Refrigerating system and refrigerating method thereof

Abstract

The invention discloses a refrigerating system and a refrigerating method thereof. In the refrigerating system, a compressor is used for mixing and boosting a first gaseous refrigerant sucked through a first air suction port and a second gaseous refrigerant sucked through a second air suction port to obtain a third gaseous refrigerant. The input end of the condenser is connected with an exhaust port of the compressor, and the input end of the filter is connected with the output end of the condenser. The input port of the flow divider is connected with the output end of the filter. The flow divider is used for evenly dividing the second liquid refrigerant and then flowing the second liquid refrigerant into the first capillary tube and the second capillary tube. The first evaporator is used for exchanging heat with the refrigerating chamber so that the first gas-liquid two-phase refrigerant flowing out of the second capillary tube can be converted into a first gas-state refrigerant. The second evaporator is used for exchanging heat with the freezing chamber so as to evaporate, absorb heat and refrigerate the second gas-liquid two-phase refrigerant flowing out of the second capillary tube to obtain a second gas-state refrigerant, the effect of refrigerating the refrigerating chamber and the freezing chamber in the refrigerating system at the same time is achieved, the energy consumption of the system is reduced, and the food fresh-keeping effect is good.

Description

Technical Field

[0001] The present invention relates to the field of refrigeration technology, and in particular to a refrigeration system and a refrigeration method thereof. Background Art

[0002] The dual-system low-temperature refrigeration cycle system uses two independent refrigeration cycle systems to accurately control the temperature of the refrigerator and freezer compartments. The two systems are designed to be closed to ensure that the air in the refrigerator compartment does not enter the freezer compartment, and vice versa. In the refrigerator compartment, the system can achieve an 80% moisture retention rate, effectively lock in the moisture of the food and achieve "active freshness". In the freezer compartment, the system locks in the freshness of the food through rapid refrigeration to maintain nutrition.

[0003] In the current dual-system low-temperature refrigeration cycle system, the refrigeration compartment and the freezer compartment are refrigerated alternately and separately. This refrigeration method has some defects in terms of system energy saving and food preservation. Specifically, in terms of system energy saving, alternating refrigeration means that only one compartment is working at a time, while the other compartment is idle, which will lead to a decrease in the efficiency of the entire refrigeration system. When the refrigeration compartment or the freezer compartment does not need refrigeration, if the system is still running, it will waste energy. In addition, in terms of food preservation, alternating refrigeration may cause large temperature fluctuations in the refrigeration compartment and the freezer compartment. Because only one compartment is working at a time, when switching to another compartment, it takes some time to reach the set temperature. This temperature fluctuation may affect the preservation effect of food, especially for some temperature-sensitive foods, such as high-end fresh food, fresh cut flowers, etc. Large temperature fluctuations will also accelerate the spoilage process of food, shorten the shelf life of food, and may also cause changes in the taste of food, making the food no longer delicious. Summary of the invention

[0004] In view of this, the present invention aims to solve one of the problems in the related art at least to a certain extent. To this end, an object of the present invention is to provide a refrigeration system and a refrigeration method thereof.

[0005] The present application provides a refrigeration system. The refrigeration system includes a first evaporator, a cold storage compartment, a second evaporator, a freezing compartment, a compressor, a condenser, a filter, a diverter, a first capillary tube, and a second capillary tube. The compressor includes a first air intake port and a second air intake port, the first air intake port is connected to the output end of the first evaporator, and the second air intake port is connected to the output end of the second evaporator; the compressor is used to mix and boost the first gaseous refrigerant sucked in through the first air intake port and the second gaseous refrigerant sucked in through the second air intake port to obtain a third gaseous refrigerant; the input end of the condenser is connected to the exhaust port of the compressor, the condenser is used to receive the third gaseous refrigerant and exchange heat with the outside to convert the third gaseous refrigerant into a first liquid refrigerant; the input end of the filter is connected to the output end of the condenser, the filter is used to dry and filter the first liquid refrigerant to obtain a second liquid refrigerant; the diverter includes a first output port and a second output port, the input port of the diverter is connected to the output end of the filter, the The flow divider is used to evenly divide the second liquid refrigerant and output it from the first output port and the second output port; the input end of the first capillary tube is connected to the first output port, and the first capillary tube is used for throttling and reducing the pressure of the second liquid refrigerant, which is a first gas-liquid two-phase refrigerant; the output end of the first capillary tube is connected to the input end of the first evaporator, and the first evaporator is used for heat exchange with the refrigerated compartment to convert the first gas-liquid two-phase refrigerant into the first gaseous refrigerant; the input end of the second capillary tube is connected to the second output port, and the second capillary tube is used for throttling and reducing the pressure of the second liquid refrigerant, which is a second gas-liquid two-phase refrigerant; the output end of the second capillary tube is connected to the input end of the second evaporator, and the second evaporator is used for heat exchange with the freezing compartment to evaporate the second gas-liquid two-phase refrigerant to absorb heat and cool it to obtain the second gaseous refrigerant.

[0006] In certain embodiments, the compressor includes a compression cylinder body, an exhaust pipe, a first intake pipe, and a second intake pipe. A piston compression cylinder is provided in the compression cylinder body. The first intake pipe is provided with a first welding port and the first intake port, and the first welding port is welded to the outer wall of the compression cylinder body; the second intake pipe is provided with a second welding port and the second intake port, and the second welding port is welded to the outer wall of the compression cylinder body; the exhaust pipe is provided with a third welding port and the exhaust port, and the third welding port is welded to the outer wall of the compression cylinder body.

[0007] In some embodiments, the compressor further includes a process pipe, the process pipe is provided with a fourth welding port and a process port, the fourth welding port is welded to the outer wall of the compression cylinder, and the process port is used to inject gaseous refrigerant into the compression cylinder.

