100 has an additional second suction port at the middle stroke of the traditional compressor. Therefore, the double suction compressor 100 has a first suction port 110 (main suction) and a second suction port 120 (secondary suction). The main suction maintains the compression ratio of the original compressor, and the compression ratio of the secondary suction is reduced. When the main suction and the secondary suction are mixed, the entire compression ratio is reduced under the condition that the cylinder of the original compressor remains unchanged, thereby improving the coefficient of refrigeration (COP) of the refrigeration system 1000 and making the system more energy-efficient. In addition, since the refrigeration system 1000 of this embodiment also includes a regenerator 950, the refrigeration system 1000 has a heat recovery function. The regenerator 950 cooperates with the double-suction compressor 100 to fully utilize the heat and cold in the system, further improving the energy efficiency of the system.

[0055] The following mainly describes the connection relationship between various components and pipelines. Figure 1 and Fig.12 As shown, the double suction compressor 100 has a first suction port 110, a second suction port 120 and an exhaust port 130, the inlet of the first pipeline 500 is connected to the exhaust port 130, the inlet of the second pipeline 600 is connected to the outlet of the first pipeline 500, the outlet of the second pipeline 600 is connected to the first suction port 110, the inlet of the third pipeline 700 is connected to the outlet of the first pipeline 500, and the outlet of the third pipeline 700 is connected to the first suction port 110 or the second suction port 120. Specifically, Figures 1 to 12 In the embodiment, the outlet of the third pipeline 700 is communicated with the first air intake port 110 . Figures 12 to 21, the outlet of the third pipeline 700 is communicated with the second air intake port 120. Further, the condenser 200 is arranged in the first pipeline 500, the first component is arranged in the second pipeline 600, the second component is arranged in the third pipeline 700, and the third component is arranged in the second pipeline 600. The first component and the second component can be understood as evaporation components. The first component includes a first throttling element 300 and a first evaporator 310, and the outlet of the first throttling element 300 is communicated with the inlet of the first evaporator 310, and the second component includes a second throttling element 400 and a second evaporator 410, and the outlet of the second throttling element 400 is communicated with the inlet of the second evaporator 410. The third component includes a gas-liquid separator 900 and a third throttling element 940. The gas-liquid separator 900 has an input port 910, a gas output port 920, and a liquid output port 930. The inlet of the third throttling element 940 is connected to the outlet of the first pipeline 500, the outlet of the third throttling element 940 is connected to the input port 910, and the liquid output port 930 is connected to the inlet of the first throttling element 300. The inlet of the fourth pipeline 800 is connected to the gas output port 920, and the outlet of the fourth pipeline 800 is connected to the second air intake port 120.

[0056] The following mainly explains the flow direction of the refrigerant and its temperature changes. Figure 1 and Fig.12 In the direction of the middle arrow, the refrigerant flows out of the double suction compressor 100 from the exhaust port 130. At this time, the refrigerant is in a gaseous state, and the pressure and temperature of the refrigerant are relatively high. Then, the refrigerant enters the first pipeline 500, and the refrigerant becomes liquid after heat dissipation through the condenser 200, and can enter the second pipeline 600 and the third pipeline 700. It can also be understood that the second pipeline 600 and the third pipeline 700 divert the refrigerant in the first pipeline 500. In the second pipeline 600, the refrigerant first passes through the third component and then passes through the first component. Specifically, after the refrigerant passes through the third throttling element 940 of the third component, its pressure and boiling point are reduced, part of the refrigerant evaporates, and the refrigerant becomes a low-temperature and low-pressure gas-liquid mixed state. Then, the gas-liquid mixed refrigerant is separated by the gas-liquid separator 900, so that the gaseous refrigerant enters the second air intake port 120, and the liquid refrigerant enters the first throttling element 300. After the liquid refrigerant passes through the first throttling element 300, its pressure and boiling point are further reduced, and then the liquid refrigerant continues to enter the first evaporator 310, and evaporates to become a low-temperature and low-pressure gas, and finally the refrigerant enters the first air intake port 110. In the third pipeline 700, the refrigerant passes through the second throttling element 400, and its pressure and boiling point are reduced. The refrigerant then enters the second evaporator 410 to evaporate and become a low-temperature and low-pressure gas. Figure 1 When the outlet of the third pipeline 700 is connected to the first air intake port 110, the refrigerant finally enters the first air intake port 110. Fig.12When the outlet of the third pipeline 700 is connected to the second air inlet 120, the refrigerant finally enters the second air inlet 120. It can also be understood that the refrigerant flows counterclockwise, the first pipeline 500 and the second pipeline 600 form a refrigeration circuit, and the first pipeline 500 and the third pipeline 700 form another refrigeration circuit, thereby realizing dual refrigeration.

