Cooling Systems and Equipment

Abstract

A cooling system (100) and a cooling device, the cooling system (100) including a circulation circuit, the circulation circuit including a main flow path (21) and a first branch path (22) and a second branch path (23) connected to the main flow path (21) and installed in parallel, a condenser (3) and a compressor (1) are installed in the main flow path (21), and an output end of the condenser (3) is connected to the first branch path (22) and The compressor (1) has two intake holes (1a, 1b), and the two intake holes (1a, 1b) of the compressor (1) communicate with the other ends of the first branch path (22) and the second branch path (23), respectively. A first evaporator (41) and a second evaporator (42) are provided in the first branch path (22) and the second branch path (23) corresponding to each other.

Description

[Technical field]

[0001] This application claims priority to Chinese patent applications bearing application numbers 202210155536.5 and 202220372515.4, filed on February 18, 2022, the entire contents of which are incorporated herein by reference.

[0002] The present application relates to the technical field of cooling systems, and in particular to cooling systems and cooling equipment. [Background technology]

[0003] Traditional refrigerators, freezers and other cooling equipment and reciprocating compressors have undergone decades of development, and the current equipment technology maturity is very high, and the performance level also tends to be a bottleneck. Facing the future major upgrade of the refrigeration industry, there is a lack of innovative and breakthrough technological progress. For example, some current independent double circulation refrigerators adopt two compressors and corresponding two sets of independent refrigeration equipment and control, and such simple combination and superposition results in high overall equipment cost, poor system integration, and only basic functions. Summary of the Invention [Problem to be solved by the invention]

[0004] The main objective of this application is to provide a refrigeration system and refrigeration equipment, which applies a dual suction compressor to set up a dual evaporator refrigeration system, so as to meet the demands of more multi-function and higher performance. [Means for solving the problem]

[0005] In order to achieve the above object, the present application provides a cooling system, comprising a circulation circuit, the circulation circuit including a main flow path and a first branch path and a second branch path connected to the main flow path and arranged in parallel, a condenser and a compressor are installed in the main flow path, an output end of the condenser is connected to one end of the first branch path and one end of the second branch path, the compressor has two intake holes, the two intake holes of the compressor are connected to the other end of the first branch path and the second branch path respectively, and a first evaporator and a second evaporator are installed in the first branch path and the second branch path correspondingly.

[0006] In one embodiment, the compressor includes a working chamber opened therein, a first intake hole is provided at a bottom of the working chamber and a second intake hole is provided at a side wall of the working chamber, the first intake hole and the second intake hole are respectively connected to the first branch passage and the second branch passage, and a piston movably mounted within the working chamber, the piston having a piston component having a first dead center located at a bottom of the working chamber and a second dead center away from the bottom of the working chamber during a movable stroke.

[0007] In one embodiment, the distance between the second intake port and the first dead center is L, the distance between the first dead center and the second dead center is S, and 0.5S <Lである。

[0008] In one embodiment, the intake pressure of the first intake port is less than the intake pressure of the second intake port, and the temperature of the first evaporator is less than the temperature of the second evaporator.

[0009] In one embodiment, the temperature of the second evaporator is T1 and the temperature of the first evaporator is T2, where 0≦T1−T2≦25° C.

[0010] In one embodiment, -15°C≦T1≦0°C, -30°C≦T2≦-15°C, and 10≦T1-T2≦20°C.

[0011] In one embodiment, the cooling system further includes at least one diversion valve, the diversion valve being installed at a connection point between the first branch, the second branch and the main flow path, or a control valve being installed in the first branch and / or the second branch.

[0012] In one embodiment, the cooling system further includes two throttling elements installed in the first branch and the second branch, respectively, one of the throttling elements being located between the corresponding condenser and the first evaporator, and the other of the throttling elements being located between the corresponding condenser and the second evaporator.

[0013] In one embodiment, each said throttling element is a capillary or an expansion valve.