[0008] In some embodiments, the refrigeration system also includes a first return air pipe and a second return air pipe, the first return air pipe is connected to the first air intake port, the second return air pipe is connected to the second air intake port, the first return air pipe connects the compressor and the first evaporator, and the second return air pipe connects the compressor and the second evaporator.

[0009] In some embodiments, the refrigeration system further includes a controller and a switch valve, wherein the controller is electrically connected to the switch valve, the switch valve is located on the pipeline between the first capillary tube and the diverter, and the controller is used to control the closing and opening of the switch valve.

[0010] In certain embodiments, the refrigeration system further comprises a refrigerating fan and a freezing fan, wherein the refrigerating fan is used to drive the air in the refrigerating compartment to pass through the first evaporator; and the freezing fan is used to drive the air in the freezing compartment to pass through the second evaporator.

[0011] In some embodiments, the flow divider includes a body and a valve core. The body is provided with a jet channel and a shunt channel, the first end of the jet channel extends to the outer surface of the body and forms the input port; there are multiple shunt channels, the first ends of the multiple shunt channels are all connected to the second end of the jet channel, the second ends of the multiple shunt channels extend to the outer surface of the body and form multiple output ports; the valve core is arranged between the jet channel and the shunt channel in the body, the valve core is provided with a throttling channel, the diameter of the throttling channel is smaller than the diameter of the jet channel; wherein the diameter of the throttling channel is less than or equal to 0.7 mm.

[0012] The present application also provides a refrigeration method, which is applied to the refrigeration system described in any one of the above embodiments. The refrigeration method includes: controlling the injection of gaseous refrigerant into the compressor, so that the gaseous refrigerant is cooled by the condenser and converted into liquid refrigerant, and the liquid refrigerant flows into the first evaporator and the second evaporator respectively after being evenly diverted by the diverter; controlling the refrigeration fan and the freezing fan to start working at the same time, so that the first evaporator and the second evaporator respectively exchange heat with the cold storage room and the freezing room at the same time, so as to reduce the temperature of the cold storage room and the freezing room at the same time; wherein, the first gaseous refrigerant output by the first evaporator flows back to the compressor through the first return air pipe to form a first refrigeration cycle, and the second gaseous refrigerant output by the second evaporator flows back to the compressor through the second return air pipe to form a second refrigeration cycle.

[0013] In certain embodiments, the refrigeration method includes: detecting the temperature of the refrigerating compartment; and controlling the switch valve to close when the temperature of the refrigerating compartment is less than or equal to a first temperature threshold.

[0014] In some embodiments, the refrigeration method includes: detecting the temperature of the freezing chamber; and controlling the compressor to stop working when the temperature of the freezing chamber is less than or equal to a second temperature threshold.

[0015] In this way, the refrigeration system of the present application can achieve the simultaneous refrigeration effect of the refrigerating compartment and the freezing compartment, saving the energy consumption of the refrigerating system, and the temperature fluctuation of the refrigerating compartment and the freezing compartment is small, and the food in the refrigerating compartment and the freezing compartment is better kept fresh.

[0016] 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

[0017] The above and / or additional aspects and advantages of the present invention will become apparent and easily understood from the following description of the embodiments in conjunction with the accompanying drawings, in which:

[0018] Figure 1 is a schematic diagram of a refrigeration system according to some embodiments of the present application;

[0019] Figure 2 is a schematic diagram of the structure of a compressor in a refrigeration system in certain embodiments of the present application;

[0020] Figure 3 is a schematic diagram of the structure of a flow divider in a refrigeration system in certain embodiments of the present application;

[0021] Figure 4 yes Figure 3 The schematic cross-section diagram along line AA;

[0022] Figure 5 is a schematic diagram of the structure of a flow divider in a refrigeration system in certain embodiments of the present application;

[0023] Figure 6 is a schematic diagram of the relationship between the diameter of the throttling channel and the liquid refrigerant split flow ratio in the splitter of certain embodiments of the present application;

[0024] Figure 7 Schematic diagram of the relationship between the diameter of the first section of the flow channel of the diverter and the diverted flow ratio of the liquid refrigerant in some embodiments of the present application;

[0025] Figure 8 is a schematic flow chart of a refrigeration method according to certain embodiments of the present application;

[0026] Fig. 9 is a schematic flow chart of a refrigeration method according to certain embodiments of the present application;

[0027] Fig.10 It is a schematic flow chart of a refrigeration method according to certain embodiments of the present application.

[0028] Main component reference numbers:

[0029] Refrigeration system 1000;

[0030] The first evaporator 100, the refrigerating compartment 200, the second evaporator 300, the freezing compartment 400, the compressor 500, the compression cylinder 510, the exhaust pipe 520, the first air intake pipe 530, the second air intake pipe 540, the process pipe 550, the condenser 600, the filter 700, the diverter 800, the body 810, the jet channel 811, the input port 8111, the plane portion 8112, the conical portion 8113, the diverter channel 812, the output port 8121, the first section flow channel 8122, the second section flow channel 8123, the valve core 820, the throttling channel 821, the first capillary tube 910, the second capillary tube 920, the first return air pipe 930, the second return air pipe 940, the switch valve 950, the refrigerating fan 960, and the freezing fan 970. DETAILED DESCRIPTION

[0031] The 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.

[0032] In the description of the present invention, the terms "first" and "second" are used for descriptive purposes only and cannot be understood as indicating or implying relative importance, or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, the meaning of "plurality" is two or more, unless otherwise clearly and specifically defined.

[0033] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installation" and "connection" should be understood in a broad sense, and may refer to fixed connection, detachable connection, or integral connection; mechanical connection, electrical connection, or mutual communication; direct connection, indirect connection through an intermediate medium, internal connection between two elements, or interaction between two elements. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0034] The disclosure below provides many different embodiments or examples to implement different structures of the present invention. In order to simplify the disclosure of the present invention, the parts and settings of specific examples are described below. Of course, they are only examples, and the purpose is not to limit the present invention. In addition, the present invention can repeat reference numbers and / or reference letters in different examples, and this repetition is for the purpose of simplification and clarity, which itself does not indicate the relationship between the various embodiments and / or settings discussed.

