CN115717786A - Refrigerating system, air conditioner and freezer - Google Patents

Abstract

The application relates to a refrigerating system, air conditioner and freezer includes: a compressor provided with an exhaust port and a return port; the inlet end of the condenser is communicated with the exhaust port; the inlet end of the first evaporator is communicated with the outlet end of the condenser through the first throttling element; a second evaporator and a second throttling element; the inlet end of the second evaporator is connected with the outlet end of the first evaporator through the second throttling element, so that the second evaporation temperature of the second evaporator is lower than the first evaporation temperature of the first evaporator; the outlet end of the second evaporator is communicated with the air return port. The refrigeration system, the air conditioner and the refrigeration house have the advantage of low cost.

Description

Refrigerating system, air conditioner and freezer

Technical Field

The application relates to the technical field of refrigeration, in particular to a refrigeration system, an air conditioner and a refrigeration house.

Background

With the improvement of the living standard of people, the application occasions requiring double-temperature refrigeration are gradually increased. Particularly, for large-scale cold storages and refrigerated transport vehicles, a refrigeration system is usually required to provide two evaporation temperatures at the same time, and the requirements of relatively low-temperature refrigeration and relatively high-temperature refrigeration are met respectively.

In the related art, two independent refrigerating systems are arranged to meet the requirements of two evaporation temperatures, but the design can increase the production cost, the number of overall welding points for pipeline design is increased, the pipeline layout on the spot by an engineer is more complex, the equipment maintenance amount is large, and the market requirements cannot be met.

Disclosure of Invention

Based on this, this application provides a refrigerating system, air conditioner and freezer, reduce cost when providing two kinds of evaporating temperature.

A first aspect of the present application provides a refrigeration system comprising: a compressor provided with an exhaust port and a return port; the inlet end of the condenser is communicated with the exhaust port; the inlet end of the first evaporator is communicated with the outlet end of the condenser through the first throttling element; a second evaporator and a second throttling element; the inlet end of the second evaporator is connected with the outlet end of the first evaporator through the second throttling element, so that the second evaporation temperature of the second evaporator is lower than the first evaporation temperature of the first evaporator; the outlet end of the second evaporator is communicated with the air return port.

In one embodiment, the refrigeration system comprises a first circuit, a second circuit, and a first pressure tank; the first pressure tank comprises a first tank opening and a second tank opening; two ends of the first pipeline are respectively communicated with the first tank opening and the outlet end of the condenser; the first throttling element is arranged on the first pipeline; and two ends of the second pipeline are respectively connected with the second tank opening and the inlet end of the first evaporator.

In one embodiment, the refrigeration system includes a third circuit and an on-off valve; two ends of the third pipeline are respectively communicated with the second throttling element and the second pipeline; the on-off valve is arranged on the third pipeline to control on-off.

In one embodiment, the refrigeration system comprises a second pressure tank, a fifth line, and a sixth line; the second pressure tank comprises a fourth tank opening and a fifth tank opening; two ends of the fifth pipeline are respectively connected with the fourth tank opening and the outlet end of the first evaporator, and the second throttling element is arranged on the fifth pipeline; and two ends of the sixth pipeline are respectively connected with the fifth tank opening and the inlet end of the second evaporator.

In one embodiment, the pressure in the second pressure tank is lower than the pressure in the first pressure tank, so that the evaporation temperature of the second evaporator is lower than the evaporation temperature of the first evaporator.

In one embodiment, the refrigeration system includes a refrigerant pump disposed on the sixth line to pump the refrigerant in the second pressure tank to the second evaporator.

In one embodiment, the refrigeration system includes a seventh circuit and an eighth circuit; the second pressure tank comprises a sixth tank opening and a seventh tank opening; two ends of the seventh pipeline are respectively communicated with the sixth tank opening and the outlet end of the second evaporator; and two ends of the eighth pipeline are respectively communicated with the seventh tank opening and the air return opening.

In one embodiment, the refrigeration system includes a fourth circuit; the compressor is provided with an air supplementing port, and the first pressure tank comprises a third tank opening; and two ends of the fourth pipeline are respectively connected with the air supplementing port and the third tank opening.

A second aspect of the present application provides an air conditioner including the refrigeration system described above.

A third aspect of the present application provides a refrigeration house comprising the air conditioner described above to provide two refrigeration temperatures.

