CN213841111U - Air conditioner - Google Patents
Air conditioner Download PDFInfo
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- CN213841111U CN213841111U CN202022817794.4U CN202022817794U CN213841111U CN 213841111 U CN213841111 U CN 213841111U CN 202022817794 U CN202022817794 U CN 202022817794U CN 213841111 U CN213841111 U CN 213841111U
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Abstract
The utility model discloses an air conditioner, include: at least one indoor unit; at least one outdoor unit module, each outdoor unit module includes: a compressor; a flow path switching device; a plurality of outdoor heat exchangers arranged in a row; the subcooler comprises a main path refrigerant channel and an auxiliary path refrigerant channel, and a first throttling device is arranged between the main path refrigerant channel and the auxiliary path refrigerant channel; a plurality of tube restrictions; a plurality of air-side valves each connecting the flow path switching device and each outdoor heat exchanger; a plurality of second throttling devices arranged between the air side of each outdoor heat exchanger and one end of the first throttling device connected with the auxiliary refrigerant channel; and a defrosting branch line that branches a part of the refrigerant discharged from the compressor and selects one of the plurality of outdoor heat exchangers to allow the refrigerant to flow therein. The utility model discloses incessant when can realizing the defrosting of air conditioning system heats, and can improve the unit efficiency of heating when the defrosting, promotes indoor hot travelling comfort.
Description
Technical Field
The utility model relates to an air conditioner technical field especially relates to an air conditioner.
Background
The technology of the air source heat pump multi-split air conditioner is mature day by day, and the air source heat pump multi-split air conditioner is widely applied to the fields of household and business. The air source heat pump multi-split air conditioner comprises at least one indoor unit and at least one outdoor unit module, wherein when the number of the indoor units is two or more, the indoor units are arranged in parallel, each indoor unit is provided with an indoor heat exchanger and a corresponding indoor fan, when the number of the outdoor unit modules is two or more, the outdoor unit modules are arranged in parallel, each outdoor unit module is provided with a variable frequency compressor, a four-way valve, a throttling element, at least one outdoor heat exchanger and an outdoor fan, which are communicated through a connecting pipeline, and when the number of the outdoor heat exchangers is at least two, the outdoor heat exchangers are arranged in parallel.
The air source heat pump has a big problem in heating operation: when outdoor temperature and humidity reach certain conditions, outdoor heat exchanger air side can frost, and along with the increase of the volume of frosting, the evaporimeter surface can be blockked up gradually, leads to outdoor heat exchanger surface heat transfer coefficient to reduce, and the gas flow resistance increases, seriously influences the machine effect of heating, consequently, the unit needs regularly to defrost.
At present, a reverse defrosting mode is mostly adopted, the reversing is mainly realized by opening a four-way valve, an outdoor unit is switched into a condenser, the defrosting is realized by utilizing the sensible heat and the latent heat of condensation of a high-temperature and high-pressure refrigerant, the defrosting speed is high, and the reliability is good. However, the heating operation is stopped during defrosting, and meanwhile, heat is absorbed from the indoor space due to the fact that the indoor heat exchanger is switched to the evaporator, the indoor temperature is obviously reduced, and indoor thermal comfort is seriously affected.
In order to solve the problems, hot gas bypass defrosting is arranged, namely, the exhaust gas of a compressor is led into an outdoor heat exchanger to be defrosted by using a bypass branch to defrost under the condition that the flow direction of a system refrigerant is not changed.
This defrosting mode has the following disadvantages: 1. the heat converted by the power consumption of the compressor is utilized for defrosting, which belongs to low-pressure defrosting, and the heat is less and the defrosting time is long; 2. when the hot gas bypass defrosting is carried out, low-pressure sensible heat is utilized for defrosting, the temperature is lower, the heat exchange temperature difference with a frost layer is small, and the defrosting reliability is poor; 3. although the flow direction of the refrigerant is not changed during defrosting, the flow rate of the refrigerant of the indoor unit is very small, the system does not supply heat to the indoor unit, the indoor temperature is reduced during defrosting, and the user comfort is poor.