[0035] The 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.

[0036] See also Figure 1 The present application provides a refrigeration system 1000 . The refrigeration system 1000 includes: a first evaporator 100 , a refrigerating compartment 200 , a second evaporator 300 , a freezing compartment 400 , a compressor 500 , a condenser 600 , a filter 700 , a flow divider 800 , a first capillary tube 910 , and a second capillary tube 920 .

[0037] The first evaporator 100 is a refrigerating evaporator, and the second evaporator 300 is a freezing evaporator. The working principles of the refrigerating evaporator and the freezing evaporator are both based on the vaporization heat absorption principle of the refrigerant. In detail, when the refrigerant liquid vaporizes in the first evaporator 100, it absorbs the heat of the refrigerating compartment 200, so that the temperature of the refrigerating compartment 200 is reduced, thereby achieving the purpose of refrigerating the refrigerating compartment 200. At the same time, when the refrigerant liquid vaporizes in the second evaporator 300, it absorbs the heat of the freezing compartment 400, so that the temperature of the freezing compartment 400 is reduced, thereby achieving the purpose of refrigerating the freezing compartment 400.

[0038] The compressor 500 includes a first air intake port and a second air intake port. The first air intake port is connected to the output end of the first evaporator 100, and the second air intake port is connected to the output end of the second evaporator 300. The compressor 500 is used to mix and increase the pressure of the first gaseous refrigerant sucked through the first air intake port and the second gaseous refrigerant sucked through the second air intake port to obtain a third gaseous refrigerant.

[0039] Among them, the first gaseous refrigerant can be a medium-pressure gaseous refrigerant, and the second gaseous refrigerant can be a low-pressure gaseous refrigerant. That is to say, the medium-pressure gaseous refrigerant coming out of the first evaporator 100 is input into the compression cylinder of the compressor 500, and the low-pressure gaseous refrigerant coming out of the second evaporator 300 is input into the compression cylinder of the compressor 500. After the medium-pressure gaseous refrigerant and the low-pressure gaseous refrigerant are mixed, the low pressure of the overall refrigeration system 1000 is increased, which reduces the compression ratio of the refrigeration system 1000, thereby reducing the power of the refrigeration system 1000.

[0040] The compressor 500 in the refrigeration system 1000 of the present application is a double-suction compressor, which can simultaneously suck two gaseous refrigerants in different pressure states output from the first evaporator 100 and the second evaporator 300 into the cylinder of the compressor 500 through two air intake ports, thereby achieving the simultaneous refrigeration of the refrigeration compartment 200 and the freezing compartment 400 in the refrigeration system 1000, saving energy consumption of the refrigeration system 1000, and the temperature fluctuation of the refrigeration compartment 200 and the freezing compartment 400 is small, and the food in the refrigeration compartment 200 and the freezing compartment 400 is better kept fresh.

[0041] The input end of the condenser 600 is connected to the exhaust port 503 of the compressor 500. The condenser 600 is used to receive the third gaseous refrigerant and exchange heat with the outside to convert the third gaseous refrigerant into the first liquid refrigerant. There are many types of condensers 600, such as air-cooled condensers, water-cooled condensers, etc. Different types of condensers 600 are different in structure and heat dissipation method, but the basic principle is to use pipes and fins to dissipate the heat in the gas into the air or water, and cool the high-temperature and high-pressure gas through the pipes and fins and convert it into a medium-temperature and high-pressure liquid.

[0042] The input end of the filter 700 is connected to the output end of the condenser 600. The filter 600 is used to dry and filter the first liquid refrigerant to obtain the second liquid refrigerant.

[0043] The diverter 800 includes a first output port and a second output port. The input port of the diverter 800 is connected to the output end of the filter 700, and the diverter 800 is used to evenly divide the second liquid refrigerant and output it from the first output port and the second output port. That is, the refrigeration system 1000 of the present application can be provided with a diverter 800 between the filter 700 and the first capillary tube 910 and the second capillary tube 920 to evenly divide the second liquid refrigerant flowing out of the condenser 600, thereby avoiding the problem that the second liquid refrigerant is unevenly divided, resulting in the first evaporator 100 or the second evaporator 300 lacking liquid, thereby causing the refrigeration capacity to decay, so that the refrigeration and freezing effects of the refrigerator are better.

[0044] It is understandable that the lack of liquid in the evaporator reduces the absorption of heat and lowers the heat exchange efficiency, which will directly lead to the attenuation of the refrigerator's refrigeration capacity. The attenuation of the refrigerator's refrigeration capacity is manifested as an increase in the temperature inside the refrigerator, which weakens the refrigerator's refrigeration and freezing effects. Therefore, the refrigeration system 1000 of the present application can avoid the problem of refrigeration capacity attenuation caused by uneven distribution of the second liquid refrigerant by setting a splitter 800 to evenly distribute the second liquid refrigerant flowing out of the condenser 600, thereby achieving better refrigeration and freezing effects of the refrigerator.

[0045] The input end of the first capillary tube 910 is connected to the first output port, and the first capillary tube 910 is used to throttle and reduce the pressure of the second liquid refrigerant to be the first gas-liquid two-phase refrigerant. The output end of the first capillary tube 910 is connected to the input end of the first evaporator 100, and the first evaporator 100 is used to exchange heat with the refrigerated compartment 200 to convert the first gas-liquid two-phase refrigerant into the first gaseous refrigerant.

[0046] The input end of the second capillary tube 920 is connected to the second output port, and the second capillary tube 920 is used to throttle and depressurize the second liquid refrigerant to be a second gas-liquid two-phase refrigerant. The output end of the second capillary tube 920 is connected to the input end of the second evaporator 300, and the second evaporator 300 is used to exchange heat with the freezing chamber 400 to evaporate the second gas-liquid two-phase refrigerant to absorb heat and refrigerate to obtain a second gaseous refrigerant.