[0057] It can be understood that, in some embodiments, the first evaporator 310 can be set as a freezer compartment evaporator to cool the freezer compartment, and the second evaporator 410 can be set as a refrigerator compartment evaporator to cool the refrigerator compartment.

[0058] It should be noted that in the second pipeline 600, the refrigerant first passes through the third throttling element 940 and then enters the first throttling element 300, realizing secondary throttling of the refrigerant, which can further reduce the pressure and temperature of the refrigerant, so that more gaseous refrigerant is converted into liquid refrigerant, which is conducive to the evaporation and heat absorption of the refrigerant in the first evaporator 310, so that the system can provide more cooling capacity and improve the deep cooling effect. In addition, the gas-liquid mixed refrigerant flowing out of the third throttling element 940 passes through the gas-liquid separator 900, wherein the gaseous refrigerant is separated, and the gaseous refrigerant enters the second air intake port 120, thereby realizing the recovery of the refrigerant, which is conducive to the circulation of the refrigerant and can improve the energy efficiency of the system. In addition, the gas-liquid separator 900 separates the gaseous refrigerant, which can reduce the content of the gaseous refrigerant in the gas-liquid mixed refrigerant and increase the proportion of the liquid refrigerant. It can also be understood as reducing the dryness of the gas-liquid mixed refrigerant, which is beneficial to the subsequent evaporation and heat absorption of the liquid refrigerant in the first evaporator 310, allowing the system to provide more cooling capacity and improve energy efficiency.

[0059] It should also be noted that, since the second pipeline 600 and the third pipeline 700 are connected in parallel, the second pipeline 600 and the third pipeline 700 divide the refrigerant in the first pipeline 500, and the refrigerant can enter the second pipeline 600 and the third pipeline 700 at the same time, which can improve the flow efficiency of the refrigerant and improve the refrigeration efficiency. In addition, different refrigeration elements can be adaptively configured on the second pipeline 600 and the third pipeline 700 to meet the corresponding refrigeration needs, and the configuration flexibility is better.

[0060] Furthermore, in some embodiments, the first evaporator 310 can be a full-liquid evaporator. Since the above-mentioned gas-liquid separator 900 can ensure that the proportion of liquid refrigerant is high, the full-liquid evaporator cooperates with the gas-liquid separator 900 to achieve better heat exchange effect. It should be noted that the full-liquid evaporator is a refrigeration element that uses a heat exchanger to cool a high-temperature liquid to a required temperature. Its working principle is based on the property of liquid absorbing heat during the evaporation process. The high-temperature liquid is cooled by a cooler and then evaporated to form low-temperature steam, which is then exchanged with the low-temperature liquid on the other side to achieve cooling of the high-temperature liquid, and heat exchange between liquids is achieved. This working mode makes the full-liquid evaporator have the advantages of high heat transfer efficiency, energy saving and environmental protection, and is suitable for a variety of industrial fields.

[0061] It is understandable that, referring to Figure 1 As shown, in some embodiments, a control valve 960 is provided at the connection of the first pipeline 500, the second pipeline 600 and the third pipeline 700. It can also be understood that the first pipeline 500 is provided with a control valve 960, and the control valve 960 connects the second pipeline 600 and the third pipeline 700. The control valve 960 is used to control the refrigerant flow from the first pipeline 500 to the second pipeline 600 or the third pipeline 700, and the refrigerant flow can be flexibly adjusted. For example, the refrigerant flow from the first pipeline 500 to the second pipeline 600 can be made greater than the refrigerant flow from the first pipeline 500 to the third pipeline 700, and more refrigerant can flow into the first evaporator 310 to provide more refrigeration capacity, which can improve the deep cooling effect of the freezing chamber. The control valve 960 can also be used to control the on-off of the pipeline. For example, when there is no refrigeration demand in the refrigerating chamber, the control valve 960 can be controlled to disconnect the first pipeline 500 and the third pipeline 700. Alternatively, when there is no refrigeration demand in the freezing chamber, the control valve 960 may be controlled to disconnect the first pipeline 500 and the second pipeline 600. The control valve 960 may be an electric valve.

