CN215724330U - Refrigerant circulation system, refrigerator and air conditioner - Google Patents
Refrigerant circulation system, refrigerator and air conditioner Download PDFInfo
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- CN215724330U CN215724330U CN202122258466.XU CN202122258466U CN215724330U CN 215724330 U CN215724330 U CN 215724330U CN 202122258466 U CN202122258466 U CN 202122258466U CN 215724330 U CN215724330 U CN 215724330U
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Abstract
The disclosure relates to a refrigerant circulating system, a refrigerator and an air conditioner. The refrigerant circulation system includes: a compressor (10); a first heat exchanger (20) communicated with a discharge port of the compressor (10) through a refrigerant flow path; the two ends of the second heat exchanger (30) are respectively communicated with the first heat exchanger (20) and a suction port of the compressor (10) through a refrigerant flow path; and the first control valve (40) is arranged between the refrigerant flow paths between the first heat exchanger (20) and the second heat exchanger (30) and is configured to enable the refrigerant flow paths between the first heat exchanger (20) and the second heat exchanger (30) to be in a throttling state under a refrigerating working condition or a heating working condition and enable the refrigerant flow paths between the first heat exchanger (20) and the second heat exchanger (30) to be in a direct connection state under a defrosting working condition. The embodiment of the disclosure can reduce the input power in the defrosting process.
Description
Technical Field
The disclosure relates to the field of refrigeration, in particular to a refrigerant circulating system, a refrigerator and an air conditioner.
Background
For an air-cooled refrigerator, defrosting is required after a freezing chamber evaporator thereof frosts. In some related technologies, the defrosting is carried out by adopting an electric heating mode, the input power is high, the energy consumption is high, the temperature of a freezing chamber rises obviously during the defrosting period, the temperature rises above 3 ℃, and can seriously exceed 10 ℃, so that the temperature is uneven, and the storage of food materials is influenced.
Disclosure of Invention
In view of this, the embodiments of the present disclosure provide a refrigerant circulation system, a refrigerator and an air conditioner, which can reduce the power input during the defrosting process.
In one aspect of the present disclosure, there is provided a refrigerant circulation system including: a compressor; the first heat exchanger is communicated with the discharge port of the compressor through a refrigerant flow path; the two ends of the second heat exchanger are respectively communicated with the first heat exchanger and the suction inlet of the compressor through a refrigerant flow path; and the first control valve is arranged between the refrigerant flow paths between the first heat exchanger and the second heat exchanger and is configured to enable the refrigerant flow paths between the first heat exchanger and the second heat exchanger to be in a throttling state under a refrigerating working condition or a heating working condition and enable the refrigerant flow paths between the first heat exchanger and the second heat exchanger to be in a straight-through state under a defrosting working condition.
In some embodiments, the first control valve comprises: and the electronic expansion valve is connected in series on a refrigerant flow path between the first heat exchanger and the second heat exchanger, and the opening degree of the electronic expansion valve is set to be the maximum opening degree under the defrosting condition and is set to be the non-maximum opening degree under the refrigerating condition or the heating condition.
In some embodiments, the first control valve comprises: the switching valve is configured to conduct a refrigerant flow path where the switching valve is located under the defrosting condition and to disconnect the refrigerant flow path where the switching valve is located under the cooling condition or the heating condition.
In some embodiments, the refrigerant circulation system further includes: the heat exchange device is arranged on a refrigerant flow path between the second heat exchanger and the suction inlet of the compressor; and the second control valve is arranged on a refrigerant flow path between the second heat exchanger and the heat exchange device and is configured to enable the refrigerant flow path between the second heat exchanger and the heat exchange device to be in a direct-connection state under the refrigerating working condition or the heating working condition, and enable the refrigerant flow path between the second heat exchanger and the heat exchange device to be in a throttling state when the defrosting effect of the second heat exchanger does not meet the preset condition under the defrosting working condition.
In some embodiments, the heat exchange device comprises: the heat exchange medium container is internally filled with a liquid heat exchange medium which exchanges heat with the environment; and the heat exchange sleeve is connected in series on a refrigerant flow path between the second heat exchanger and the suction inlet of the compressor, is arranged in the heat exchange medium container and is used for enabling the refrigerant circulating in the heat exchange sleeve to exchange heat with the liquid heat exchange medium.
In some embodiments, the heat exchange medium container is a bubble trap and the liquid heat exchange medium is water.
In some embodiments, the heat exchange sleeve is smaller in size than the second heat exchanger.
In some embodiments, the first heat exchanger is also disposed in the heat exchange medium container, and is configured to exchange heat between the refrigerant circulating in the first heat exchanger and the liquid heat exchange medium.
In some embodiments, the refrigerant circulation system further includes: the temperature sensing bulb is arranged at the lowest temperature position of the second heat exchanger and is configured to detect the current lowest temperature of the second heat exchanger; the preset condition is that the current lowest temperature of the second heat exchanger exceeds a first preset temperature within a first preset time.