The beneficial effects are that:

in the refrigeration system of the embodiment of the application, by arranging the first evaporator, the first throttling element, the second evaporator and the second throttling element, the inlet end of the first evaporator is communicated with the outlet end of the condenser through the first throttling element; the inlet end of the second evaporator is connected with the outlet end of the first evaporator through the second throttling element; the refrigerant flowing out of the first evaporator is throttled for the second time, so that the numerical value of the second evaporation pressure is smaller than that of the first evaporation pressure, and further, the refrigerant flowing out of the compressor has a first evaporation temperature and a second evaporation temperature at the first evaporator and the second evaporator respectively, and the first evaporation temperature and the second evaporation temperature are different in numerical value, namely, one part of external medium air which exchanges heat with the first evaporator and the other part of medium air which exchanges heat with the second evaporator can obtain different refrigerating temperatures respectively; different evaporating temperatures can be provided for the outside by only using one compressor, so that the phenomenon that two compressors are used for providing different evaporating temperatures respectively can be avoided, the pipeline of a refrigerating system is effectively simplified, and the cost of the refrigerating system is reduced.

Drawings

FIG. 1 is a schematic diagram of a refrigeration system according to an embodiment of the present application;

FIG. 2 is a schematic diagram of a refrigeration system according to another embodiment of the present application;

FIG. 3 is a schematic diagram of a refrigeration system according to yet another embodiment of the present application;

fig. 4 is a schematic diagram of a refrigeration system according to yet another embodiment of the present application.

Detailed Description

In order to make the aforementioned objects, features and advantages of the present application more comprehensible, embodiments accompanying the present application are described in detail below with reference to the accompanying drawings. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present application. This application is capable of embodiments in many different forms than those described herein and that modifications may be made by one skilled in the art without departing from the spirit and scope of the application and it is therefore not intended to be limited to the specific embodiments disclosed below.

In the description of the present application, it is to be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the present application and for simplicity in description, and are not intended to indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and are therefore not to be considered limiting of the present application.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present application, "plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.

In this application, unless expressly stated or limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can include, for example, fixed connections, removable connections, or integral parts; can be mechanically or electrically connected; they may be directly connected or indirectly connected through intervening media, or they may be interconnected within two elements or in a relationship where two elements interact with each other unless otherwise specifically limited. The specific meaning of the above terms in the present application can be understood by those of ordinary skill in the art as appropriate.

In this application, unless expressly stated or limited otherwise, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through intervening media. Also, a first feature "on," "above," and "over" a second feature may be directly on or obliquely above the second feature, or simply mean that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.

It will be understood that when an element is referred to as being "secured to" or "disposed on" another element, it can be directly on the other element or intervening elements may also be present. When an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present. As used herein, the terms "vertical," "horizontal," "upper," "lower," "left," "right," and the like are for purposes of illustration only and do not denote a single embodiment.

A first aspect of the present application provides a refrigeration system.

Referring to fig. 1, fig. 1 illustrates a schematic diagram of a refrigeration system according to an embodiment of the present application.

The refrigeration system includes a compressor 10, a condenser 20, a first evaporator 30, a first throttling element 50, a second evaporator 40, and a second throttling element 60.

The refrigeration system is filled with a refrigerant, the type of the refrigerant includes but is not limited to one or a mixture of several of freon, dichlorodifluoromethane, tetrafluoroethane, difluoromethane and pentafluoroethane, and the embodiment of the application is not limited. The refrigerant is evaporated and condensed in the refrigerating system and is converted between a gas state and a liquid state, so that heat transfer is realized.

The compressor 10 may be a reciprocating compressor, a rotary compressor, or a centrifugal compressor, and the embodiments of the present invention are not limited thereto; the compressor 10 compresses a low-temperature and low-pressure refrigerant into a high-temperature and high-pressure refrigerant.

The compressor 10 is provided with an exhaust port 11 and a return port 12, an inlet end 21 of the condenser 20 is communicated with the exhaust port 11, and a compressed high-temperature and high-pressure refrigerant in the compressor 10 enters the condenser 20 through the exhaust port 11. The external air flows through the surface of the condenser 20 filled with the high-temperature refrigerant to exchange heat. The temperature of the external medium air is raised, and the temperature of the refrigerant is reduced.

The condenser 20 may be a copper tube fin radiator, a plate heat exchanger, or other heat exchangers, which is not limited in the embodiment of the present application.