[0014] The present application further provides a cooling device, including the above cooling system, wherein the cooling system includes a circulation circuit, the circulation circuit includes a main flow path, and a first branch path and a second branch path connected to the main flow path and installed in parallel, a condenser and a compressor are installed in the main flow path, an output end of the condenser is connected to one end of the first branch path and one end of the second branch path, the compressor has two intake holes, the two intake holes of the compressor are connected to the other end of the first branch path and the second branch path respectively, and a first evaporator and a second evaporator are installed in the first branch path and the second branch path correspondingly.

[0015] In one embodiment, the cooling appliance is a refrigerator. Effect of the Invention

[0016] In the technical solution of the present application, the two independent intake passages in the compressor can realize the first evaporator and the second evaporator to be independent from each other, and the overall efficiency of the cooling system is higher. Specifically, the first branch passage and the second branch passage can simultaneously flow through the first evaporator and the second evaporator in the dual intake structure of the compressor, and the two evaporators can be operated simultaneously, which increases the cooling capacity of the system, and has a larger cooling amount and higher cooling performance than the traditional single intake and exhaust compressor and series-parallel dual evaporator cooling system, which can better meet future technical needs. [Brief description of the drawings]

[0017] In order to more clearly describe the technical solutions in the embodiments of the present application or the prior art, the following briefly introduces drawings that need to be used in the description of the embodiments or the prior art. Obviously, the drawings in the following description are only some embodiments of the present application, and those skilled in the art can further obtain other drawings based on the structures shown in these drawings without making any creative efforts. [Figure 1] FIG. 1 is a schematic diagram of one embodiment of a cooling system provided herein. [Diagram 2] FIG. 2 is a schematic diagram of another embodiment of the cooling system in FIG. [Diagram 3] FIG. 2 is a schematic diagram of yet another embodiment of the cooling system in FIG. [Figure 4] FIG. 2 is a schematic diagram of the internal structure of one embodiment of the compressor in FIG. [Diagram 5] FIG. 5 is a schematic cross-sectional view of a part of the compressor in FIG.

[0018] The realization of the objectives, functional features and advantages of the present application will be further explained in connection with the embodiments and with reference to the drawings. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0019] Hereinafter, the technical solutions in the embodiments of the present application will be described clearly and completely with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are only some of the embodiments of the present application, and not all of the embodiments of the present application, and all other embodiments obtained by those skilled in the art on the premise of not making creative efforts based on the embodiments of the present application are all within the scope of protection of the present application.

[0020] In addition, in the case of directional indications in the embodiments of the present application, the directional indications are used only to interpret the relative positional relationships, movement conditions, etc. between each component in a certain specific posture, and if the certain posture changes, the directional indications also change accordingly.

[0021] In addition, if there is a description of "first", "second", etc. in the embodiments of the present application, the description of "first", "second", etc. is only used for explanation, and cannot be understood as indicating or implying the relative importance or implying the number of the indicated technical features. Thus, the features defined by "first" and "second" can explicitly or implicitly include at least one of the features. In addition, the technical solutions between the embodiments can be combined with each other, but this must be based on what a person skilled in the art can realize. If the combination of the technical solutions is mutually contradictory or cannot be realized, such combination of technical solutions does not exist and is not within the scope of protection claimed by the present application.

[0022] With the upgrade of global carbon emission regulations and the urgent demands of China's national carbon emissions peaking and achieving carbon neutrality, the requirements for energy saving and emission reduction in the refrigeration industry are also increasing, and the national energy efficiency standards for various home appliances are also being upgraded, which in turn increases the requirements for technological upgrades for household refrigeration equipment such as refrigerators and freezers.

[0023] Traditional refrigerators, freezers and other cooling equipment and reciprocating compressors have undergone decades of development, large-scale industrialization and market competition, and the current equipment technology maturity is very high, and the performance level also tends to be a bottleneck. Facing the future major upgrade of the refrigeration industry, lacking innovative and breakthrough technological progress, the compressor is the most important component of the refrigeration system and the component with the largest energy consumption, and the combination method of it with other parts in the refrigeration system and the circulation configuration method of the entire refrigeration system have a huge impact on the overall cooling performance and energy efficiency level of the equipment such as refrigerators and freezers.