In some embodiments, the refrigerant circulation system further includes: the condensation preventing pipe is connected in series on a refrigerant flow path between the first control valve and the first heat exchanger; and/or a filter connected in series to a refrigerant flow path between the first heat exchanger and the first control valve.
In some embodiments, the refrigerant circulation system further includes: and the controller is in signal connection with the first control valve and the second control valve, is configured to switch the working condition of the refrigerant circulating system, and sends a control instruction to the first control valve and the second control valve according to the working condition of the refrigerant circulating system.
In one aspect of the present disclosure, there is provided a refrigerator including: the above-mentioned refrigerant circulation system.
In some embodiments, the refrigerator includes: and the second heat exchanger in the refrigerant circulating system is used as an evaporator under a refrigeration working condition to control the temperature of the freezing chamber.
In one aspect of the present disclosure, there is provided an air conditioner including: the above-mentioned refrigerant circulation system.
In some embodiments, the air conditioner further comprises: and the second heat exchanger in the refrigerant circulating system is arranged in the outdoor unit and absorbs heat outdoors as an evaporator under the heating working condition.
Therefore, according to the embodiment of the disclosure, the first control valve is arranged between the first heat exchanger and the second heat exchanger, and the first control valve enables the refrigerant flow path where the first control valve is located to be in a throttling state under the cooling working condition or the heating working condition, and enables the refrigerant flow path where the first control valve is located to be in a straight-through state under the defrosting working condition. Therefore, the first control valve is used as a throttling unit between the condenser and the evaporator under the refrigerating working condition or the heating working condition and is not throttled under the defrosting working condition, so that high-temperature and high-pressure refrigerant in the condenser directly flows into the evaporator, and hot gas defrosting is carried out on the evaporator. Because the hot gas defrosting is carried out in the evaporator, mainly for the conduction heat transfer, compare in the mode of electric heater heating air among the relevant art with the convection current of evaporator defrosting or directly to the mode of evaporator radiation heating defrosting, need not extra input power, consequently reduce the power that puts into during the defrosting process, compare in electric heating mode moreover, the defrosting effect is faster, and the temperature rise of defrosting is also littleer.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, illustrate embodiments of the disclosure and together with the description, serve to explain the principles of the disclosure.
The present disclosure may be more clearly understood from the following detailed description, taken with reference to the accompanying drawings, in which:
fig. 1-5 are schematic structural views of some embodiments of a refrigerant circulation system according to the present disclosure;
FIG. 6 is a schematic diagram illustrating temperature rise comparison of defrosting according to some embodiments of the refrigerant circulation system and related technology using electric heaters;
fig. 7 is a schematic diagram illustrating temperature rise comparison between multiple times of defrosting and related art defrosting using an electric heater according to some embodiments of the refrigerant circulation system of the present disclosure.
It should be understood that the dimensions of the various parts shown in the figures are not drawn to scale. Further, the same or similar reference numerals denote the same or similar components.
Detailed Description
Various exemplary embodiments of the present disclosure will now be described in detail with reference to the accompanying drawings. The description of the exemplary embodiments is merely illustrative and is in no way intended to limit the disclosure, its application, or uses. The present disclosure may be embodied in many different forms and is not limited to the embodiments described herein. These embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the disclosure to those skilled in the art. It should be noted that: the relative arrangement of parts and steps, the composition of materials, numerical expressions and numerical values set forth in these embodiments are to be construed as merely illustrative, and not as limitative, unless specifically stated otherwise.
The use of "first," "second," and similar terms in this disclosure is not intended to indicate any order, quantity, or importance, but rather are used to distinguish one element from another. The word "comprising" or "comprises", and the like, means that the element preceding the word covers the element listed after the word, and does not exclude the possibility that other elements are also covered. "upper", "lower", "left", "right", and the like are used merely to indicate relative positional relationships, and when the absolute position of the object being described is changed, the relative positional relationships may also be changed accordingly.
In the present disclosure, when a specific device is described as being located between a first device and a second device, there may or may not be intervening devices between the specific device and the first device or the second device. When a particular device is described as being coupled to other devices, that particular device may be directly coupled to the other devices without intervening devices or may be directly coupled to the other devices with intervening devices.
All terms (including technical or scientific terms) used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this disclosure belongs unless specifically defined otherwise. It will be further understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the relevant art and will not be interpreted in an idealized or overly formal sense unless expressly so defined herein.
Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail but are intended to be part of the specification where appropriate.