It should be understood that, in the embodiment of the present application, the external medium is air as a description object, and is driven by a fan. However, the external medium may also be water or other liquid, and the flow is driven by a pump, which is not limited in the embodiment of the present application.

The inlet end 31 of the first evaporator 30 communicates with the outlet end 22 of the condenser 20 through a first throttling element 50. The first throttling element 50 may be a thermal expansion valve, an electronic expansion valve, or a capillary tube, but the application is not limited thereto. For convenience of description, the first throttling element 50 has an inlet side for the refrigerant to enter and an outlet side for the throttled refrigerant to flow out, respectively, in the flow direction of the refrigerant.

The high-temperature and high-pressure refrigerant flowing out of the outlet end 22 of the condenser 20 is throttled by the first throttling element 50 and then converted into a low-temperature and low-pressure first refrigerant in which a gas state and a liquid state are mixed. The first refrigerant of low temperature and low pressure enters the first evaporator 30 through the inlet end 31 of the first evaporator 30.

The first refrigerant entering the first evaporator 30 has a first evaporation temperature. At the first evaporation temperature, the liquid part of the first refrigerant absorbs heat and then is converted into a gas state from the liquid state, and the temperature is kept unchanged. The value of the first evaporation temperature is positively correlated with the pressure of the first refrigerant in the first evaporator 30, that is, the higher the pressure is, the higher the first evaporation temperature is; the lower the pressure, the lower the first evaporation temperature; this pressure also corresponds to the first evaporating pressure of the first evaporator 30. Theoretically, the pressures at the outlet end 32 of the first evaporator 30, the intermediate pipe of the first evaporator 30, the inlet end 31 of the first evaporator 30, and all the way to the outlet side of the first throttling element 50 are the first evaporation pressure, without considering the pressure loss.

The external air flows through the surface of the first evaporator 30 filled with the low-temperature refrigerant to exchange heat; thus, the outside air medium can be cooled at the first evaporator 30, the temperature of the refrigerant in the first evaporator 30 is not changed, and a part of the liquid low-temperature refrigerant is converted into the gaseous low-temperature refrigerant.

The inlet end 41 of the second evaporator 40 is connected to the outlet end 32 of the first evaporator 30 via a second throttling element 60 such that the second evaporation temperature of the second evaporator 40 is lower than the first evaporation temperature of the first evaporator 30.

Similarly, the second throttling element 60 may be a thermal expansion valve, an electronic expansion valve or a capillary tube, which is not limited in this application. For convenience of description, the second throttling element 60 has an inlet side for the refrigerant to enter and an outlet side for the throttled refrigerant to flow out, respectively, in the flow direction of the refrigerant.

The first refrigerant flowing from the outlet end 32 of the first evaporator 30 and having the first evaporation pressure and the first evaporation temperature is throttled for the second time by the second throttling element 60, and is transformed into the second refrigerant with lower temperature and lower pressure. The second refrigerant of lower temperature and lower pressure enters the second evaporator 40 through the inlet end 41 of the second evaporator 40.

It should be noted that the second refrigerant at a lower temperature and a lower pressure here is relative to the first refrigerant at a low temperature and a low pressure flowing out after being throttled by the first throttling element 50; the two are physically different only in temperature, pressure, state, etc., and are substantially the same refrigerant.

Similarly, the low-temperature refrigerant entering the second evaporator 40 has the second evaporation temperature. At the second evaporation temperature, the liquid part of the second refrigerant absorbs heat and then is converted from the liquid state to the gas state, and the temperature is kept unchanged. The value of the second evaporation temperature is positively correlated with the pressure of the second refrigerant in the second evaporator 40, i.e., the higher the pressure is, the higher the second evaporation temperature is; the lower the pressure, the lower the second evaporation temperature; this pressure also corresponds to the second evaporating pressure of the second evaporator 40. In theory, all pressures from the outlet end 42 of the second evaporator 40, to the intermediate pipe of the second evaporator 40, to the inlet end 41 of the second evaporator 40, up to the outlet side of the second throttling element 60, can be regarded as second evaporation pressures, without taking into account pressure losses.