[0024] In view of this, the present application provides a cooling system and cooling equipment, which uses a dual-suction compressor to set up a dual-evaporator cooling system, so as to meet the demands of greater functionality and higher performance. Figures 1 to 5 show an embodiment of the cooling system provided by the present application.

[0025] 1 and 2, a cooling system 100 includes a circulation circuit, the circulation circuit including a main flow path 21 and a first branch path 22 and a second branch path 23 connected to the main flow path 21 and installed in parallel, a condenser 3 and a compressor 1 are installed in the main flow path 21, an output end of the condenser 3 is connected to one end of the first branch path 22 and the second branch path 23, the compressor 1 has two intake holes, the two intake holes of the compressor 1 are connected to the other ends of the first branch path 22 and the second branch path 23 correspondingly, and a first evaporator 41 and a second evaporator 42 are installed corresponding to the first branch path 22 and the second branch path 23.

[0026] In the technical solution of the present application, the two independent intake passages in the compressor 1 can realize that the first evaporator 41 and the second evaporator 42 are independent from each other, and the overall efficiency of the cooling system 100 is higher; specifically, the first branch passage 22 and the second branch passage 23 allow the compressor 1 to have a dual intake structure and flow through the first evaporator 41 and the second evaporator 42 simultaneously, and the first evaporator 41 and the second evaporator 42, which have different temperatures, can be operated simultaneously, thereby increasing the cooling capacity of the system, and compared with the conventional single-suction single-row compressor and series-parallel dual evaporator cooling system, it has a larger cooling amount and higher cooling performance, and can better meet future technical requirements.

[0027] In order to realize the dual intake function of the compressor 1, referring to Figs. 4 and 5, the compressor 1 provided in the present application includes a cylinder body and a piston component, the cylinder body includes a working chamber 11 opened therein, a first intake hole 1a is provided at the bottom of the working chamber 11, and a second intake hole 1b is provided at the side wall of the working chamber 11, the first intake hole 1a and the second intake hole 1b are respectively connected to the first branch passage 22 and the second branch passage 23, the piston component includes a piston 12 movably installed in the working chamber 11, and the piston 12 has a first dead center located at the bottom of the working chamber 11 and a second dead center away from the bottom of the working chamber 11 during a moving stroke. In the compressor 1 provided by the present application, the working chamber 11 is simultaneously connected to the first intake hole 1a and the second intake hole 1b, and gas can be simultaneously replenished into the working chamber 11 through the first branch passage 22 and the second branch passage 23, which are connected to the first intake hole 1a and the second intake hole 1b, thereby improving the intake amount of the working chamber 11 and further improving the compression energy efficiency of the compression cylinder, and the first intake hole 1a and the second intake hole 1b are respectively connected to two parallel flow paths to realize respective working conditions and reduce power consumption. In addition, the compressor 1 has the advantages of simple structure, low cost, higher performance and higher practicality.

[0028] Specifically, the compressor 1 is a double intake compressor, and due to the positions of the first intake hole 1a and the second intake hole 1b in the working chamber 11, the intake pressure of the first intake hole 1a is lower than the intake pressure of the second intake hole 1b, and the first intake hole 1a communicates with an external duct to form a first intake through passage with low airflow pressure, and the second intake hole 1b communicates with an external duct to form a second intake through passage with high airflow pressure, which can effectively improve the energy efficiency of the cooling system 100 and reduce power consumption. Accordingly, the first evaporator 41 and the second evaporator 42 correspond to different cold chambers in the cooling equipment and are used for storing fresh-keeping or refrigerated foods, respectively, and therefore taking into consideration the different evaporation temperatures of the different evaporators, the first evaporator 41 communicating with the first intake passage having a low airflow pressure should have a low temperature, and the second evaporator 42 communicating with the second intake passage having a high airflow pressure should have a high temperature.

[0029] Specifically, the temperature difference between the first evaporator 41 and the second evaporator 42 is required as follows, where the temperature of the second evaporator 42 is T1 and the temperature of the first evaporator 41 is T2, where 0≦T1-T2≦25°C.