Fig. 1-5 are schematic structural diagrams of some embodiments of a refrigerant circulation system according to the present disclosure. Referring to fig. 1-5, in some embodiments, the refrigerant circulation system includes: a compressor 10, a first heat exchanger 20, a second heat exchanger 30, and a first control valve 40. The first heat exchanger 20 communicates with a discharge port of the compressor 10 through a refrigerant passage. Both ends of the second heat exchanger 30 are respectively communicated with the first heat exchanger 20 and the suction port of the compressor 10 through a refrigerant passage. The first control valve 40 is disposed between the refrigerant flow paths between the first heat exchanger 20 and the second heat exchanger 30, and is configured to enable the refrigerant flow paths between the first heat exchanger 20 and the second heat exchanger 30 to be in a throttling state under a cooling working condition or a heating working condition, and enable the refrigerant flow paths between the first heat exchanger 20 and the second heat exchanger 30 to be in a straight-through state under a defrosting working condition.
In this embodiment, the first control valve is arranged between the first heat exchanger and the second heat exchanger, and the first control valve makes the refrigerant flow path where the first control valve is located in a throttling state under a cooling working condition or a heating working condition, and makes the refrigerant flow path where the first control valve is located in a straight-through state under a defrosting working condition. Thus, the first control valve is used as a throttling unit between the condenser and the evaporator in a refrigerating working condition or a heating working condition to form a refrigerating/heating refrigerant circulation loop comprising the compressor, the first heat exchanger (used as the condenser), the first control valve (used as the throttling unit) and the second heat exchanger (used as the evaporator).
The first control valve is switched to a straight-through state under the defrosting working condition, the refrigerant is not throttled any more, and therefore the high-temperature and high-pressure refrigerant in the condenser can directly flow into the evaporator through the first control valve to defrost the evaporator through hot gas. Because the hot gas defrosting is carried out in the evaporator and mainly adopts conduction heat exchange, compared with the mode of heating air by an electric heater in the related art and convecting with the evaporator to defrost or the mode of directly heating the evaporator to defrost by radiation, extra input power is not needed, and the input power in the defrosting process is reduced. Compared with an electric heating mode, the hot-air defrosting mode adopted by the embodiment has the advantages that the defrosting speed is higher, and the defrosting temperature is increased less. In addition, the safety of the electric appliance is better by omitting an electric heater.
The refrigerant circulation system of the embodiment can be applied to various devices needing defrosting of the evaporator, such as a refrigerator or an air conditioner. Taking the refrigerator including the refrigerant circulation system of the present embodiment as an example, the refrigerator includes a freezing chamber in addition to the refrigerant circulation system. The refrigerator may further include a refrigerating chamber, a temperature changing chamber, and the like. And the second heat exchanger in the refrigerant circulating system can be used as an evaporator under the refrigeration working condition to control the temperature of the freezing chamber. When the first control valve makes the refrigerant flow path in the throttling state in the refrigerating or heating condition, the refrigerant circulating system may form a refrigerating circulation loop, the first heat exchanger has temperature of about 42 deg.c to dissipate heat to the outside, and the second heat exchanger may reach below-26 deg.c to lower the temperature of the freezing chamber of the refrigerator to-18 deg.c.
For the air-cooled refrigerator, cooled airflow can enter a freezing chamber, a temperature changing chamber and a refrigerating chamber through an air duct system so as to realize the conventional refrigerating function of the refrigerator. Due to the existence of water vapor, after certain door opening and closing times are accumulated, the second heat exchanger frosts. In the related art, the defrosting is realized by adopting a heat transfer mode that an electric heater radiates or convects air to the second heat exchanger outside the second heat exchanger, and heated air can enter a freezing chamber and the like along with an air duct system, so that the temperature of the freezing chamber and the like is obviously increased, and the storage condition is influenced.
For the refrigerator of the present embodiment, the operation mode of the refrigerator is switched from the cooling mode to the defrosting mode when defrosting is required. Under the defrosting mode, the first control valve is switched to a direct connection state, the refrigerant is not throttled any more, the high-temperature and high-pressure refrigerant in the first heat exchanger can directly flow into the second heat exchanger through the first control valve, and defrosting of defrosting on the second heat exchanger by the high-temperature gaseous refrigerant is achieved. This way, the electric heater can be eliminated, thereby saving the component cost and the energy consumed by defrosting the electric heater. In addition, in the defrosting effect, the hot gas defrosting is realized by directly conducting and heating the second heat exchanger by the high-temperature gaseous refrigerant flowing into the second heat exchanger, the heat loss is small, and the air around the second heat exchanger is not directly heated, so that the temperature rise of a freezing chamber and the like is less, and the storage condition of the refrigerator is influenced as little as possible.
Fig. 6 is a schematic diagram illustrating temperature rise comparison when defrosting is performed according to some embodiments of the refrigerant circulation system and the related art using the electric heater according to the present disclosure. Referring to fig. 6, a curve a is a temperature rise curve of a freezing chamber of a refrigerator defrosted by an electric heater, and a curve B isThe temperature rise curve of the freezing chamber of the refrigerator comprising the refrigerant circulating system of the embodiment is shown. Temperature peak T of curve AATemperature peak T higher than B curveBAnd T isBThe difference between the temperature values of the freezing chamber before and after defrosting is small, so that the storage condition in the freezing chamber is less influenced.