By arranging the second throttling element 60 between the inlet end 41 of the second evaporator 40 and the outlet end 32 of the first evaporator 30, the refrigerant flowing out of the first evaporator 30 is throttled for the second time, so that the value of the second evaporation pressure is smaller than that of the first evaporation pressure, and further, the refrigerant flowing out of the compressor 10 has the first evaporation temperature and the second evaporation temperature at the first evaporator 30 and the second evaporator 40 respectively, which are different in value, that is, a part of the external medium air exchanging heat with the first evaporator 30 and another part of the medium air exchanging heat with the second evaporator 40 can obtain different refrigeration temperatures respectively.

Therefore, 2 different evaporation temperatures can be provided to the outside by only using one compressor 10, and the condition that only one compressor can provide one evaporation temperature (corresponding evaporation pressure) in the related art is avoided, so that two compressors are avoided being used for respectively providing one evaporation temperature, the pipeline of the refrigeration system is effectively simplified, and the cost of the refrigeration system is reduced; in addition, because two sets of compressors are not needed to be respectively connected with the pipeline, the pipeline arrangement is simplified, the maintenance difficulty of equipment is reduced, the welding points of the pipeline can be reduced, the possibility of leakage at the joint of the pipeline is reduced, and the process is optimized.

The outlet end 42 of the second evaporator 40 communicates with the return air opening 12; the second refrigerant after heat exchange in the second evaporator 40 flows out of the outlet end 42 of the first evaporator 40 and flows back to the compressor 10 through the return port 12, thereby realizing the overall circulation of the refrigerant.

Referring to fig. 2, in some embodiments, fig. 2 illustrates a schematic diagram of a refrigeration system of another embodiment of the present application. The refrigeration system includes a first line 71, a second line 72, and a first pressure tank 80.

The first pressure tank 80 includes a first port 81 and a second port 82. Both ends of the first pipe 71 communicate with the first tank port 81 and the outlet end 22 of the condenser 20, respectively, and the first throttling element 50 is disposed in the first pipe 71. The first pipeline 71 and the second pipeline 72 can be copper pipes, and the outside of the first pipeline and the second pipeline is wrapped with heat insulation layer materials.

The second pipe 72 has two ends connected to the second tank opening 82 and the inlet end 31 of the first evaporator 30, respectively. In this manner, the first pressure tank 80 can stabilize the pressure value from the outlet side of the first throttling element 50 to the outlet end 32 of the first evaporator 30 against fluctuation.

It will be appreciated that the pressure is communicated from the first evaporator 30 to the first pressure tank 80 to the outlet side of the first throttling element 50 at the first evaporation pressure irrespective of the pressure loss.

The first pressure tank 80 is a pressure container with certain strength, the first pipeline 71 injects a first refrigerant into the first pressure tank 80 through the first tank opening 81, and the first refrigerant is in a gas-state and liquid-state mixed state; under the action of gravity, the refrigerant in liquid state is deposited at the bottom of the first pressure tank 80, and the refrigerant in gaseous state is partially located at the top of the first pressure tank 80. The second pipe 72 is inserted into the first pressure tank 80 from the second tank port 82 to a region below the liquid level of the refrigerant in the first pressure tank 80.

As the refrigerant is continuously injected into the first pressure tank 80 through the first pipe line 71, the liquid refrigerant is pressed to flow into the first evaporator 30 through the second pipe line 72, and the external medium air flows over the surface of the first evaporator 30 filled with the liquid low-temperature refrigerant to exchange heat; the temperature of the external medium air is reduced, part of the liquid refrigerant in the first evaporator 30 absorbs heat and boils into a gaseous state, and the temperature value is kept unchanged; the refrigerant, which is a mixture of gas and liquid, exits the outlet end 32 of the first evaporator 30 and enters the second throttling element 60 for a second throttling, thereby being converted into a second refrigerant of lower temperature and lower pressure.

In some embodiments, referring to fig. 2, the refrigeration system includes a third line 73 and an on-off valve 90; both ends of the third pipe 73 communicate with the inlet side of the second throttling element 60 and the second pipe 72, respectively; the on-off valve 90 is provided on the third line 73; the on-off valve 90 may be a solenoid valve for controlling the on-off of the third pipeline 73.

In this manner, separate activation of the first evaporator 30, the second evaporator 40, and simultaneous activation of the first evaporator 30 and the second evaporator 40 may be achieved.

During the activation of the first evaporator 30 alone, the on-off valve 90 disconnects the third line 73.