[0030] Furthermore, the first evaporator 41 in this application is a freezing evaporator, and the second evaporator 42 is a refrigerated evaporator, which generally have different temperature settings, -15°C≦T1≦0°C, -30°C≦T2≦-15°C, and 10≦T1-T2≦20°C, because the cooling demands of the cold rooms corresponding to the refrigerated evaporator and the freezing evaporator are different.

[0031] In one embodiment, the piston component further includes a crankshaft and a link, the crankshaft is transmission-connected to one end of the link, and one end of the link remote from the crankshaft is transmission-connected to the piston 12. Thus, the crankshaft drives the link to move by the drive of a motor, and further drives the piston 12 to reciprocate in the working chamber 11, completing the operations of airflow intake and airflow compression.

[0032] As can be understood, taking a refrigerator as an example, in the cooling process, the high-temperature and high-pressure refrigerant gas is transported from the compressor to the evaporators of the corresponding freezer compartment and refrigerator compartment to perform evaporation and heat absorption, thereby realizing the cooling of the freezer compartment and the refrigerator compartment. However, the temperatures set for the freezer compartment and the refrigerator compartment do not match, and their evaporation temperatures are different. After the refrigerant exchanges heat in the freezer compartment and the refrigerator compartment, the temperature and pressure are different. The first evaporator 41 and the second evaporator 42 in this embodiment respectively correspond to the freezer compartment and the refrigerator compartment. In the prior art, the compressor realizes the cooling functions of refrigeration and refrigeration through one flow path. When it is necessary to cool the freezer compartment or the refrigerator compartment in this way, the entire heat exchange system needs to participate in the operation, resulting in high energy consumption and low energy efficiency.

[0033] In a normal compressor, it is always necessary to control the opening and closing of each intake hole by a control valve group. Therefore, when the compressor has only one intake hole, one control valve group is installed. When the compressor has a plurality of intake holes, generally a plurality of control valve groups are installed correspondingly, and thus the control is complicated. Therefore, in an embodiment of the present application, the distance between the second intake hole 1b and the first dead center is L, and the distance between the first dead center and the second dead center is S, where 0.5S < L. During the movement process of the piston 12, the opening and closing states of the first intake hole 1a and the second intake hole 1b are as follows.

[0034] The intake stroke of the compressor 1 includes the following.

[0035] In the first stroke, the piston 12 moves from the first dead center to the second dead center, and the distance from the first dead center is less than 0.5S. In the first stroke, the control valve group is turned on, the first intake hole 1a is open, and the second intake hole 1b is blocked by the piston 12. At this time, the working chamber 11 realizes intake only through the first intake hole 1a, and the total amount of refrigerant in the working chamber 11 at this time is derived from the refrigerant of the first intake hole 1a. As can be seen, when the piston 12 moves to a position approaching the second dead center, the compression space of the working chamber 11 increases and is in a negative pressure state, so that the external air flow is likely to enter the working chamber 11 from the first intake hole 1a. Meanwhile, the pressure of the air flow through the first intake hole 1a is smaller than the pressure of the air flow through the second intake hole 1b. Therefore, during this moving stroke, the piston 12 blocks the second intake hole 1b, preventing the airflow from the second intake hole 1b from impeding the airflow from the first intake hole 1a from entering the working chamber 11.