[0047] In this way, the refrigeration system 1000 of the present application can achieve the simultaneous refrigeration effect of the refrigerating compartment 200 and the freezing compartment 400 in the refrigerating system 1000, saving the energy consumption of the refrigerating system 1000, and the temperature fluctuation of the refrigerating compartment 200 and the freezing compartment 400 is small, and the food in the refrigerating compartment 200 and the freezing compartment 400 is better kept fresh.

[0048] See also Figure 2 In some embodiments, the compressor 500 includes a compression cylinder 510, an exhaust pipe 520, a first intake pipe 530, and a second intake pipe 540. A piston compression cylinder is provided in the compression cylinder 510. The exhaust pipe 520 is provided with a third welding port and an exhaust port, and the third welding port is welded to the outer wall of the compression cylinder 510.

[0049] The first air intake pipe 530 is provided with a first welding port and a first air intake port, and the first welding port is welded to the outer wall of the compression cylinder 510. The second air intake pipe 540 is provided with a second welding port and a second air intake port, and the second welding port is welded to the outer wall of the compression cylinder 510.

[0050] In this way, the compressor 500 of the present application can simultaneously inhale the first gaseous refrigerant of the first evaporator 100 and the second gaseous refrigerant of the second evaporator 300 through the first suction pipe 530 and the second suction pipe 540, thereby achieving simultaneous refrigeration of the refrigerating compartment 200 and the freezing compartment 400 of the refrigeration system 1000.

[0051] See also Figure 2 The compressor 500 further includes a process pipe 550. The process pipe 550 is provided with a fourth welding port and a process port. The fourth welding port is welded to the outer wall of the compression cylinder 510. The process port is used to inject gaseous refrigerant into the compression cylinder 510.

[0052] Specifically, the main function of the process pipe 550 in the double suction compressor is to provide an interface for performing specific process operations, such as charging refrigerant, detecting the internal pressure of the compressor 500, and exhausting the internal air. These operations are usually performed during the installation, commissioning, repair or maintenance of the compressor, and are not functions of the compressor during normal operation. Therefore, the function of the process pipe 250 in the double suction compressor is to provide an interface for specific process operations, which can ensure that the compressor can conveniently perform necessary operations during the installation, commissioning, repair or maintenance process.

[0053] See also Figure 1 The refrigeration system 1000 further includes a first air return pipe 930 and a second air return pipe 940. The first air return pipe 930 is connected to the first air intake port, and the second air return pipe 940 is connected to the second air intake port. The first air return pipe 930 is connected to the compressor 500 and the first evaporator 100, and the second air return pipe 940 is connected to the compressor 500 and the second evaporator 300.

[0054] That is, the refrigeration system 1000 of the present application can connect the first evaporator 100 and the compressor 500 through the first return air pipe 930, and recover the first gaseous refrigerant output from the first evaporator 100 to the compressor 500, and connect the second evaporator 300 and the compressor 500 through the second return air pipe 940, and recover the second gaseous refrigerant output from the second evaporator 300 to the compressor 200.

[0055] The refrigeration system 1000 further includes a controller and a switch valve 950. The controller is electrically connected to the switch valve 950, and the switch valve 950 is located on the pipeline between the first capillary tube 910 and the diverter 800. The controller is used to control the closing and opening of the switch valve 950.

[0056] Specifically, the switch valve 950 is provided with two interfaces and wiring terminals, and the wiring terminals are connected to the controller of the refrigeration system 1000 . The controller can control the two interfaces of the switch valve 950 to be connected or cut off, thereby controlling the closing and opening of the switch valve 950 .

[0057] The refrigeration system 1000 further includes a refrigerating fan 960 and a freezing fan 970. The refrigerating fan 960 is used to drive the air in the refrigerating compartment 200 to pass through the first evaporator 100. The refrigerating fan 960 is provided with a connection terminal and a fan blade, and the connection terminal is connected to a controller, and the controller can control the start and stop and the speed of the refrigerating fan 960. After the fan blade rotates, the air in the refrigerating compartment 200 of the refrigerator passes through the first evaporator 100 at a certain speed to form forced convection heat exchange, thereby blowing the coldness of the first evaporator 100 into the refrigerating compartment 200 of the refrigerator. The refrigerating fan 960 can be arranged in the refrigerating compartment 200.

[0058] The refrigeration fan 970 is used to drive the air in the freezing compartment 400 to pass through the second evaporator 300. The refrigeration fan 970 is provided with a connection terminal and a fan blade, and the connection terminal is connected to the controller. The controller can control the start and stop and the speed of the refrigeration fan 970. After the fan blade rotates, the air in the freezing compartment 400 of the refrigerator passes through the second evaporator 300 at a certain speed to form forced convection heat exchange, and the cold energy of the second evaporator 300 can be blown into the freezing compartment 400 of the refrigerator. The refrigeration fan 970 can be arranged in the freezing compartment 400.

[0059] Please also read Figures 3 to 5 The flow divider 800 includes a body 810 and a valve core 820 .

[0060] The body 810 is provided with a jet channel 811 and a shunt channel 812. The first end of the jet channel 811 extends to the outer surface of the body 810 and forms an input port 8111. There are multiple shunt channels 812, and the first ends of the multiple shunt channels 812 are all connected to the second end of the jet channel 811, and the second ends of the multiple shunt channels 812 extend to the outer surface of the body 810 and form multiple output ports 8121.

[0061] The valve core 820 is disposed between the jet channel 811 and the diversion channel 812 in the body 810. A throttling channel 821 is disposed in the valve core 820. The diameter d2 of the throttling channel 821 is smaller than the diameter d1 of the jet channel 811. The diameter d2 of the throttling channel 821 is less than or equal to 0.7 mm.