Specifically, the compressor 10 compresses a low-temperature and low-pressure refrigerant into a high-temperature and high-pressure refrigerant, and the high-temperature and high-pressure refrigerant enters the condenser 20 through the exhaust port 11. The external air flows through the surface of the condenser 20 filled with the high-temperature refrigerant to exchange heat, the high-temperature and high-pressure refrigerant flowing out of the outlet end 22 of the condenser 20 enters the first pipeline 71 to flow, is throttled by the first throttling element 50, is converted into the first refrigerant mixed with gas and liquid at low temperature and low pressure, and flows into the first pressure tank 80, and the refrigerant in the liquid state is deposited at the bottom of the first pressure tank 80 and enters the second pipeline 72 under the action of pressure.

The on-off valve 90 is turned off, all the liquid refrigerant flows into the first evaporator 30 through the second pipeline 72, the external medium air is driven by the fan corresponding to the first evaporator 30 and flows over the surface of the first evaporator 30 filled with the liquid low-temperature refrigerant, the air exchanges heat with the refrigerant in the first evaporator 30, the temperature of the external medium air is reduced to a first temperature, for example, 0 ℃, part of the liquid refrigerant in the first evaporator 30 absorbs heat and boils into a gas state, and the temperature value is kept unchanged.

The refrigerant of the mixture of the gas state and the liquid state flows out from the outlet end 32 of the first evaporator 30 and flows into the second evaporator 40, and at this time, the fan corresponding to the second evaporator 40 stops working, and it can be understood that the external medium air does not flow from the surface of the second evaporator 40, so that the heat exchange between the external medium air and the second evaporator 40 is very little, which is equivalent to that only the first evaporator 30 provides the corresponding refrigeration function. The refrigerant flowing out of the outlet end 42 of the second evaporator 40 flows back to the compressor 10 through the return port 12, and the entire circulation of the refrigerant is realized.

In this mode, in order to improve the efficiency of the refrigeration system, the second throttling element 60 may be opened to a full open state to reduce the throttling effect if it is an expansion valve, and a line with a solenoid valve may be bypassed to reduce the throttling effect if the second throttling element 60 is a capillary tube.

During the separate activation of the second evaporator 40, the on-off valve 90 communicates with the third line 73.

Specifically, the compressor 10 compresses a low-temperature and low-pressure refrigerant into a high-temperature and high-pressure refrigerant, and the high-temperature and high-pressure refrigerant enters the condenser 20 through the exhaust port 11. The external air flows through the surface of the condenser 20 filled with the high-temperature refrigerant to exchange heat, the high-temperature and high-pressure refrigerant flowing out of the outlet end 22 of the condenser 20 enters the first pipeline 71, is throttled by the first throttling element 50, is converted into the first refrigerant mixed with gas and liquid at low temperature and low pressure, and flows into the first pressure tank 80, and the refrigerant in the liquid state is deposited at the bottom of the first pressure tank 80 and enters the second pipeline 72 under the action of pressure.

The on-off valve 90 is connected, and the pressure at the inlet end 31 and the pressure at the outlet end 32 of the first evaporator 30 are equal, so that no refrigerant flows inside the first evaporator 30, and the fan corresponding to the first evaporator 30 is stopped, it can be understood that the external medium air does not flow from the surface of the first evaporator 30, and therefore the heat exchange between the external medium air and the first evaporator 30 is very small, which is equivalent to that only the second evaporator 40 provides a corresponding refrigeration function.

The liquid refrigerant flows into the third pipeline 73 through the second pipeline 72 without passing through the first evaporator 30, and then reaches the inlet side of the second throttling element 60, and the liquid refrigerant is throttled for the second time through the second throttling element 60, and is converted into a second refrigerant with lower temperature and lower pressure. The second refrigerant of lower temperature and lower pressure enters the second evaporator 40 through the inlet end 41 of the second evaporator 40. The external medium air is driven by the fan corresponding to the second evaporator 40 and flows over the surface of the second evaporator 40 filled with the low-temperature refrigerant, the air exchanges heat with the refrigerant in the second evaporator 40, the temperature of the external medium air is lowered to a second temperature, for example, -20 ℃, part of the liquid refrigerant in the second evaporator 40 absorbs the heat and boils into a gas state, and the temperature value is kept unchanged. The refrigerant flowing out of the outlet end 42 of the second evaporator 40 flows back to the compressor 10 through the return port 12, and the entire circulation of the refrigerant is realized.

The on-off valve 90 disconnects the third line 73 during simultaneous activation of the first evaporator 30 and the second evaporator 40.