[0036] In the second stroke, the piston 12 moves from the first dead center to the second dead center, and the distance from the first dead center is greater than 0.5S. In the second stroke, the piston 12 does not block the second intake hole 1b, and the second intake hole 1b communicates with the working chamber 11. At this time, the control valve group switches between an on state and an off state according to actual demand. When the control valve group is in an on state, the first intake hole 1a and the second intake hole 1b simultaneously input airflow into the working chamber 11. In the first stroke, a certain amount of airflow is sucked into the space of the working chamber 11 through the first intake hole 1a, so that the compression space has a certain airflow pressure. Therefore, when the airflow is input into the working chamber 11 through the second intake hole 1b, the impact on the airflow of the first intake hole 1a is small. And the distance from the second intake port 1b to the first dead center is greater than 0.5S, i.e., the distance to the first intake port 1a is greater than 0.5S, so that there is an appropriate buffer distance between them, which reduces the obstruction effect of the airflow of the second intake port 1b on the airflow of the first intake port 1a, and improves the compression energy efficiency. When the control valve group is in the OFF state, the second intake port 1b inputs the airflow into the working chamber 11. At this time, the refrigerant replenished in the working chamber 11 comes from the second intake port 1b. As can be understood, the closer the second intake hole 1b is to the midpoint between the first dead point and the second dead point, the sooner the on-time of the second intake hole 1b is, the later the closing time is, the longer the high pressure refrigerant time provided by the corresponding flow path is, and the larger the gas replenishment amount is, and the closer the second intake hole 1b is to the second dead point, the slower the on-time of the second intake hole 1b is, the sooner the closing time is, the shorter the high pressure refrigerant time provided by the corresponding flow path is, and the shorter the gas replenishment time is, and therefore the smaller the gas replenishment amount is. In reality, the position of the second intake hole 1b can be set according to the demand for the gas replenishment amount.

[0037] The compression stroke of the compressor 1 includes:

[0038] In the third stroke, the piston 12 moves from the second dead center toward the first dead center, and the distance from the first dead center is greater than 0.5S. In the third stroke, the control valve group closes, and the piston 12 moves rapidly toward the first dead center. At this time, the second intake port 1n still inputs airflow into the working chamber 11, and the refrigerant replenished in the working chamber 11 at this time comes from the second intake port 1b, so that in the third stroke, when the airflow in the working chamber 11 is compressed, the airflow input into the working chamber 11 through the second intake port 1b is not excessively hindered, and the compressor 1 can still suck in the airflow in the compression stroke. In addition, since the airflows originating from the first air intake hole 1a and the second air intake hole 1b are mixed in the working chamber 11, the pressure of the airflow in the working chamber 11 is lower than the pressure of the airflow passing through the second air intake hole.

[0039] In the fourth stroke, the piston 12 moves from the second dead center toward the first dead center, and the distance from the first dead center is less than 0.5S. In the fourth stroke, the control valves are still closed, and the piston 12 blocks the second intake port 1b. In this process, the piston 12 compresses the airflow in the working chamber 11 into a high-pressure airflow. When the piston 12 moves to the second dead center, the airflow pressure in the working chamber 11 is compressed to a predetermined position. At this time, the control valves communicating with the output pipe of the working chamber 11 are switched from a closed state to an open state, and the compressed high-pressure airflow is output.

[0040] In addition, in this embodiment, the compressor 1 further includes a housing, a first intake outer pipe 210, a second intake outer pipe 220, and a second intake inner pipe 13 communicating with the second intake outer pipe 220, the first intake outer pipe 210 and the second intake outer pipe 220 are installed outside the housing, and the second intake inner pipe 13 is installed inside the housing, specifically, the first intake outer pipe 210 and the second intake outer pipe 220 are used to connect to the first intake hole 1a and the second intake hole 1b. The compressor 1 is installed in the inner chamber of the housing, where the second intake inner pipe 13 is connected to one end of the second intake outer pipe 220 installed in the housing to form a second intake through passage, and the first intake outer pipe 210 correspondingly forms a first intake through passage.

[0041] The operating lines corresponding to the two cooling channels are as follows:

[0042] The airflow path in the first intake through passage is the first cooling passage→the first intake hole 1 a→the working chamber 11.

[0043] The airflow passage in the second intake through passage is the second cooling passage→the second intake port 1b→the working chamber 11.

[0044] The compressor 1 further includes an internal exhaust pipe 14 communicating with the working chamber 11, and the internal exhaust pipe 14 communicates with an exhaust outer pipe 230 of the compressor 1, thereby being used to discharge the high-pressure air flow compressed in the working chamber 11 from the internal exhaust pipe 14 to the exhaust outer pipe 230.