[0062] It is understandable that since a valve core 820 is provided between the jet channel 811 and the diverter channel 812 inside the diverter 800, and a throttling channel 821 is provided inside the valve core 820, the diameter d2 of the throttling channel 821 is smaller than the diameter d1 of the jet channel 811. When the liquid passes through the throttling channel 821, since the diameter d2 of the throttling channel 821 is smaller than the diameter d1 of the jet channel 811, there will be a pressure difference between the jet channel 811 and the throttling channel 821. According to Bernoulli's principle, in an incompressible, inviscid ideal fluid, the flow rate of the fluid is inversely proportional to the pressure. Therefore, when the liquid flows through the narrow area of ​​the throttling channel 821, in order to maintain the flow continuity, the flow rate must increase to compensate for the reduction in cross-sectional area. In this way, the diverter 800 of the present application can increase the flow rate of the liquid refrigerant after passing through the throttling channel 821, thereby reducing the influence of the gravity of the liquid refrigerant, allowing the liquid refrigerant to be output stably, and facilitating uniform diversion of the liquid refrigerant.

[0063] like Figure 2 As shown, the jet channel 811 can be divided into two sections, the first section is a cylindrical channel, and the second section is a conical channel, and the diameters of the two sections are greater than the diameter of the throttling channel 821. In addition, the jet channel 811 can also be only one section of a cylindrical channel, which is not limited here.

[0064] That is, when the diverter 800 of the present application is used in a dual-system low-temperature refrigeration cycle system, the liquid refrigerant can increase its flow rate after flowing from the jet channel 811 of the diverter 800 through the throttling channel 821, thereby reducing the influence of the gravity of the liquid refrigerant, and stably distributing the liquid refrigerant to the first evaporator 100 and the second evaporator 300 in the refrigeration system 1000, thereby avoiding the problem of uneven distribution of the second liquid refrigerant, resulting in lack of liquid in the first evaporator 100 or the second evaporator 300, thereby causing a decrease in cooling capacity, thereby improving the refrigeration and freezing effects of the refrigerator.

[0065] In certain embodiments, the diameter d2 of the throttling channel 821 is less than or equal to 0.7 mm, and the length L of the throttling channel 821 is greater than or equal to 4 mm.

[0066] The diameter d2 of the throttling channel 821 is ≤ 0.7 mm, that is, the maximum diameter of the throttling channel 821 of the present application can be designed to be 0.7 mm, thereby limiting the flow rate of the liquid flowing into the throttling channel 821 and increasing the flow rate of the liquid flowing out of the throttling channel 821.

[0067] It is understandable that when the liquid flows through the throttling channel 821 with a diameter less than or equal to 0.7 mm, the flow rate of the liquid will increase, because the flow rate (volume / time) requires a higher speed to maintain when the orifice area is reduced. This increase in flow rate helps to reduce the influence of liquid gravity, because a faster flow rate means that the liquid is more difficult to accumulate or stagnate due to gravity. Therefore, the smaller the diameter d2 of the throttling channel 821, the faster the flow rate, which is more conducive to reducing the influence of liquid gravity.

[0068] Also, see Figure 6 When the diameter d2 of the throttling channel 821 is greater than 0.7 mm, the split flow ratio of the liquid refrigerant is less than 90%. A liquid refrigerant split flow ratio of less than 90% means that part of the refrigerant is not evenly distributed to each evaporator. This may lead to inconsistent refrigeration effects in the evaporator, with some areas having good refrigeration effects and some areas having insufficient refrigeration. This uneven refrigeration effect will reduce the overall performance of the refrigeration system 1000. In other words, a liquid refrigerant split flow ratio of less than 90% means that part of the refrigerant fails to fully participate in the refrigeration cycle. This will cause the refrigeration effect of the refrigeration system 1000 to decrease, and the expected cooling effect cannot be met.

[0069] Therefore, the present application sets the maximum diameter d2 of the throttling channel 821 to 0.7 mm, which can ensure that almost all of the liquid can pass through the throttling channel 821 and the flow rate through the throttling channel 821 is faster.

[0070] In addition, it can be understood that the increase in flow rate helps the liquid to pass through the throttling channel 821 more quickly and reduces the accumulation or stagnation inside the diverter 800, thereby improving the uniformity of liquid distribution. Therefore, the throttling channel with a diameter less than or equal to 0.7 mm also helps to more accurately control the distribution of the liquid and ensure that the liquid is evenly distributed between the two diverting channels.

[0071] Secondly, the design of the length L2 ≥ 4 mm of the throttling channel 821 has an important influence on the pressure drop of the liquid. When the liquid flows through the throttling channel 821, the pressure of the liquid will decrease due to the increase in flow resistance. The longer throttling channel 821 can provide a larger flow resistance area, thereby increasing the pressure drop. This pressure drop helps to further reduce the flow rate and flow rate of the liquid, and also helps to stabilize the flow state of the liquid.

[0072] See also Figure 2 In some embodiments, the length of the jet channel 811 is greater than or equal to 6 mm.

[0073] It can be understood that, since the first end of the jet channel 811 is the liquid inlet 8111, and the second end 11 of the jet channel 811 passes through the throttling channel 821 of the valve core 820, the docking length of the jet channel 811 and the external pipe can be increased with the length of the jet channel 811, and the length of the jet channel 811 is greater than or equal to 6 mm. Therefore, the matching length L of the jet channel 811 of the present application and the external liquid inlet pipe can be greater than or equal to 6 mm, so that the matching of the liquid inlet pipe and the jet channel 811 is more stable. Therefore, the longer the length of the jet channel 811, the more stable the docking of the jet channel 811 with the external pipe is, and the stability of the liquid flowing into the diverter 800 is improved.

[0074] That is, the length of the jet channel is crucial to the stability of the liquid flowing into the diverter. A longer channel can provide a more stable fluid flow and reduce flow fluctuations caused by fluid disturbances or external interference.

[0075] In addition, from a manufacturing perspective, a length of 6 mm is a size that is relatively easy to process and control, and it does not bring excessive complexity or cost increases to the manufacturing process. At the same time, a length of 6 mm is also convenient for installation and connection with other piping systems. Although a shorter jet channel 811 may be easier to process in manufacturing, an overly short length of the jet channel 811 may cause difficulties in installation and connection with other piping systems.