The overall principle process is similar to the process of separately starting the first evaporator 30, and the detailed description is omitted here; however, the fan corresponding to the second evaporator 40 needs to be turned on, the refrigerant in a mixture of gas and liquid flows from the outlet end 32 of the first evaporator 30 into the second evaporator 40, and the fan corresponding to the second evaporator 40 drives the external medium air to exchange heat with the second evaporator 40, so that the first evaporator 30 and the second evaporator 40 can respectively provide corresponding cooling functions. In which a portion of the external medium air can exchange heat with the refrigerant in the first evaporator 30, and the temperature of the external medium air is lowered to a first temperature, for example, -10 ℃. Another part of the external medium air can exchange heat with the refrigerant in the second evaporator 40, and the temperature of the external medium air is lowered to a second temperature, for example, -30 ℃.

The refrigerant flowing out of the outlet end 42 of the second evaporator 40 flows back to the compressor 10 through the return port 12, and the entire circulation of the refrigerant is realized.

Referring to fig. 3, in some embodiments, fig. 3 is a schematic diagram of a refrigeration system according to yet another embodiment of the present application. The refrigeration system comprises a second pressure tank 100, a fifth line 75 and a sixth line 76. The second pressure tank 100 comprises a fourth tank opening 101 and a fifth tank opening 102; both ends of the fifth pipe 75 are connected to the fourth tank opening 101 and the outlet end 32 of the first evaporator 30, respectively, and the second throttling element 60 is provided on the fifth pipe 75. The fifth pipeline 75 and the sixth pipeline 76 may be copper pipes, and are wrapped with insulation layer material.

Both ends of the sixth pipeline 76 are connected to the fifth tank port 102 and the inlet end 41 of the second evaporator 40, respectively. In this manner, the second pressure tank 100 can stabilize the pressure value from the outlet side of the second throttling element 60 to the outlet end 42 of the second evaporator 40 against fluctuation.

It will be appreciated that the pressure is communicated from the second evaporator 40 to the second pressure tank 100 to the outlet side of the second throttling element 60 at the second evaporation pressure irrespective of the pressure loss.

It is understood that the evaporation pressure in the refrigeration system is positively correlated with the evaporation temperature, the pressure in the first pressure tank 80 is the first evaporation pressure, the pressure in the second pressure tank 100 is the second evaporation pressure, and the pressure in the second pressure tank 100 is set lower than the pressure in the first pressure tank 80, so that the second evaporation temperature of the second evaporator 40 is lower than the first evaporation temperature of the first evaporator 30, regardless of the pressure loss.

The second pressure tank 100 is a pressure container with a certain strength, and the fifth pipeline 75 injects a second refrigerant into the second pressure tank 100 through the fourth tank opening 101, where the second refrigerant is in a mixed state of a gas state and a liquid state; the refrigerant in the liquid state is deposited on the bottom of the second pressure tank 100 under the gravity, and the refrigerant in the gaseous state is partially located on the top of the second pressure tank 100. The sixth pipe 76 is inserted into the second pressure tank 100 from the fifth port 102 to a region below the liquid level of the refrigerant in the second pressure tank 100.

As the fifth pipe 75 continues to inject the refrigerant into the second pressure tank 100, the liquid refrigerant is pressed to flow into the second evaporator 40 from the sixth pipe 76, and the external medium air flows over the surface of the second evaporator 40 filled with the liquid low-temperature refrigerant to exchange heat; the temperature of the external medium air is reduced, part of the liquid refrigerant in the second evaporator 40 absorbs heat and boils into a gas state, and the temperature value is kept unchanged; thereby, the refrigerant mixed with gas and liquid flows out from the outlet end 42 of the second evaporator 40 and flows back to the compressor 10 from the return port 12, and the entire circulation of the refrigerant is realized.

In some embodiments, referring to fig. 4, fig. 4 is a schematic diagram of a refrigeration system according to yet another embodiment of the present application. The refrigeration system includes a refrigerant pump 110, the refrigerant pump 110 is disposed on the sixth pipeline 76 to pump the refrigerant in the second pressure tank 100 to the second evaporator 40; thus, the refrigerant can be provided to the second evaporator 40 in a pumping manner, and the liquid part in the refrigerant throttled for the second time by the second throttling element 60 is prevented from being too small, so that the refrigerant flowing into the second evaporator 40 is sufficient, and the heat exchange effect of the second evaporator 40 can be ensured.