In other embodiments of the present application, an electric heater may be further included as a spare, so that either defrosting mode is selected according to circumstances, or both defrosting modes of hot air defrosting and electric heating are used simultaneously to increase the defrosting speed.
Taking the air conditioner including the refrigerant circulation system of the present embodiment as an example, the air conditioner includes an outdoor unit in addition to the refrigerant circulation system. And a second heat exchanger in the refrigerant circulating system is arranged in the outdoor unit and is used as an evaporator for absorbing heat outdoors under the heating working condition. The air conditioner may frost a heat exchanger in an outdoor unit during heating in winter, and needs to be defrosted. Under the heating working condition of the air conditioner, the refrigerant discharged by the compressor firstly enters a first heat exchanger in the indoor unit and then enters a second heat exchanger of the outdoor unit after passing through the throttling action of the first control valve. And when the second heat exchanger needs defrosting, the air conditioner is switched to a defrosting mode.
Under the defrosting mode, the first control valve is switched to a direct connection state, the refrigerant is not throttled any more, the high-temperature and high-pressure refrigerant in the first heat exchanger can directly flow into the second heat exchanger through the first control valve, and defrosting of defrosting on the second heat exchanger by the high-temperature gaseous refrigerant is achieved. Compared with the mode of assisting defrosting by adopting another unit in the related art, the defrosting is assisted without another heating unit in the embodiment, so that the cost can be saved and the adaptability is improved. For the refrigeration air conditioner, when the external environment temperature is too low and the outdoor heat exchanger frosts, the embodiment of the application can also be adopted to realize the hot gas defrosting mode.
Referring to fig. 2, in some embodiments, the first control valve 40 includes: and an electronic expansion valve 41 connected in series to a refrigerant flow path between the first heat exchanger 20 and the second heat exchanger 30, wherein an opening degree of the electronic expansion valve 41 is set to a maximum opening degree in the defrosting mode, and is set to a non-maximum opening degree in the cooling mode or the heating mode. The electronic expansion valve 41 can realize the direct connection of the refrigerant flow path between the first heat exchanger 20 and the second heat exchanger 30 in the maximum opening state, so that the high-temperature gaseous refrigerant in the first heat exchanger 20 can directly enter the second heat exchanger 30 through the electronic expansion valve 41 to realize the hot gas defrosting. The electronic expansion valve 41 can adjust the opening degree according to the actual conditions of the refrigeration working condition or the heating working condition under the non-maximum opening degree so as to meet the refrigeration or heating requirements.
In some embodiments, the coolant circulation system further includes a controller. The controller is in signal connection with the first control valve 40, and is configured to switch the working condition of the refrigerant circulation system and send a control instruction to the first control valve 40 according to the working condition of the refrigerant circulation system. For example, the controller is in signal connection with the electronic expansion valve 41, and the electronic expansion valve 41 can adjust its opening degree according to a control command issued by the controller.
Referring to fig. 3, in some embodiments, the first control valve 40 includes: a throttle valve 42 and a switching valve 43 connected in parallel with each other. The switching valve 43 is configured to open the refrigerant flow path where the switching valve 43 is located under the defrosting condition, and to close the refrigerant flow path where the switching valve 43 is located under the cooling condition or the heating condition. The throttle valve 42 may employ a throttle element such as a capillary tube. The controller can be in signal connection with the switching valve 43, and the switching valve 43 can be used for switching on or off the refrigerant flow path of the switching valve according to a control command sent by the controller.
The throttle valve 42 corresponds to a throttling element of the refrigerant circulation circuit when the switching valve 43 cuts off the refrigerant passage in which it is located. When the switching valve 43 is turned on, the pressure drop of the refrigerant flow path where the switching valve 43 is located is smaller than that of the refrigerant flow path where the throttle valve 42 is located, so that the high-temperature refrigerant of the first heat exchanger 20 mainly flows into the second heat exchanger 30 through the switching valve 43 to achieve hot gas defrosting.
Considering that the heat accumulated when the first heat exchanger 20 is used as a condenser in the cooling operation or the heating operation may not be enough to defrost the second heat exchanger 30, referring to fig. 4 and 5, in some embodiments, the refrigerant cycle system further includes: a heat exchange device 50 and a second control valve 60. The heat exchanger 50 is disposed in a refrigerant flow path between the second heat exchanger 30 and the suction port of the compressor 10. The second control valve 60 is disposed in a refrigerant flow path between the second heat exchanger 30 and the heat exchanger 50.