[0062] It should be noted that the regenerator 950 is mainly used to transfer the heat of the refrigerant flowing out of the exhaust port 130 to at least one of the first air intake port 110 and the second air intake port 120. Specifically, it is mainly through connecting a part of the first pipeline 500, the second pipeline 600, the third pipeline 700 and the fourth pipeline 800 to the regenerator 950, so as to realize heat exchange of each pipeline and transfer of heat of the refrigerant in the pipeline, so as to recover the heat of the refrigerant and make full use of the heat and cold in the refrigeration system 1000, thereby improving the energy efficiency of the refrigeration system 1000 and reducing the cost.

[0063] In addition, it should be noted that when the compressor inhales refrigerant that has not fully absorbed heat and evaporated, liquid hammer will occur. The liquid hammer phenomenon mainly refers to: the refrigerant flowing out of the evaporator has not fully absorbed heat and evaporated, which will cause liquid refrigerant to be mixed in it. After the liquid refrigerant enters the compressor and is compressed, it will produce a large impact force, which will damage the internal parts of the compressor, and in severe cases, it will cause structural fractures of the internal parts.

[0064] Based on this, the present embodiment sets a regenerator 950, which transfers the heat of the refrigerant flowing out of the exhaust port 130 to at least one of the first air inlet 110 and the second air inlet 120, so that the temperature of the refrigerant before entering the first air inlet 110 or the second air inlet 120 increases, wherein the liquid refrigerant fully evaporates into a gaseous state, which can reduce the content of the liquid refrigerant and the risk of liquid hammer at the first air inlet 110 and the second air inlet 120. In addition, the present embodiment sets a gas-liquid separator 900, so that the gaseous refrigerant enters the second air inlet 120, and the liquid refrigerant is prevented from entering the second air inlet 120, which can also reduce the risk of liquid hammer at the second air inlet 120.

[0065] It is understandable that, referring to Figure 1 As shown, in some embodiments, the second pipeline 600 includes a first section 610 and a second section 620, and the first component is located between the first section 610 and the second section 620. Specifically, the first section 610 connects the inlet of the first throttling element 300 and the liquid output port 930 of the gas-liquid separator 900, and the second section 620 connects the first air intake port 110 and the outlet of the first evaporator 310. The refrigerant first passes through the first section 610, the first throttling element 300 and the first evaporator 310 in sequence, then passes through the second section 620, and finally enters the first air intake port 110. Since the refrigerant evaporates in the first evaporator 310, the temperature of the refrigerant in the first section 610 is greater than the temperature of the refrigerant in the second section 620. The third pipeline 700 includes a third section 710 and a fourth section 720, and the second component is located between the third section 710 and the fourth section 720. Specifically, the third section 710 connects the inlet of the second throttling element 400 and the outlet of the first pipeline 500. Referring to Figure 1 As shown, when the third pipeline 700 is connected to the first air intake port 110, the fourth section 720 is connected to the first air intake port 110 and the outlet of the second evaporator 410, and the refrigerant first passes through the third section 710, the second throttling element 400 and the second evaporator 410 in sequence, and then passes through the fourth section 720, and finally enters the first air intake port 110. Fig.12As shown, when the third pipeline 700 is connected to the second air intake port 120, the fourth section 720 is connected to the second air intake port 120 and the outlet of the second evaporator 410, and the refrigerant first passes through the third section 710, the second throttling element 400, and the second evaporator 410 in sequence, and then passes through the fourth section 720, and finally enters the second air intake port 120. Since the refrigerant evaporates in the second evaporator 410, the temperature of the refrigerant in the third section 710 is higher than the temperature of the refrigerant in the fourth section 720.