[0045] In actual practice, the first cooling flow path corresponds to the freezer compartment of a refrigerator, and the amount of cooling required for the freezer compartment is large, so the amount of refrigerant required is large, and the pressure of the refrigerant consumed during operation is also large, while the second cooling flow path corresponds to the refrigerator compartment of a refrigerator, and the amount of cooling required for the refrigerator compartment is small, so the pressure of the refrigerant consumed during operation is also small, and thus the pressure of the refrigerant returned to the first intake port 1a is much smaller than the pressure of the second intake port 1b, but the amount of refrigerant in the first cooling flow path is large, and thus, when the compressor 1 operates, the first intake port 1a is mainly opened to perform main intake during the intake stroke of just over half the time before the intake stroke, and a large amount of refrigerant can be sucked into the cooling flow path corresponding to the freezer compartment, and during the intake stroke of just under half the time after the intake stroke, In this embodiment, the second intake hole 1b communicates with the working chamber 11, the first intake hole 1a closes, the second intake hole 1b starts to replenish high pressure refrigerant gas, continues to replenish gas in a little less than half of the stroke before the compression stage, and finally, in a little more than half of the stroke after the compression, the second intake hole 1b closes, and the piston 12 compresses the refrigerant in the working chamber 11. By setting the distance from the second intake hole 1b to the first dead center and the second dead center, the amount of air supplied to the second intake hole 1b can be controlled; that is, by setting the position of the second intake hole 1b, the opening and closing time of the second intake hole 1b can be adjusted when the piston 12 reciprocates, thereby realizing the adjustment of the mixture ratio of the flow rate of the first intake hole 1a and the second intake hole 1b. By locating the second intake port 1b on the side wall of the cylinder body and close to the second dead center, the compressor 1 does not need to install a special control valve group to control the opening and closing of the second intake port 1b. The second intake port 1b can be automatically opened and closed during the moving stroke of the piston 12, which is an ingenious structural design and further saves costs.

[0046] The distance between the first dead center and the second dead center is S. That is, the first dead center is the position where one end of the piston 12 approaches the bottom wall of the cylinder body when the end face of the one end of the piston 12 approaches the bottom of the working chamber 11 moves to the closest distance where it approaches the bottom wall of the cylinder body. The second dead center is the position where one end of the piston 12 approaches the bottom wall of the cylinder body when the end face of the one end of the piston 12 approaches the bottom wall of the cylinder body moves to the farthest distance from the bottom of the working chamber 11. That is, the distance S is the distance between two limit states of the end face of one end of the piston 12 approaching the bottom wall of the cylinder body. The distance between the second intake hole 1b and the first dead center is L, that is, the distance between the center line of the second intake hole 1b and the first dead center is L.

[0047] In addition, a vibration-damping pipe section can be designed in the second intake inner pipe 13, and the inner wall surface of the vibration-damping pipe section is provided with a concave-convex structure in the length direction of the second intake inner pipe 13. By providing the concave-convex structure in the second intake pipe, the sound waves generated by the high-pressure gas passing through the second intake inner pipe 13 can be reflected by the concave-convex structure due to the deformation of the cross section of the pipe in the transport direction. Some of the sound waves propagating forward return to the origin and then turn around and propagate forward again. This point merges with the second sound wave propagating forward that is not reflected. The two are equal in amplitude and differ in phase by an odd multiple of 180 degrees, so they interfere with each other and cancel each other out, thereby achieving the effect of vibration and noise suppression.

[0048] The throttle element is one of the basic components in a compression type cooling system. Its function is to reduce the high pressure coolant liquid from the condenser 3 to a low pressure low temperature coolant and put it into the evaporator to absorb heat by evaporation. Main types include capillary, throttle short tube, thermal expansion valve, electronic expansion valve, float valve, etc. In one embodiment, the cooling system 100 further includes two throttle elements 7 installed in the first branch 22 and the second branch 23, respectively, one of the throttle elements 7 is located between the corresponding condenser 3 and the first evaporator 41, and the other throttle element 7 is located between the corresponding condenser 3 and the second evaporator 42, thereby realizing its function, and the present application does not limit the specific type of the two throttle elements 7, and both of them may be installed the same or designed differently.