Under the cooling working condition or the heating working condition, the second control valve 60 makes the refrigerant flow path between the second heat exchanger 30 and the heat exchanging device 50 in a straight-through state. Under the defrosting condition, the second control valve 60 still keeps the refrigerant flow path between the second heat exchanger 30 and the heat exchange device 50 in a straight-through state. If the defrosting effect of the second heat exchanger 30 can satisfy the preset condition, the second control valve 60 does not need to be switched. When the defrosting effect of the second heat exchanger 30 does not satisfy the preset condition, the second control valve 60 allows the refrigerant flow path between the second heat exchanger 30 and the heat exchange device 50 to be in a throttling state.
Referring to fig. 4 and 5, in some embodiments, the refrigerant circulation system further includes: a bulb 71, disposed at a lowest temperature position of the second heat exchanger 30 (e.g., a bottom of the second heat exchanger 30, etc.), configured to detect a current lowest temperature of the second heat exchanger 30. Accordingly, the preset condition in the foregoing embodiment is that the current lowest temperature of the second heat exchanger 30 exceeds the first preset temperature (e.g., 10 ℃ or the like) within a first preset time period (e.g., 15 minutes or the like). In other embodiments, the preset condition may also take other forms, such as only determining whether the current lowest temperature exceeds the first preset temperature. The temperature of the second heat exchanger may also be not limited to the lowest temperature, for example, the temperature of a plurality of locations on the second heat exchanger may be collected and averaged, or the temperature of the second heat exchanger may be collected or calculated by other means.
Still taking the refrigerator as an example, under the defrosting condition, the first control valve is switched to the through state, the refrigerant is not throttled any more, the second control valve is kept in the through state, and the refrigerant is not throttled, at this time, the high-temperature and high-pressure refrigerant in the first heat exchanger can directly flow into the second heat exchanger through the first control valve, the evaporator is defrosted by hot gas defrosting, and the refrigerant flows back to the compressor through the second control valve and the heat exchange device.
If the defrosting of the second heat exchanger does not reach the end condition, for example, the current lowest temperature of the second heat exchanger does not reach 10 ℃ all the time, or the time length of exceeding 10 ℃ does not exceed 15 minutes, the controller sends an instruction to the second control valve 60, so that the second control valve 60 enables the refrigerant flow path between the second heat exchanger 30 and the heat exchange device 50 to be in a throttling state. Thus, the second control valve 60 corresponds to a throttle unit in the refrigerant circulation circuit, the first heat exchanger 20 and the second heat exchanger 30 correspond to a condenser in the refrigerant circulation circuit, and the heat exchanger 50 corresponds to an evaporator in the refrigerant circulation circuit. The heat absorbed by the heat exchange device 50 is transferred to the second heat exchanger along with the refrigerant circulation loop, so that the second heat exchanger continues to be heated and defrosted.
In fig. 4 and 5, the heat exchanging device 50 includes: a heat exchange medium container 51 and a heat exchange sleeve 52. The heat exchange medium container 51 is filled with a liquid heat exchange medium that exchanges heat with the environment. For example, the heat exchange medium container 51 is a bubble water box, and the liquid heat exchange medium is water. The water in the water soaking box can come from defrosting water discharged by the water receiving tray, and the water keeps basically consistent with the temperature of the external environment under the refrigerating or heating working condition.
The heat exchange sleeve 52 is connected in series to a refrigerant flow path between the second heat exchanger 30 and the suction port of the compressor 10, and is disposed in the heat exchange medium container 51, so as to perform heat exchange between the refrigerant circulating in the heat exchange sleeve 52 and the liquid heat exchange medium. Compared with a heat exchange mode with air, the liquid heat exchange medium has certain heat capacity and can provide more heat for the refrigerant circulating system under the defrosting working condition.
To reduce the effect of heat exchange sleeve 52 on the refrigeration cycle when functioning as an evaporator under normal cooling or heating conditions, in some embodiments, heat exchange sleeve 52 is sized smaller than the size of the second heat exchanger 30.
Referring to fig. 5, in some embodiments, the first heat exchanger 20 may also be disposed in the heat exchange medium container 51, and configured to exchange heat between the refrigerant circulating in the first heat exchanger 20 and the liquid heat exchange medium. In other words, the first heat exchanger 20 and the heat exchange jacket 52 can be disposed adjacently and both of them are immersed in the liquid heat exchange medium in the heat exchange medium container 51, which can further enhance the heat exchange effect.
Under the refrigeration condition, the first heat exchanger 20 is used as a condenser to release heat to the liquid heat exchange medium, so that the temperature of the liquid heat exchange medium is increased, and the liquid heat exchange medium starts to store heat, for example, the temperature of the liquid heat exchange medium is consistent with that of the first heat exchanger 20 and is 40 ℃. When the defrosting operation mode is switched, the heat exchange sleeve 52 is equivalent to an evaporator through the switching of the second control valve, the heat exchange sleeve can absorb heat from a heat-storage liquid heat exchange medium, and the absorbed heat is transferred to the second heat exchanger along with the circulation of the refrigerant in the refrigerant circulation loop to be defrosted, so that the defrosting effect is enhanced, and the defrosting time is shortened.