[0076] The present application sets the length of the jet channel 811 to be greater than or equal to 6 mm. The longer jet channel 811 can provide more stable fluid flow, reduce flow fluctuations caused by fluid disturbances or external interference, and facilitate installation and connection with other piping systems.

[0077] See also Figure 2 In some embodiments, the center line P2 of the diversion channel 812 is arranged at a preset angle α with the center line P1 of the jet channel 811. Specifically, the preset angle α can be, for example, 20°, 23°, 25°, 28°, 29°, 30°, 32°, 37°, 45° or 50°, which is not limited here.

[0078] That is, the angle between the center line P2 of the diverter channel 812 and the center line P1 of the jet channel 811 of the present application can be freely changed according to the different diverter directions, meeting the demand for diverting the liquid through the diverter channels 812 in different directions. The angles between the center lines of the multiple diverter channels 812 and the center line of the jet channel 811 can be the same or different, and there is no limitation here.

[0079] See also Figure 2 and Figure 3 In some embodiments, a plurality of output ports 8121 are spaced apart along the circumference of the body 810 .

[0080] Specifically, the distances between the multiple output ports 8121 can be the same or different, and there is no limitation here. Figure 3 As shown, the diverter 800 of the present application may be provided with two diverter channels 812 , correspondingly provided with two output ports 8121 , and the two output ports 8121 are arranged at intervals along the circumference of the body 810 .

[0081] That is, the multiple liquid outlets formed by the multiple diverter channels 812 of the present application on the main body 810 can be arranged at intervals along the circumference of the main body 810, so that the overall structure of the diverter 800 of the present application is more compact.

[0082] See also Figure 2 and Figure 3 In some embodiments, the plurality of outlets 8121 are symmetrically arranged along the central axis of the body 810. That is, at this time, the distances between the plurality of outlets 8121 can be the same, and the plurality of liquid outlets are symmetrically arranged along the central axis of the body 810, which makes the overall structure of the diverter 800 of the present application compact and more beautiful.

[0083] See also Figure 2 In some embodiments, the flow diversion channel 812 includes a first flow channel 8122 and a second flow channel 8123 connected to each other. The first flow channel 8122 is located at the first end of the flow diversion channel 812, and the second flow channel 8123 is located at the second end of the flow diversion channel 812. A step surface is formed between the first flow channel 8122 and the second flow channel 8123. The second flow channel 8123 cooperates with an external pipeline, and the diameter d3 of the first flow channel 8122 is smaller than the diameter d4 of the second flow channel 8123.

[0084] It can be understood that the present application can more effectively control the flow and distribution of liquid by designing the shunt channel 812 into two sections of different sizes. The second section of the flow channel 8123 with a larger diameter can accommodate more liquid and play a role of buffering and storage to a certain extent, while the first section of the flow channel 8122 with a smaller diameter can adjust the flow more finely. This design helps to ensure that the liquid can be evenly and stably distributed to each liquid outlet during the shunt process, avoiding performance problems caused by excessive or insufficient flow.

[0085] In addition, during the flow of liquid, vortex and backflow are common flow problems, which can lead to energy loss and flow instability. By designing the diverter channel 812 into two sections of different sizes, the occurrence of vortex and backflow can be effectively reduced.

[0086] See also Figure 2In some embodiments, the diameter d3 of the first section of the flow channel 8122 is greater than the diameter d2 of the throttling channel 821, and the diameter d3 of the first section of the flow channel 8122 is less than or equal to 1.8 mm.

[0087] It can be understood that since the diameter d3 of the first section of the flow channel 8122 is larger than the diameter d2 of the throttling channel 821, and the diameter d2 of the throttling channel 821 is smaller than the diameter d1 of the jet channel 811, the throttling channel 821 is between the jet channel 811 and the diversion channel 812, which is equivalent to forming a "bottleneck" in the diverter 800. Due to the pressure difference before and after the throttling channel 821, the pressure of the liquid behind the throttling channel 821 is lower, which also helps to accelerate the flow of the liquid.

[0088] The diameter d3 of the first section of the flow channel 8122 is less than or equal to 1.8 mm. The first section of the flow channel 8122 has a smaller flow channel diameter, which helps to achieve a more uniform flow of liquid and reduce the residence time of the liquid in the first section of the flow channel 8122. The liquid can pass through the first section of the flow channel 8122 more quickly, reducing accumulation or stagnation inside the first section of the flow channel 8122 and improving the uniformity of liquid distribution.

[0089] Also, see Figure 7 , when the diameter d3 of the first section of the flow channel 8122 is greater than 1.8 mm, the diversion flow ratio of the liquid refrigerant is less than 90%. The diversion flow ratio of the liquid refrigerant is less than 90%, which means that part of the refrigerant is not evenly distributed to each evaporator. This may lead to inconsistent refrigeration effects in the evaporator, with some areas having good refrigeration effects and some areas having insufficient refrigeration. This uneven refrigeration effect will reduce the overall performance of the refrigeration system 1000. In other words, a liquid refrigerant diversion flow ratio of less than 90% means that part of the refrigerant fails to fully participate in the refrigeration cycle. This will cause the refrigeration effect of the refrigeration system 1000 to decrease, and the expected cooling effect cannot be met. Therefore, the diameter d3 of the first section of the flow channel 8122 can be limited to less than or equal to 1.8 mm.

[0090] In some embodiments, one end of the body 810 corresponding to the output port 8121 includes a planar portion 8112 and a conical portion 8113 disposed on the circumferential outer side of the planar portion 8112 , and the output port 8121 is disposed on the conical portion 8113 .

[0091] That is, the diverter 800 of the present application sets the output port 8121 on the conical surface portion 8113, and can accurately control the flow distribution in each diversion channel 812 by adjusting the inclination angle of the conical surface portion 8113 and the size of the output port 8121, thereby achieving a more uniform and accurate diversion effect.