[0066] The following describes in detail various connection methods of the regenerator 950. Since the temperature of the refrigerant flowing out of the exhaust port 130 is relatively high, the temperature of the refrigerant before and after the first component or the second component is relatively low, it is possible to consider utilizing this temperature difference to fully utilize the heat and cold of the system. Figures 3 to 8 , Figures 12 to 15 , Fig.18 and Fig.19 As shown, in some embodiments, at least one of the second section 620, the fourth section 720 and the fourth pipeline 800 exchanges heat with the first pipeline 500 through the regenerator 950. It should be noted that the temperature of the refrigerant in the first pipeline 500 is relatively high, and the temperature of the refrigerant in the second section 620, the fourth section 720 and the fourth pipeline 800 is relatively low. By exchanging heat through the regenerator 950, the temperature of the refrigerant in the first pipeline 500 can be reduced, and the evaporation temperature of the refrigerant can be reduced, which is beneficial for the subsequent evaporation and heat absorption of the refrigerant in the evaporator, thereby providing more cooling capacity. In addition, the temperature of the refrigerant in the second section 620, the fourth section 720 and the fourth pipeline 800 is increased, reducing the risk of condensation or frost at the first air intake port 110 and the second air intake port 120. Further, referring to Figure 1 and Fig.12 As shown, the first pipeline 500 includes a fifth section 510, and the fifth section 510 is connected to the outlet of the condenser 200. It should be noted that the refrigerant in the fifth section 510 is in liquid state, and the liquid refrigerant has a better heat exchange effect. Specifically, at least one of the second section 620, the fourth section 720 and the fourth pipeline 800 can exchange heat with the fifth section 510 through the heat regenerator 950.

[0067] It can be understood that, since the refrigerant in the second section 620 and the fourth section 720 are both evaporated by the evaporator, the temperature of the refrigerant in the first section 610 is greater than the temperature of the refrigerant in the second section 620 and the fourth section 720, and this temperature difference can be considered to be utilized. Figure 1 , Figure 2 , Fig.16 and Fig.17As shown, in some embodiments, at least one of the second section 620 and the fourth section 720 exchanges heat with the first section 610 through the regenerator 950. It can also be understood that the heat of the refrigerant before freezing and throttling is transferred to the first air inlet 110 or the second air inlet 120. The refrigerant before freezing and throttling can obtain a lower evaporation temperature, improve the cooling capacity, and reduce the risk of condensation or frost at the first air inlet 110 or the second air inlet 120.

[0068] Specifically, refer to Figure 1 As shown, in some embodiments, the first section 610 and the fourth section 720 are connected to the regenerator 950, and the first section 610 and the fourth section 720 exchange heat through the regenerator 950, which can also be understood as the refrigerant at the refrigeration return air and the refrigerant before the freezing throttling heat exchange, which can reduce the temperature of the refrigerant in the first section 610, and can reduce the evaporation temperature of the refrigerant, which is conducive to the evaporation and heat absorption of the refrigerant in the first evaporator 310, and provide a lower refrigeration temperature. In addition, the temperature of the refrigerant in the fourth section 720 can also be increased, reducing the risk of condensation or frost at the first air inlet 110.

[0069] It should be noted that in the test experiment of this embodiment, 65g of R600a is used as the refrigerant, the refrigeration system 1000 is in an environment of 32°C, and the relative humidity of the environment is 75%. The refrigeration system 1000 is specifically arranged in a household refrigerator. The refrigeration system 1000 receives refrigeration and freezing refrigeration requests at the same time. After testing, it is found that: when the above-mentioned regenerator 950 is not set, the average temperature of the refrigerator is 4.2°C, the average temperature of the freezer is -33°C, and the energy consumption test result is 1.05kwh / 24h; when the above-mentioned regenerator 950 is set, the average temperature of the refrigerator is 4.6°C, the average temperature of the freezer is -40.1°C, and the energy consumption test result is 0.99kwh / 24h. Compared with the solution without the above-mentioned regenerator 950, the average temperature of the freezer is reduced by 7.1°C, the energy consumption is also reduced, the deep cooling effect is better, and the energy efficiency is also better.

[0070] Alternatively, in some embodiments, the first section 610 and the second section 620 may be connected to the regenerator 950 , and the first section 610 and the second section 620 may exchange heat through the regenerator 950 .

[0071] Specifically, refer to Figure 2 As shown, it can be Figure 1On the basis of the embodiment of the present invention, a regenerator 950 is added, the fifth section 510 and the fourth pipeline 800 are connected to the regenerator 950, the fifth section 510 and the fourth pipeline 800 exchange heat through the regenerator 950, and the temperature of the refrigerant in the fifth section 510 is greater than the temperature of the refrigerant in the fourth pipeline 800. It can also be understood that the refrigerant before flowing into the second air intake port 120 exchanges heat with the refrigerant at the outlet of the condenser 200. The temperature of the refrigerant in the fifth section 510 can be reduced, the evaporation temperature of the refrigerant can be reduced, which is conducive to the evaporation and heat absorption of the refrigerant in the first evaporator 310 or the second evaporator 410, and provides a lower refrigeration temperature. The temperature of the refrigerant in the fourth pipeline 800 can also be increased, reducing the risk of condensation or frost at the second air intake port 120.