In addition, referring to fig. 4 and 5, in some embodiments, the refrigerant circulation system may further include: a condensation prevention tube 72 and/or a filter 73. The condensation preventing pipe 72 is connected in series to the refrigerant flow path between the first control valve 40 and the first heat exchanger 20, and may be used as a condenser with the first heat exchanger 20 under a cooling condition. The filter 73 is connected in series to the refrigerant flow path between the first heat exchanger 20 and the first control valve 40, and filters impurities in the refrigerant after the refrigerant enters the first control valve.
The embodiments of the refrigerant circulation system disclosed by the disclosure can be applied to various refrigeration/heating equipment with defrosting requirements, such as refrigerators, air conditioners and the like. Therefore, the present disclosure further provides a refrigerator including the embodiment of the refrigerant circulation system. The refrigerator may further include: and the second heat exchanger 30 in the refrigerant circulating system is used as an evaporator under a refrigerating condition to control the temperature of the freezing chamber. In addition, the present disclosure also provides an air conditioner (for example, a household air conditioner) including the refrigerant circulation system. The air conditioner may further include: and an outdoor unit, wherein the second heat exchanger 30 of the refrigerant circulation system is disposed in the outdoor unit and absorbs heat outdoors as an evaporator under a heating condition.
Based on the embodiments of the refrigerant circulation system, the embodiment of the present disclosure further provides a corresponding defrosting process. The defrosting process comprises the following steps: when the working condition of the refrigerant cycle system is switched from the cooling working condition or the heating working condition to the defrosting working condition, a control instruction is sent to the first control valve 40, so that the first control valve 40 switches the refrigerant flow path between the first heat exchanger 20 and the second heat exchanger 30 from the throttling state to the straight-through state. The steps of the defrosting method can be completed by calling a program instruction in a memory by a controller in the refrigerant circulating system.
In some embodiments, the defrosting process may include: when the working condition of the refrigerant circulating system is switched from a refrigeration working condition or a heating working condition to a defrosting working condition, sending a control instruction to the first control valve 40; according to the received control instruction, the first control valve 40 switches the refrigerant flow path between the first heat exchanger 20 and the second heat exchanger 30 from the throttling state to the through state.
In this embodiment, the first control valve is used as a throttling unit between the condenser and the evaporator under the cooling working condition or the heating working condition, and is not throttled under the defrosting working condition, so that the high-temperature and high-pressure refrigerant in the condenser directly flows into the evaporator, and the evaporator is defrosted by hot gas defrosting. Because the hot gas defrosting is carried out in the evaporator, mainly for the conduction heat transfer, compare in the mode of electric heater heating air among the relevant art with the convection current of evaporator defrosting or directly to the mode of evaporator radiation heating defrosting, need not extra input power, consequently reduce the power that puts into during the defrosting process, compare in electric heating mode moreover, the defrosting effect is faster, and the temperature rise of defrosting is also littleer.
In some embodiments, the refrigerant circulation system further includes a heat exchanging device 50 and a second control valve 60, the heat exchanging device 50 is disposed on the refrigerant flow path between the second heat exchanger 30 and the suction port of the compressor 10, and the second control valve 60 is disposed on the refrigerant flow path between the second heat exchanger 30 and the heat exchanging device 50. Correspondingly, the defrosting process further comprises the following steps: and judging whether the defrosting effect of the second heat exchanger 30 meets the preset condition or not under the defrosting working condition.
And if the preset condition is met, enabling the refrigerant circulating system to exit the defrosting working condition, such as switching to a refrigerating working condition or a heating working condition. The preset condition here may be that the current lowest temperature of the second heat exchanger 30 exceeds a first preset temperature (e.g., 10 ℃ or the like) for a first preset time period (e.g., 15 minutes or the like).
If the preset condition is not met, a control instruction is sent to the second control valve 60, so that the second control valve 60 switches the refrigerant flow path between the second heat exchanger 30 and the heat exchange device 50 from a straight-through state to a throttling state. In this way, the second control valve 60 corresponds to a throttle unit in the refrigerant circulation circuit, the first heat exchanger 20 and the second heat exchanger 30 correspond to a condenser in the refrigerant circulation circuit, and the heat exchanger 50 corresponds to an evaporator in the refrigerant circulation circuit. The heat absorbed by the heat exchange device 50 is transferred to the second heat exchanger along with the refrigerant circulation loop, so that the second heat exchanger continues to be heated and defrosted.
For a refrigerator or the like which needs to maintain a low temperature in a partial space (for example, a freezing chamber) therein, a defrosting condition, a defrosting duration, and the like have an influence on a defrosting effect and a temperature rise degree of the freezing chamber. In order to reduce the influence of the defrosting process on the freezing chamber, segmented defrosting control can be realized by controlling the condition of entering the defrosting working condition.