Disclosure of Invention
An embodiment of the utility model provides an air conditioner can realize the incessant heating when air conditioning system defrosts, and the defrosting refrigerant gets into behind the defrosting heat exchanger release heat can through tonifying qi or return vapour and liquid separator behind the subcooler heat transfer, can improve the unit efficiency of heating when the defrosting, promotes indoor thermal comfort.
In order to realize the purpose of the utility model, the utility model adopts the following technical scheme to realize:
the application relates to an air conditioner, its characterized in that includes:
at least one indoor unit;
at least one outdoor unit module, each outdoor unit module includes:
a compressor;
a flow path switching device for switching a flow path of the refrigerant discharged from the compressor;
a plurality of outdoor heat exchangers arranged in parallel;
the subcooler comprises a main path refrigerant channel and an auxiliary path refrigerant channel, wherein a first throttling device is arranged between the main path refrigerant channel and the auxiliary path refrigerant channel;
a plurality of liquid pipe throttling devices which are respectively connected with each outdoor heat exchanger and the main path refrigerant channel;
a plurality of air-side valves each connecting the flow path switching device and each outdoor heat exchanger;
the second throttling devices are arranged between the air side of each outdoor heat exchanger and one end of the first throttling device, which is connected with the auxiliary refrigerant channel;
a defrosting branch path that branches a part of the refrigerant discharged from the compressor and selects one of the plurality of outdoor heat exchangers in response to the branching of the part of the refrigerant and allows the refrigerant to flow therein;
and a control device for controlling the flow path switching devices, the liquid pipe throttling devices, the second throttling devices, the gas side valves, the first throttling devices and the defrosting branches, so that the outdoor heat exchanger to be defrosted is used as a defrosting heat exchanger, and the rest of the outdoor heat exchangers are used as evaporators.
The application relates to an air conditioner, when the air conditioner carries out the defrosting by turns, controlling means control flow path auto-change over device, each liquid pipe throttling arrangement, each second throttling arrangement, each gas side valve, first throttling arrangement and each defrosting branch road, and when outdoor heat exchanger carries out the defrosting, all the other outdoor heat exchangers can form heating cycle with the indoor set, realize the incessant heating of defrosting while, satisfy the incessant heating of air conditioner, indoor temperature can rise fast after the defrosting.
In addition, the air conditioner is provided with the subcooler, when defrosting the defrosting heat exchanger, a part of the refrigerant discharged from the compressor enters the defrosting heat exchanger to release heat for defrosting, then flows out to the auxiliary refrigerant passage of the subcooler for heat exchange through the second throttling device connected with the defrosting heat exchanger, and then enters the air supplementing port or the gas-liquid separator of the compressor, so that the unit heating energy efficiency can be improved during defrosting, and the indoor thermal comfort is improved.
In the application, the main refrigerant channel comprises a first port and a second port, the first port is communicated with the indoor unit, and the second port is connected with the liquid pipe throttling devices of the outdoor heat exchangers;
the auxiliary refrigerant channel comprises a first port and a second port, one end of the first throttling device is connected to the connecting position between the liquid pipe throttling device of each outdoor heat exchanger and the second port of the first heat exchange channel, the other end of the first throttling device is connected to the connecting position between the second throttling device of each outdoor heat exchanger and the second port of the second heat exchange channel, and the first port of the second heat exchange channel is connected with the compressor or the gas-liquid separator.
In the present application, the first throttling means is an electronic expansion valve, a two-way thermostatic expansion valve, or a combination of a throttling capillary tube and a one-way valve.
In the present application, the gas-side valve is an electromagnetic valve or a large-caliber two-way valve.
In the present application, the pipe throttling device and the second throttling device are electronic expansion valves, respectively.
In this application, be provided with on the defrosting branch:
and the air pipe throttling device is connected with the control device and is used for switching on and off the corresponding defrosting branch when the air pipe throttling device controls the on and off.
In the present application, the air pipe throttling device is an electronic expansion valve.
In the application, when the defrosting heat exchanger defrosts, the control device controls the flow path switching device to be powered on; controlling the defrosting branch to enable the refrigerant discharged by the compressor to be communicated with the defrosting heat exchanger; controlling to close a liquid pipe throttling device and a gas side valve which are communicated with the defrosting heat exchanger; and controlling the second throttling device to be opened.