[0092] See also Figure 8The present application also provides a refrigeration method, which is applied to the refrigeration system 1000 in any one of the above embodiments. The refrigeration method includes:

[0093] 01: Control the injection of gaseous refrigerant into the compressor 500, so that the gaseous refrigerant is cooled by the condenser 600 and converted into liquid refrigerant. The liquid refrigerant is evenly split by the splitter 800 and flows into the first evaporator 100 and the second evaporator 300 respectively;

[0094] 02: Control the refrigerating fan 960 and the freezing fan 970 to start working at the same time, so that the first evaporator 100 and the second evaporator 300 respectively exchange heat with the refrigerating compartment 960 and the freezing compartment 970 at the same time, so as to reduce the temperature of the refrigerating compartment 960 and the freezing compartment 970 at the same time;

[0095] The first gaseous refrigerant outputted from the first evaporator 100 flows back into the compressor 500 through the first return air pipe 930 to form a first refrigeration cycle, and the second gaseous refrigerant outputted from the second evaporator 300 flows back into the compressor 500 through the second return air pipe 940 to form a second refrigeration cycle.

[0096] Specifically, the specific structure of the refrigeration system 1000 is as described above and will not be repeated here.

[0097] In this way, the refrigeration system 1000 of the present application can simultaneously absorb the two gaseous refrigerants in different pressure states output from the first evaporator 100 and the second evaporator 300 into the compression cylinder of the compressor 500, and then respectively pass through the condenser 600, the filter 700 and the diverter 800, the first capillary tube 910 and the second capillary tube 920 in sequence, so as to achieve the simultaneous refrigeration effect of the refrigeration compartment 200 and the freezing compartment 400 in the refrigeration system 1000, save the energy consumption of the refrigeration system 1000, and the temperature fluctuation of the refrigeration compartment 200 and the freezing compartment 400 is small, and the preservation effect of food in the refrigeration compartment 200 and the freezing compartment 400 is better.

[0098] See also Fig. 9 In certain embodiments, the refrigeration method comprises:

[0099] 03: Detect the temperature of the cold storage room 200;

[0100] 04: When the temperature of the refrigerating compartment 200 is less than or equal to the first temperature threshold, the switch valve 950 is controlled to be closed.

[0101] That is, the refrigeration system 1000 of the present application may further include a first temperature sensor. The first temperature sensor may be disposed in the refrigerating compartment 200, and the first temperature sensor is used to detect the temperature of the refrigerating compartment 200 and send the temperature value to the controller, and the controller may control the closing of the switch valve 950 when the temperature of the refrigerating compartment 200 is less than or equal to the first temperature threshold.

[0102] The first temperature threshold may be, for example, 3°C, 3.5°C, 3.8°C, 4°C, 4.1°C, 4.2°C, 4.3°C, 4.4°C, 4.5°C or 5°C, and is not limited here.

[0103] It can be understood that, since the refrigeration system 1000 of the present application refrigerates the refrigerating compartment 200 and the freezing compartment 400 at the same time, the refrigerating compartment 200 will reach the desired refrigeration temperature before the freezing compartment 400. Therefore, in the refrigeration system 1000 of the present application, the temperature of the refrigerating compartment 200 can be detected in real time by the first temperature sensor. When the temperature of the refrigerating compartment 200 reaches the desired lower temperature range first, the switch valve 950 can be controlled to be closed by the controller first, so that further heat exchange between the refrigerating compartment 200 and the first evaporator 100 can be suspended, thereby reducing the energy consumption of the refrigeration system 1000, so that the refrigeration system 1000 of the present application is more energy-saving.

[0104] See also Fig.10 In certain embodiments, the refrigeration method comprises:

[0105] 05: Detect the temperature of the freezing compartment 400;

[0106] 06: When the temperature of the freezing chamber 400 is less than or equal to the second temperature threshold, the compressor 500 is controlled to stop working.

[0107] That is, the refrigeration system 1000 of the present application may also include a second temperature sensor, which may be disposed in the freezer compartment 400. The second temperature sensor is used to detect the temperature of the freezer compartment 400 and send the temperature value to the controller. The controller may control the compressor 500 to stop working when the temperature of the freezer compartment 400 is less than or equal to the second temperature threshold.

[0108] The second temperature threshold may be, for example, -16°C, -16.7°C, -17.°C, -17.5°C, -18°C, -18.5°C, -18.8°C, -19°C, -19.6°C or -20°C, without limitation herein.

[0109] It can be understood that, since the refrigeration system 1000 of the present application refrigerates the refrigerating compartment 200 and the freezing compartment 400 at the same time, the refrigerating compartment 200 will reach the desired refrigeration temperature before the freezing compartment 400. Therefore, in the refrigeration system 1000 of the present application, the temperature of the refrigerating compartment 200 can be detected in real time by the first temperature sensor. When the temperature of the refrigerating compartment 200 reaches the desired lower temperature range first, the switch valve 950 can be controlled to be closed by the controller first, so that further heat exchange between the refrigerating compartment 200 and the first evaporator 100 can be suspended, and the energy consumption of the refrigeration system 1000 can be reduced, so that the refrigeration system 1000 of the present application is more energy-saving. At the same time, in the refrigeration system 1000 of the present application, the temperature of the freezing compartment 400 can also be detected in real time by the second temperature sensor. When the temperature of the freezing compartment 400 reaches the desired lower temperature range first, the compressor 500 can be controlled to stop working by the controller to ensure that both the freezing compartment 400 and the refrigerating compartment 200 can be maintained in the corresponding expected low temperature range.

[0110] That is, the refrigeration system 1000 of the present application can form two independent refrigeration cycles in pure parallel connection, and the freezing compartment 200 and the refrigerating compartment 400 can be cooled by independent cycles at the same time.