[0049] In order to facilitate the control of selective opening and closing of the first branch path 22 and the second branch path 23, referring to FIG. 2, the cooling system 100 further includes a diverter valve 5, which is installed at the connection point of the first branch path 22, the second branch path 23 and the main flow path 21. The diverter valve 5 is also called a speed synchronization valve, which is a collective term for the diverter valve 5, junction valve, one-way diverter valve 5, one-way junction valve and proportional diverter valve 5 in hydraulic valves. It has many advantages such as simple structure, low cost, easy manufacture and high reliability, and is widely used in hydraulic systems. The design of the diverter valve 5 can synchronize the flow speed of the liquid divided by the main flow path 21 into the first branch path 22 and the second branch path 23, and at the same time, the diverter valve 5 can close one of the branches, thereby controlling the communication and blocking of the first branch path 22 and the second branch path 23 according to the actual working state.

[0050] 3, in another embodiment, a control valve 6 is installed in the second branch path 23, and in this case, the first branch path 22 is always in communication, but the second branch path 23 can be selectively opened or closed under the control of the control valve 6, thereby realizing different operating states. In addition, the control valve 6 may be installed separately in the first branch path 22, or the control valves 6 may be installed in both the first branch path 22 and the second branch path 23, thereby realizing automatic opening and closing of each branch path.

[0051] Specifically, the cooling system 100 in this embodiment has the following structure.

[0052] A double intake reciprocating compressor and a condenser 3 are installed in the main flow path 21, a freezing evaporator and a refrigerating evaporator are installed in the first branch path 22 and the second branch path 23, respectively, corresponding to a first intake hole 1a and a second intake hole 1b communicating with the double intake reciprocating compressor, wherein the first intake hole 1a and the second intake hole 1b communicate with a first intake outer pipe 210 and a second intake outer pipe 220 independent of each other, and the intake pressure of the second intake hole 1b is higher than the intake pressure of the first intake hole 1a, a throttle element 7 located in the first branch path 22 is installed between the condenser 3 and the first evaporator 41, and a throttle element 7 located in the second branch path 23 is installed between the condenser 3 and the second evaporator 42. a refrigeration evaporator 7 is installed in the refrigeration system 100; and a dividing valve 5 is installed at the junction of the first branch passage 22, the second branch passage 23 and the main passage 21, so that the refrigeration system 100 has different working states. The dual suction reciprocating compressor forms two independent suction passages with different suction pressures, which realizes that the refrigeration evaporator and the freezing evaporator are independent of each other and have different evaporation temperatures, thereby improving the refrigeration evaporation temperature compared with the conventional refrigeration system 100, so that the overall efficiency of the refrigeration system is higher, has a larger cooling amount and higher cooling performance, and can better meet future technical demands. Moreover, the dual suction reciprocating compressor and the refrigeration system 100 are simple, low-cost and more practicable.

[0053] In the technical solution provided by the present application, the first branch path 22 and the second branch path 23 correspond to a freezing cooling flow path and a refrigeration cooling flow path, respectively, that is, the compressor 1 can rationally distribute the high-temperature, high-pressure refrigerant compressed and formed to the freezing flow path and the refrigeration flow path, and the high-temperature, high-pressure refrigerant compressed and formed by the compressor 1 has a low temperature and a low pressure when it returns to the compressor 1 after passing through the first evaporator 41 corresponding to the freezing compartment, but the high-temperature, high-pressure refrigerant compressed and formed by the compressor 1 has a high temperature and a high pressure when it returns to the compressor 1 after passing through the second evaporator 42 corresponding to the refrigeration compartment. The working chamber 11 of the cylinder body is simultaneously connected to the first intake hole 1a and the second intake hole 1b, and can pass through the first intake through-passage corresponding to the first intake hole 1a and the second intake through-passage corresponding to the second intake hole 1b. Thus, the low-temperature and low-pressure refrigerant returned from the freezing chamber is transported into the cylinder body of the compressor 1 through the first intake hole 1a, while the high-temperature and high-pressure refrigerant returned from the refrigerator chamber is transported to the compressor 1 through the second intake hole 1b. Thus, when the cylinder body compresses the refrigerant gas transported from the first intake hole 1a, the second intake hole 1b can replenish gas into the working chamber 11, thereby improving the intake amount of the working chamber 11 of the cylinder body and further improving the compression energy efficiency of the compressor 1.