[0072] It should be noted that in the test experiment of this embodiment, 65g of R600a is used as the refrigerant, the refrigeration system 1000 is in an environment of 32°C, and the relative humidity of the environment is 75%. The refrigeration system 1000 is specifically arranged in a household refrigerator. The refrigeration system 1000 receives refrigeration and freezing refrigeration requests at the same time. After testing, it is found that: when the above-mentioned regenerator 950 is not set, the average temperature of the refrigerator is 4.2°C, the average temperature of the freezer is -33°C, and the energy consumption test result is 1.05kwh / 24h; when the above-mentioned regenerator 950 is set, the average temperature of the refrigerator is 4.3°C, the average temperature of the freezer is -40.5°C, and the energy consumption test result is 0.96kwh / 24h. Compared with the solution without the above-mentioned regenerator 950, the average temperature of the freezer is reduced by 7.5°C, the energy consumption is also reduced, the deep cooling effect is better, and the energy efficiency is also better.

[0073] Or, alternatively, refer to Figure 3 As shown, a heat regenerator 950 is separately provided, the fifth section 510 and the fourth pipeline 800 are connected to the heat regenerator 950 , and the fifth section 510 and the fourth pipeline 800 exchange heat through the heat regenerator 950 .

[0074] Specifically, refer to Figure 4As shown, the fifth section 510, the second section 620, the fourth section 720 and the fourth pipeline 800 are connected to the regenerator 950, and the fifth section 510, the second section 620, the fourth section 720 and the fourth pipeline 800 exchange heat through the regenerator 950. It should be noted that the temperature of the refrigerant in the fifth section 510 is relatively high, and the temperature of the refrigerant in the second section 620, the fourth section 720 and the fourth pipeline 800 is relatively low. It can also be understood that the refrigerant at the outlet of the condenser 200 exchanges heat with the refrigerant before the first air intake port 110 and before the second air intake port 120. The temperature of the refrigerant in the fifth section 510 can be reduced, and the evaporation temperature of the refrigerant can be reduced, which is conducive to the evaporation and heat absorption of the refrigerant in the first evaporator 310 or the second evaporator 410, and provides a lower refrigeration temperature. Furthermore, the temperature of the refrigerant in the second section 620 , the fourth section 720 and the fourth pipeline 800 may be increased, thereby reducing the risk of condensation or frost at the first air intake port 110 and the second air intake port 120 .

[0075] It should be noted that in the test experiment of this embodiment, 65g of R600a is used as the refrigerant, the refrigeration system 1000 is in an environment of 32°C, and the relative humidity of the environment is 75%. The refrigeration system 1000 is specifically arranged in a household refrigerator. The refrigeration system 1000 receives refrigeration and freezing refrigeration requests at the same time. After testing, it is found that: when the above-mentioned regenerator 950 is not set, the average temperature of the refrigerator is 4.2°C, the average temperature of the freezer is -33°C, and the energy consumption test result is 1.05kwh / 24h; when the above-mentioned regenerator 950 is set, the average temperature of the refrigerator is 3.7°C, the average temperature of the freezer is -41.4°C, and the energy consumption test result is 0.92kwh / 24h. Compared with the solution without the above-mentioned regenerator 950, the average temperature of the freezer is reduced by 8.4°C, the energy consumption is also reduced, the deep cooling effect is better, and the energy efficiency is also better.

[0076] It can be understood that since the refrigerant in the third section 710 has not passed through the evaporator, the refrigerant in the second section 620 and the fourth section 720 have passed through the evaporator. Therefore, the temperature of the refrigerant in the third section 710 is greater than the temperature of the refrigerant in the second section 620 and the fourth section 720. It can be considered to utilize this part of the temperature difference. Based on this, in some embodiments, at least one of the second section 620 and the fourth section 720 exchanges heat with the third section 710 through the regenerator 950. It can also be understood that the refrigerant before the refrigeration throttling exchanges heat with the refrigerant at the refrigerated return air, or the refrigerant before the refrigeration throttling exchanges heat with the refrigerant at the refrigerated return air. The temperature of the refrigerant in the third section 710 can be reduced to reach a lower evaporation temperature, thereby increasing the cooling capacity. The temperature of the refrigerant in the second section 620 and the fourth section 720 can be increased, thereby reducing the risk of condensation or frost at the first air intake 110 and the second air intake 120. For example, referring to Fig.18As shown, the second section 620 exchanges heat with the third section 710 through the regenerator 950. Alternatively, refer to Fig.21 As shown, the fourth section 720 exchanges heat with the third section 710 via the regenerator 950 .