[0111] The above embodiments only express several implementation methods of the present invention, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the present invention. It should be pointed out that, for a person of ordinary skill in the art, several modifications and improvements can be made without departing from the concept of the present invention, and these all belong to the protection scope of the present invention. Therefore, the protection scope of the present invention patent shall be subject to the attached claims.

Claims

1. A refrigeration system, characterized in that: The refrigeration system comprises: A first evaporator; Cold storage room; A second evaporator; Freezer compartment; A compressor, the compressor comprising a first air intake port and a second air intake port, the first air intake port being connected to an output end of the first evaporator, the second air intake port being connected to an output end of the second evaporator; the compressor being used for mixing and boosting a first gaseous refrigerant sucked in through the first air intake port and a second gaseous refrigerant sucked in through the second air intake port to obtain a third gaseous refrigerant; A condenser, wherein the input end of the condenser is connected to the exhaust port of the compressor, and the condenser is used to receive the third gaseous refrigerant and exchange heat with the outside so that the third gaseous refrigerant is converted into the first liquid refrigerant; A filter, wherein the input end of the filter is connected to the output end of the condenser, and the filter is used to dry and filter the first liquid refrigerant to obtain a second liquid refrigerant; A flow splitter, the flow splitter comprising a first output port and a second output port, the input port of the flow splitter being connected to the output end of the filter, the flow splitter being used to evenly split the second liquid refrigerant and output it from the first output port and the second output port; a first capillary tube, wherein the input end of the first capillary tube is connected to the first output port, the first capillary tube is used for throttling and reducing the pressure of the second liquid refrigerant, and the output end of the first capillary tube is connected to the input end of the first evaporator, and the first evaporator is used for heat exchange with the refrigerated compartment to convert the first gas-liquid two-phase refrigerant into the first gaseous refrigerant; A second capillary tube, the input end of the second capillary tube is connected to the second output port, the second capillary tube is used for throttling and reducing the pressure of the second liquid refrigerant, which is a second gas-liquid two-phase refrigerant; the output end of the second capillary tube is connected to the input end of the second evaporator, and the second evaporator is used for exchanging heat with the freezing chamber to evaporate the second gas-liquid two-phase refrigerant to absorb heat and cool it to obtain the second gaseous refrigerant.

2. The refrigeration system according to claim 1, characterized in that: The compressor includes a compression cylinder body, an exhaust pipe, a first intake pipe and a second intake pipe. A piston compression cylinder is arranged in the compression cylinder body. The first intake pipe is provided with a first welding port and the first intake port, and the first welding port is welded to the outer wall of the compression cylinder body; the second intake pipe is provided with a second welding port and the second intake port, and the second welding port is welded to the outer wall of the compression cylinder body; the exhaust pipe is provided with a third welding port and the exhaust port, and the third welding port is welded to the outer wall of the compression cylinder body.

3. The refrigeration system according to claim 2, characterized in that: The compressor further comprises a process pipe, wherein the process pipe is provided with a fourth welding port and a process port, wherein the fourth welding port is welded to the outer wall of the compression cylinder body, and the process port is used for injecting gaseous refrigerant into the compression cylinder body.

4. The refrigeration system according to claim 1, characterized in that: The refrigeration system also includes a first air return pipe and a second air return pipe, the first air return pipe is connected to the first air intake port, the second air return pipe is connected to the second air intake port, the first air return pipe connects the compressor and the first evaporator, and the second air return pipe connects the compressor and the second evaporator.

5. The refrigeration system according to claim 1, characterized in that: The refrigeration system further comprises a controller and a switch valve, wherein the controller is electrically connected to the switch valve, the switch valve is located on the pipeline between the first capillary tube and the diverter, and the controller is used to control the closing and opening of the switch valve.

6. The refrigeration system according to claim 1, characterized in that: The refrigeration system further comprises a refrigerating fan and a freezing fan. The refrigerating fan is used to drive the air in the refrigerating compartment to pass through the first evaporator; the freezing fan is used to drive the air in the freezing compartment to pass through the second evaporator.

7. The refrigeration system according to claim 1, characterized in that: The flow divider comprises a body and a valve core. The body is provided with a jet channel and a shunt channel, the first end of the jet channel extends to the outer surface of the body and forms the input port; there are multiple shunt channels, the first ends of the multiple shunt channels are all connected to the second end of the jet channel, and the second ends of the multiple shunt channels extend to the outer surface of the body and form multiple output ports; The valve core is arranged between the jet channel and the diversion channel in the body, and a throttling channel is arranged in the valve core, and the diameter of the throttling channel is smaller than the diameter of the jet channel; Wherein, the diameter of the throttling channel is less than or equal to 0.7 mm.

8. A refrigeration method, applied to the refrigeration system according to any one of claims 1 to 7, characterized in that: The refrigeration method comprises: Controlling the injection of gaseous refrigerant into the compressor, so that the gaseous refrigerant is cooled by the condenser and converted into liquid refrigerant, and the liquid refrigerant is evenly split by the splitter and flows into the first evaporator and the second evaporator respectively; Controlling the refrigerating fan and the freezing fan to start working simultaneously, so that the first evaporator and the second evaporator respectively perform heat exchange with the refrigerating compartment and the freezing compartment at the same time, so as to reduce the temperature of the refrigerating compartment and the freezing compartment at the same time; The first gaseous refrigerant output by the first evaporator flows back to the compressor through the first return pipe to form a first refrigeration cycle, and the second gaseous refrigerant output by the second evaporator flows back to the compressor through the second return pipe to form a second refrigeration cycle.

9. The refrigeration method according to claim 8, characterized in that: The refrigeration method comprises: detecting the temperature of the refrigerated compartment; When the temperature of the refrigerating compartment is less than or equal to a first temperature threshold, the switch valve is controlled to be closed.

10. The refrigeration method according to claim 9, characterized in that: The refrigeration method comprises: detecting the temperature of the freezing compartment; When the temperature of the freezing compartment is less than or equal to a second temperature threshold, the compressor is controlled to stop working.

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