Fig. 7 is a schematic diagram illustrating temperature rise comparison between multiple times of defrosting and related art defrosting using an electric heater according to some embodiments of the refrigerant circulation system of the present disclosure. Referring to fig. 7, a curve a is a temperature rise curve of a freezing chamber of a refrigerator for defrosting by using an electric heater, and a curve B is a temperature rise curve of a freezing chamber of a refrigerator including a refrigerant circulation system according to the present embodiment. Relative to the time of the last defrosting completion, the time t of the curve A corresponding to the defrosting condition againA(e.g., 56 hours) later than the time t corresponding to the B curve to re-enter the defrosting modeB(e.g., 20 hours), and the time interval between two adjacent frosting conditions of the B curve is shorter, so that the effect of multiple defrosting is achieved.
In the defrosting process in two modes, the temperature peak value T of the curve AATemperature peak T higher than B curveBAnd T isBCompared with the difference of the temperature values of the freezing chamber before and after defrosting, therefore, the difference of the temperature values of the freezing chamber and the refrigerating chamber before and after defrosting is smaller, and the temperature difference of the freezing chamber and the refrigerating chamber is smallerThe storage conditions have less influence. The electric heater defrosting mode can only reduce the influence by increasing the interval of entering the defrosting working condition due to the over-fast temperature rise, but the defrosting layer is easy to be thicker, and the working effect of the second heat exchanger is influenced. And the hot air defrosting is carried out for multiple times at short time intervals, the influence on the temperature rise of the freezing chamber is small, and the defrosting time of the frost layer is shorter.
Thus, in some embodiments of the present disclosure, the defrosting procedure may further comprise: when the working condition of the refrigerant circulation system is in the cooling working condition or the heating working condition, and when it is determined that the current lowest temperature of the second heat exchanger 30 is lower than a second preset temperature (e.g., -24 ℃ or the like) within a second preset time (e.g., 20 hours or the like), the working condition of the refrigerant circulation system is switched from the cooling working condition or the heating working condition to the defrosting working condition.
The second preset time period may be adjusted according to actual conditions, and accordingly, in some embodiments, the defrosting process further includes: determining the moisture content of the object of temperature control of the second heat exchanger 30 as an evaporator; and adjusting the second preset time according to the moisture content and the defrosting time of the object. Taking the object as a refrigerator freezing chamber as an example, when the moisture content is determined, the air volume size and the humidity and temperature state of the air in the refrigerator body can be judged according to the actual volume of the refrigerator and the temperature and humidity sensor carried by the refrigerator, so that the total moisture content can be calculated. In addition, the moisture content increase amount can be judged according to the times and the duration of opening and closing the door.
The initial value of the second preset time length can be determined according to the calculated total moisture content, and the second preset time length can be adjusted according to the change of the moisture content of the freezing chamber and the actual defrosting time length in the actual defrosting process. For example, if the current defrosting time period (e.g. 3 minutes) is shorter, for example, it is 1/5 which is about the longest defrosting time period (e.g. 15 minutes), which indicates that the frost layer of the second heat exchanger is not thick, the second preset time period before entering the defrosting condition this time can be correspondingly extended, for example, the second preset time period is increased by 5 hours. On the contrary, if the defrosting time of the previous time is longer, the second preset time before entering the defrosting working condition at this time can be shortened.
The time length and the temperature parameters can be determined according to various conditions such as different environmental temperatures, different humidity conditions, different refrigerator volumes, different door opening and closing times and time lengths, no load or full load. For example, the test can be carried out in advance in a laboratory to form a database, and the actual operation parameters can be selected according to the database in a comparison manner, so that the condition of entering the defrosting condition every time can be intelligently judged.
Thus, various embodiments of the present disclosure have been described in detail. Some details that are well known in the art have not been described in order to avoid obscuring the concepts of the present disclosure. It will be fully apparent to those skilled in the art from the foregoing description how to practice the presently disclosed embodiments.
Although some specific embodiments of the present disclosure have been described in detail by way of example, it should be understood by those skilled in the art that the foregoing examples are for purposes of illustration only and are not intended to limit the scope of the present disclosure. It will be understood by those skilled in the art that various changes may be made in the above embodiments or equivalents may be substituted for elements thereof without departing from the scope and spirit of the present disclosure. The scope of the present disclosure is defined by the appended claims.
Claims (15)
1. A refrigerant circulation system, comprising:
a compressor (10);
a first heat exchanger (20) communicated with a discharge port of the compressor (10) through a refrigerant flow path;
the two ends of the second heat exchanger (30) are respectively communicated with the first heat exchanger (20) and a suction port of the compressor (10) through a refrigerant flow path; and
the first control valve (40) is arranged between the refrigerant flow paths between the first heat exchanger (20) and the second heat exchanger (30) and is configured to enable the refrigerant flow paths between the first heat exchanger (20) and the second heat exchanger (30) to be in a throttling state under a refrigerating working condition or a heating working condition and enable the refrigerant flow paths between the first heat exchanger (20) and the second heat exchanger (30) to be in a through state under a defrosting working condition.