[0077] It can be understood that, since the refrigerant in the third section 710 does not pass through the second throttling element 400, the refrigerant in the fourth pipeline 800 passes through the third throttling element 940 to complete a throttling, the temperature and pressure of the refrigerant in the fourth pipeline 800 become lower, and therefore, the temperature of the refrigerant in the fourth pipeline 800 is lower than the temperature of the refrigerant in the third section 710. Based on this, referring to Fig. 9 As shown, in some embodiments, the third section 710 exchanges heat with the fourth pipeline 800 through the regenerator 950. It can also be understood that the heat exchange between the refrigerant before refrigeration throttling and the refrigerant at the second air inlet 120 can reduce the temperature of the refrigerant in the third section 710, which is conducive to the evaporation of the refrigerant in the second evaporator 410 and the increase of the cooling capacity, and can increase the temperature of the refrigerant in the fourth pipeline 800 and reduce the risk of condensation or frost at the second air inlet 120.

[0078] It is understandable that, referring to Fig.12 As shown, in some embodiments, the outlet of the third pipeline 700 is communicated with the second air inlet 120, the outlet of the third pipeline 700 is communicated with the outlet of the fourth pipeline 800, the fourth pipeline 800 is provided with a one-way valve 970, the inlet of the one-way valve 970 is communicated with the gas output port 920, and the outlet of the one-way valve 970 is communicated with the second air inlet 120. The refrigerant flowing out of the second evaporator 410 can be prevented from flowing to the gas-liquid separator 900.

[0079] It is understood that in some embodiments, reference Fig.10 , Fig.11 , Fig. 20As shown, the second pipeline 600 includes a sixth section 630, the sixth section 630 is connected to the inlet of the third throttling element 940 and the outlet of the first pipeline 500, and at least one of the second section 620, the fourth section 720 and the fourth pipeline 800 exchanges heat with the sixth section 630 through the regenerator 950. It should be noted that since the refrigerant in the sixth section 630 is not throttled, the temperature of the refrigerant in the sixth section 630 is greater than the temperature of the refrigerant in the second section 620, the fourth section 720 and the fourth pipeline 800. It can also be understood that the refrigerant before entering the third throttling element 940 exchanges heat with the refrigerant before entering the first throttling element 300, or the refrigerant before entering the third throttling element 940 exchanges heat with the refrigerant at the refrigeration return air or the freezing return air. It should be noted that connecting the sixth section 630 to the regenerator 950 will not affect the refrigerant in the third section 710. It can also be understood that it will not affect the refrigerant before flowing into the second throttling element 400. It only reduces the evaporation temperature of the refrigerant before entering the third throttling element 940, thereby ensuring that the temperature of the refrigerator compartment will not be too low while making the temperature of the freezer compartment lower.

[0080] It can be understood that the first throttling element 300, the second throttling element 400 and the third throttling element 940 of the above embodiment can be set as a thermal expansion valve, an electronic expansion valve or a capillary tube, etc., as long as they can achieve a throttling effect, and the heat regenerator 950 can be an attached heat exchanger, a shell and tube heat exchanger or a sleeve heat exchanger, etc.

[0081] It is understandable that a plurality of heat regenerators 950 in the above embodiment can be provided so as to simultaneously realize the above-mentioned various connection modes of the heat regenerators 950, which is not limited here.

[0082] It can be understood that an embodiment of the present invention further provides a refrigeration device, and the refrigeration device includes the refrigeration system 1000 of the above embodiment. Specifically, the refrigeration device can be a freezer, a refrigerator, a refrigerated container, etc. Since the refrigeration device includes the refrigeration system 1000 of the above embodiment, it has the above-mentioned technical effects and will not be repeated here.

[0083] In the description of the present invention, it should be understood that descriptions involving orientations, such as up, down, front, back, inside, outside, etc., indicating orientations or positional relationships, are based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as a limitation on the present invention.