[0054] The present application further provides a cooling device, which includes the above cooling system 100, and the cooling device includes all the technical features of the above cooling system 100, and therefore has the technical effects of all the above technical features, which will not be described here one by one. Note that the cooling device may be a refrigerator, a freezer, a cooler box, etc., and is not limited here. In this embodiment, the cooling device is a refrigerator.

[0055] The above are merely preferred embodiments of the present application, and are not intended to limit the scope of the patent of the present application. Equivalent structural transformations made using the contents of the specification and drawings of the present application based on the inventive concept of the present application, or direct / indirect application in other related technical fields, are all within the scope of patent protection of the present application. [Explanation of symbols]

[0056] 100 Cooling System 1 Compressor 1a First air intake 1b Second intake hole 11 Working chamber 12 Piston 13 Second intake inner pipe 14 Internal drain pipe 21 Main channel 22 The first fork 23 The second fork 3. Condenser 41 First evaporator 42 Second evaporator 5. Diverter Valve 6. Control valve 7 Aperture element 210 First intake outer pipe 220 Second intake outer pipe 230 Exhaust Outer Pipe

Claims

1. a refrigeration system comprising: a circulation circuit, the circulation circuit including a main flow path, and a first branch path and a second branch path connected to the main flow path and installed in parallel; a condenser and a compressor are installed in the main flow path, an output end of the condenser is connected to one end of the first branch path and one end of the second branch path; the compressor has two intake holes, the two intake holes of the compressor are connected to the other end of the first branch path and the second branch path, respectively; and a first evaporator and a second evaporator are installed in the first branch path and the second branch path, corresponding to each other.

2. The compressor includes: a cylinder body including a working chamber opened therein, a first intake hole provided at a bottom of the working chamber and a second intake hole provided at a side wall of the working chamber, the first intake hole and the second intake hole communicating with the first branch passage and the second branch passage, respectively; 2. The cooling system of claim 1, further comprising: a piston movably mounted within the working chamber, the piston having a first dead center located at a bottom of the working chamber and a second dead center away from the bottom of the working chamber during a moving stroke.

3. 3. The cooling system of claim 2, wherein a distance between the second intake port and the first dead center is L, a distance between the first dead center and the second dead center is S, and 0.5S<L.

4. an intake pressure of the first intake hole is lower than an intake pressure of the second intake hole; The cooling system of claim 2 , wherein the temperature of the first evaporator is lower than the temperature of the second evaporator.

5. 2. The cooling system of claim 1, wherein the temperature of the second evaporator is T1 and the temperature of the first evaporator is T2, and 0≦T1-T2≦25° C.

6. 6. The cooling system of claim 1, wherein -15°C≦T1≦0°C, -30°C≦T2≦-15°C, and 10≦T1-T2≦20°C.

7. The cooling system further includes at least one diversion valve, the diversion valve being located at a junction of the first branch, the second branch, and the main flow path; or The cooling system of claim 1 , wherein a control valve is provided in the first branch and / or the second branch.

8. 2. The cooling system of claim 1, further comprising two throttling elements respectively installed in the first branch and the second branch, one of the throttling elements being located between the corresponding condenser and the first evaporator, and the other of the throttling elements being located between the corresponding condenser and the second evaporator.

9. The cooling system of claim 8 , wherein each said throttling element is a capillary or an expansion valve.

10. A cooling appliance comprising a cooling system according to any one of claims 1 to 9.

11. The cooling appliance of claim 10, wherein the cooling appliance is a refrigerator.

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