In some embodiments, referring to fig. 4, the refrigeration system includes a seventh circuit 77 and an eighth circuit 78; the second pressure tank 100 includes a sixth port 103 and a seventh port 104;

both ends of the seventh pipe 77 communicate with the sixth tank port 103 and the outlet port 42 of the second evaporator 40, respectively; both ends of the eighth pipeline 78 are communicated with the seventh tank port 104 and the return air port 12, respectively. The seventh pipeline 77 and the eighth pipeline 78 can both be copper pipes, and the exterior of the copper pipes is wrapped with a heat insulation layer material.

The mixed refrigerant of gas and liquid flowing out of the outlet end 42 of the second evaporator 40 can be returned to the second pressure tank 100 from the sixth tank port 103 through the seventh pipe 77; thus, the refrigerant in the second pressure tank 100 includes the refrigerant in the gas and liquid states which is throttled for the second time by the second throttling element 60, and the refrigerant in the gas and liquid states which is heat-exchanged by the second evaporator 40 (both are substantially throttled for the second time, and the difference is whether the refrigerant passes through the second evaporator 40).

The coolant in liquid form is deposited by gravity at the bottom of the second pressure tank 100 and the coolant in gaseous form is partially located at the top of the second pressure tank 100. The seventh tank opening 104 is located at the top of the second pressure tank 100, and the eighth pipeline 78 is communicated with the seventh tank opening 104 and located in a region above a liquid level line of the refrigerant in the second pressure tank 100.

In this way, as the refrigerant in the gas state and the liquid state is stored in the second pressure tank 100, the refrigerant in the liquid state is pumped by the refrigerant pump 110 to flow from the sixth pipeline 76 into the second evaporator 40 for heat exchange, and the refrigerant in the gas state enters the eighth pipeline 78 through the seventh tank opening 104 and flows back to the compressor 10 from the return port 12, so that the refrigerant in the liquid state is prevented from impacting the compressor 10, and the overall circulation of the refrigerant is realized.

In other embodiments, referring to fig. 2 and 3, the refrigerant system may also be provided with a separate gas-liquid separator 120, and the outlet end 42 of the second evaporator 40 is connected to the return air inlet 12 through the gas-liquid separator 120.

Specifically, the mixed refrigerant of gas phase and liquid phase flowing out from the outlet end 42 of the second evaporator 40 enters the gas-liquid separator 120, and the gas-phase refrigerant flows back to the compressor 10 from the return port 12, so as to prevent the liquid-phase refrigerant from impacting the compressor 10, thereby realizing the overall circulation of the refrigerant.

In some embodiments, as shown with reference to fig. 2-4, the refrigeration system includes a fourth line 74; the compressor 10 is provided with an air supplement port 13, and the first pressure tank 80 comprises a third tank port 83; the air supply port 13 and the third tank port 83 are connected to both ends of the fourth pipeline 74. The fourth pipe 74 may be a copper pipe, and is wrapped with a thermal insulation layer material.

The high-temperature and high-pressure refrigerant flowing out of the outlet end 22 of the condenser 20 is throttled by the first throttling element 50 and converted into a low-temperature and low-pressure first refrigerant in which a gas state and a liquid state are mixed, and the first refrigerant flows along the first pipeline 71 and is injected into the first pressure tank 80 through the first tank port 81.

Under the action of gravity, the refrigerant in the liquid state is deposited at the bottom of the first pressure tank 80, and the refrigerant in the gaseous state is partially located at the top of the first pressure tank 80. The third tank port 83 is located at the top of the first pressure tank 80, and the fourth pipe 74 is communicated with the third tank port 83 and located in a region above a liquid level line of the refrigerant in the first pressure tank 80.

In this way, as the refrigerant in the gas state and the liquid state are mixed and stored in the first pressure tank 80, the liquid refrigerant flows into the first evaporator 30 from the second pipeline 72 to exchange heat, the gas refrigerant enters the fourth pipeline 74 through the third tank port 83, and flows back to the compressor 10 from the air supplement port 13, so that the gas refrigerant is prevented from accumulating in the first pressure tank 80, and the overall circulation of the refrigerant is realized.

A second aspect of the present application provides an air conditioner including the refrigeration system described above.

A third aspect of the present application provides a refrigeration storage, including the above-mentioned air conditioner, this refrigeration storage provides two kinds of refrigeration temperatures through this air conditioner.