[0084] In the description of the present invention, if there is a description of first or second, it is only for the purpose of distinguishing the technical features, and cannot be understood as indicating or implying the relative importance or implicitly indicating the number of the indicated technical features or implicitly indicating the sequence of the indicated technical features.

[0085] In the description of the present invention, unless otherwise clearly defined, terms such as setting, installing, connecting, etc. should be understood in a broad sense, and technicians in the relevant technical field can reasonably determine the specific meanings of the above terms in the present invention in combination with the specific content of the technical solution.

[0086] The embodiments of the present invention are described in detail above in conjunction with the accompanying drawings. Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that the technical solutions described in the aforementioned embodiments can still be modified, or some or all of the technical features therein can be replaced by equivalents. However, these modifications or replacements do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present invention.

Claims

1. A refrigeration system, characterized in that: include: A double suction compressor is provided with a first suction port, a second suction port and an exhaust port; a first pipeline, wherein an inlet of the first pipeline is connected to the exhaust port; a second pipeline, wherein an inlet of the second pipeline is connected to an outlet of the first pipeline, and an outlet of the second pipeline is connected to the first air inlet; a third pipeline, wherein the inlet of the third pipeline is connected to the outlet of the first pipeline, and the outlet of the third pipeline is connected to the first air inlet or the second air inlet; A condenser, arranged in the first pipeline; a first component, arranged in the second pipeline, the first component comprising a first throttling element and a first evaporator, the outlet of the first throttling element being in communication with the inlet of the first evaporator; a second component, disposed in the third pipeline, the second component comprising a second throttling element and a second evaporator, the outlet of the second throttling element being in communication with the inlet of the second evaporator; a third component, arranged in the second pipeline, comprising a gas-liquid separator and a third throttling element, the gas-liquid separator having an input port, a gas output port and a liquid output port, the outlet of the third throttling element being in communication with the input port, and the liquid output port being in communication with the inlet of the first throttling element; a fourth pipeline, wherein the inlet of the fourth pipeline is connected to the gas output port, and the outlet of the fourth pipeline is connected to the second air intake port; The regenerator is used to transfer the heat of the refrigerant flowing out of the exhaust port to at least one of the first air intake port and the second air intake port.

2. The refrigeration system according to claim 1, characterized in that: The second pipeline includes a first section and a second section, the first section is connected to the inlet of the first throttling element, and the second section is connected to the outlet of the first evaporator. The third pipeline includes a third section and a fourth section, the third section is connected to the inlet of the second throttling element, and the fourth section is connected to the outlet of the second evaporator.

3. The refrigeration system according to claim 2, characterized in that: At least one of the second section and the fourth section exchanges heat with the first section through the regenerator.

4. The refrigeration system according to claim 2, characterized in that: At least one of the second section and the fourth section exchanges heat with the third section through the regenerator.

5. The refrigeration system according to claim 2, characterized in that: The third section exchanges heat with the fourth pipeline through the heat regenerator.

6. The refrigeration system according to claim 2, characterized in that: At least one of the second section, the fourth section and the fourth pipeline exchanges heat with the first pipeline through the heat regenerator.

7. The refrigeration system according to claim 6, characterized in that: The first pipeline includes a fifth section, the fifth section is connected to the outlet of the condenser, and at least one of the second section, the fourth section and the fourth pipeline exchanges heat with the fifth section through the regenerator.

8. The refrigeration system according to claim 2, characterized in that: The second pipeline includes a sixth section, the sixth section is connected to the inlet of the third throttling element, and at least one of the second section, the fourth section and the fourth pipeline exchanges heat with the sixth section through the regenerator.

9. The refrigeration system according to claim 1, characterized in that: The outlet of the third pipeline is communicated with the second air intake port, the outlet of the third pipeline is communicated with the outlet of the fourth pipeline, the fourth pipeline is provided with a one-way valve, the inlet of the one-way valve is communicated with the gaseous output port, and the outlet of the one-way valve is communicated with the second air intake port.

10. The refrigeration system according to claim 1, characterized in that: The first pipeline is provided with a control valve, and the control valve connects the second pipeline and the third pipeline to control the refrigerant flow from the first pipeline to the second pipeline or the third pipeline.

11. The refrigeration system according to claim 1, characterized in that: The first evaporator is a freezing chamber evaporator, and the second evaporator is a refrigerating chamber evaporator.

12. Refrigeration equipment, characterized in that Comprising a refrigeration system as claimed in any one of claims 1 to 11.

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