2. The coolant circulation system according to claim 1, wherein the first control valve (40) includes: and an electronic expansion valve (41) connected in series to a refrigerant flow path between the first heat exchanger (20) and the second heat exchanger (30), wherein an opening degree of the electronic expansion valve (41) is set to a maximum opening degree under the defrosting condition, and is set to a non-maximum opening degree under the cooling condition or the heating condition.
3. The coolant circulation system according to claim 1, wherein the first control valve (40) includes: the defrosting device comprises a throttling valve (42) and a switching valve (43) which are connected in parallel, wherein the switching valve (43) is configured to conduct a refrigerant flow path where the switching valve (43) is located under the defrosting condition and disconnect the refrigerant flow path where the switching valve (43) is located under the cooling condition or the heating condition.
4. The refrigerant circulation system as claimed in claim 1, further comprising:
a heat exchanger (50) disposed in a refrigerant flow path between the second heat exchanger (30) and a suction port of the compressor (10); and
the second control valve (60) is arranged on a refrigerant flow path between the second heat exchanger (30) and the heat exchange device (50) and is configured to enable the refrigerant flow path between the second heat exchanger (30) and the heat exchange device (50) to be in a straight-through state under the refrigerating working condition or the heating working condition, and enable the refrigerant flow path between the second heat exchanger (30) and the heat exchange device (50) to be in a throttling state when the defrosting effect of the second heat exchanger (30) does not meet the preset condition under the defrosting working condition.
5. The coolant circulation system according to claim 4, wherein the heat exchanging device (50) comprises:
a heat exchange medium container (51) filled with a liquid heat exchange medium for exchanging heat with the environment; and
and the heat exchange sleeve (52) is connected in series on a refrigerant flow path between the second heat exchanger (30) and the suction inlet of the compressor (10), is arranged in the heat exchange medium container (51), and is used for performing heat exchange between the refrigerant circulating in the heat exchange sleeve (52) and the liquid heat exchange medium.
6. The refrigerant circulation system as claimed in claim 5, wherein the heat exchange medium container (51) is a bubble water box, and the liquid heat exchange medium is water.
7. The coolant circulation system of claim 5 wherein the heat exchange jacket (52) is smaller in size than the second heat exchanger (30).
8. The refrigerant circulation system according to claim 5, wherein the first heat exchanger (20) is also disposed in the heat exchange medium container (51) for exchanging heat between the refrigerant circulating in the first heat exchanger (20) and the liquid heat exchange medium.
9. The refrigerant circulation system as claimed in claim 4, further comprising:
a bulb (71) disposed at a lowest temperature position of the second heat exchanger (30) and configured to detect a current lowest temperature of the second heat exchanger (30);
the preset condition is that the current lowest temperature of the second heat exchanger (30) exceeds a first preset temperature within a first preset time.
10. The refrigerant circulation system as claimed in claim 1, further comprising:
a condensation preventing pipe (72) connected in series to a refrigerant flow path between the first control valve (40) and the first heat exchanger (20); and/or
And a filter (73) connected in series in a refrigerant flow path between the first heat exchanger (20) and the first control valve (40).
11. The refrigerant circulation system as claimed in claim 4, further comprising:
and the controller is in signal connection with the first control valve (40) and the second control valve (60), is configured to switch the working condition of the refrigerant circulating system, and sends a control instruction to the first control valve (40) and the second control valve (60) according to the working condition of the refrigerant circulating system.
12. A refrigerator, characterized by comprising:
the refrigerant circulation system according to any one of claims 1 to 11.
13. The refrigerator of claim 12, further comprising: and the second heat exchanger (30) in the refrigerant circulating system is used as an evaporator under the refrigeration working condition to control the temperature of the freezing chamber.
14. An air conditioner, comprising:
the refrigerant circulation system according to any one of claims 1 to 11.
15. The air conditioner according to claim 14, further comprising: and the outdoor unit, wherein a second heat exchanger (30) in the refrigerant circulating system is arranged in the outdoor unit and absorbs heat outdoors as an evaporator under the heating working condition.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122258466.XU CN215724330U (en) | 2021-09-17 | 2021-09-17 | Refrigerant circulation system, refrigerator and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122258466.XU CN215724330U (en) | 2021-09-17 | 2021-09-17 | Refrigerant circulation system, refrigerator and air conditioner |
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| Publication Number | Publication Date |
|---|---|
| CN215724330U true CN215724330U (en) | 2022-02-01 |
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| CN202122258466.XU Active CN215724330U (en) | 2021-09-17 | 2021-09-17 | Refrigerant circulation system, refrigerator and air conditioner |
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| Country | Link |
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| CN (1) | CN215724330U (en) |
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2021
- 2021-09-17 CN CN202122258466.XU patent/CN215724330U/en active Active
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