Wherein a first temperature, which may be 10 to-10 °, is provided by the first evaporator 30 for pre-cooling the item to be frozen; a first temperature, which may be in the range of-20 to-50 deg., is provided by the second evaporator 40 for use in freezing the pre-cooled items.

The technical features of the embodiments described above may be arbitrarily combined, and for the sake of brevity, all possible combinations of the technical features in the embodiments described above are not described, but should be considered as being within the scope of the present specification as long as there is no contradiction between the combinations of the technical features.

The above-mentioned embodiments only express several embodiments of the present application, and the description thereof is more specific and detailed, but not construed as limiting the claims. It should be noted that, for a person skilled in the art, several variations and modifications can be made without departing from the concept of the present application, which falls within the scope of protection of the present application. Therefore, the protection scope of the present patent shall be subject to the appended claims.

Claims (10)

1. A refrigeration system, comprising:

a compressor (10), the compressor (10) being provided with an exhaust port (11) and a return port (12);

a condenser (20), an inlet end of the condenser (20) being in communication with the exhaust port (11);

a first evaporator (30) and a first throttling element (50), wherein the inlet end of the first evaporator (30) is communicated with the outlet end of the condenser (20) through the first throttling element (50);

a second evaporator (40) and a second throttling element (60); the inlet end of the second evaporator (40) is connected to the outlet end of the first evaporator (30) by means of the second throttling element (60) so that the second evaporation temperature of the second evaporator (40) is lower than the first evaporation temperature of the first evaporator (30); the outlet end of the second evaporator (40) is communicated with the air return opening (12).

2. A refrigeration system according to claim 1, characterized in that it comprises a first circuit (71), a second circuit (72) and a first pressure tank (80);

the first pressure tank (80) comprises a first tank opening (81) and a second tank opening (82);

two ends of the first pipeline (71) are respectively communicated with the first tank opening (81) and the outlet end of the condenser (20); the first throttling element (50) is arranged in the first pipeline (71);

the two ends of the second pipeline (72) are respectively connected with the second tank opening (82) and the inlet end of the first evaporator (30).

3. A refrigeration system according to claim 2, characterized in that it comprises a third line (73) and a shut-off valve (90);

both ends of the third pipeline (73) are respectively communicated with the second throttling element (60) and the second pipeline (72); the on-off valve (90) is arranged on the third pipeline (73) to control on-off.

4. A refrigeration system according to claim 3, characterized in that it comprises a second pressure tank (100), a fifth line (75) and a sixth line (76);

the second pressure tank (100) comprises a fourth tank opening (101) and a fifth tank opening (102);

both ends of the fifth pipeline (75) are respectively connected with the fourth tank opening (101) and the outlet end of the first evaporator (30), and the second throttling element (60) is arranged on the fifth pipeline (75);

the two ends of the sixth pipeline (76) are respectively connected with the fifth tank opening (102) and the inlet end of the second evaporator (40).

5. A refrigeration system according to claim 4, characterized in that the pressure in the second pressure tank (100) is lower than the pressure in the first pressure tank (80), so that the evaporation temperature of the second evaporator (40) is lower than the evaporation temperature of the first evaporator (30).

6. The refrigeration system according to claim 4, characterized in that the refrigeration system comprises a refrigerant pump (110), the refrigerant pump (110) being arranged on the sixth line (76) to pump the refrigerant in the second pressure tank (100) to the second evaporator (40).

7. A refrigeration system as claimed in claim 6, characterized in that it comprises a seventh circuit (77) and an eighth circuit (78);

the second pressure tank (100) comprises a sixth tank opening (103) and a seventh tank opening (104);

two ends of the seventh pipeline (77) are respectively communicated with the sixth tank opening (103) and the outlet end of the second evaporator (40);

and two ends of the eighth pipeline (78) are respectively communicated with a seventh tank opening (104) and the air return opening (12).

8. A refrigeration system as claimed in any one of claims 2 to 7, characterized in that it comprises a fourth line (74);

the compressor (10) is provided with an air supplementing port (13), and the first pressure tank (80) comprises a third tank port (83); and two ends of the fourth pipeline (74) are respectively connected with the air supplementing port (13) and the third tank opening (83).

9. An air conditioner characterized by comprising a refrigeration system as recited in any one of claims 1 to 8.

10. A cold storage, comprising an air conditioner according to claim 9 to provide two cooling temperatures.

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