In this application, the outdoor unit module further includes:
the outdoor fans respectively correspond to the outdoor heat exchangers and are connected with the control device, and each outdoor fan and the corresponding outdoor heat exchanger form a wind field;
a separation device for separating adjacent wind farms;
and when the defrosting is performed by turns, the control device controls to close the outdoor fan corresponding to the defrosting heat exchanger.
In the application, when the outdoor heat exchangers exist in each outdoor unit module and are defrosting, the control device controls and increases the rotating speed of the outdoor fans corresponding to the other outdoor heat exchangers which are not defrosting in the outdoor unit module.
Other features and advantages of the present invention will become more apparent from the following detailed description of the invention when read in conjunction with the accompanying drawings.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings without creative efforts.
Fig. 1 is a system structure diagram of an embodiment of an air conditioner according to the present invention;
fig. 2 is a flow chart of the defrosting heat exchanger during defrosting when the embodiment of the air conditioner is in the alternate defrosting mode.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments.
Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative work belong to the protection scope of the present invention. In the description of the present invention, it is to be understood that the terms "center", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like indicate orientations or positional relationships based on those shown in the drawings, and are merely for convenience of description and simplicity of description, and do not indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, are not to be construed as limiting the present invention.
In the description of the present invention, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected. The specific meaning of the above terms in the present invention can be understood in specific cases to those skilled in the art. In the foregoing description of embodiments, the particular features, structures, materials, or characteristics may be combined in any suitable manner in any one or more embodiments or examples.
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 one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.
[ basic operation principle of air conditioner ]
A refrigeration cycle of an air conditioner includes a compressor, a condenser, an expansion valve, and an evaporator. The refrigeration cycle includes a series of processes involving compression, condensation, expansion, and evaporation, and supplies refrigerant to the air that has been conditioned and heat-exchanged.
The compressor compresses a refrigerant gas in a high-temperature and high-pressure state and discharges the compressed refrigerant gas. The discharged refrigerant gas flows into the condenser. The condenser condenses the compressed refrigerant into a liquid phase, and heat is released to the surrounding environment through the condensation process.
The expansion valve expands the liquid-phase refrigerant in a high-temperature and high-pressure state condensed in the condenser into a low-pressure liquid-phase refrigerant. The evaporator evaporates the refrigerant expanded in the expansion valve and returns the refrigerant gas in a low-temperature and low-pressure state to the compressor. The evaporator can achieve a cooling effect by heat-exchanging with a material to be cooled using latent heat of evaporation of a refrigerant. The air conditioner can adjust the temperature of the indoor space throughout the cycle.
The outdoor unit of an air conditioner refers to a portion including a compressor of a refrigeration cycle and includes an outdoor heat exchanger, the indoor unit of an air conditioner includes an indoor heat exchanger, and an expansion valve may be provided in the indoor unit or the outdoor unit of an air conditioner.
The indoor heat exchanger and the outdoor heat exchanger serve as a condenser or an evaporator. When the indoor heat exchanger is used as a condenser, the air conditioner is used as a heater in a heating mode, and when the indoor heat exchanger is used as an evaporator, the air conditioner is used as a cooler in a cooling mode.
[ air-conditioner ]
In the present application, the outdoor unit module is similar to the air conditioning outdoor unit as described above.
The air conditioner of this application design is many online air conditioners.
The air conditioner includes at least one indoor unit, which are arranged in parallel.
Each indoor unit includes indoor heat exchangers 11-1 and 11-2, respectively (i.e., the indoor heat exchangers as described above), and an indoor fan (not shown) for blowing cold or hot air generated by the indoor heat exchangers 11-1 and 11-2, respectively, toward an indoor space.
Of course, the number of indoor units is not limited to the number described above, and the number of indoor heat exchangers and indoor fans in each indoor unit is not limited to the number described above.
The air conditioner comprises at least one outdoor unit module, and all the outdoor unit modules are arranged in parallel.
For example, there are two outdoor unit modules, denoted as outdoor unit modules a and a ', each outdoor unit module a/a' includes a compressor, a flow path switching device, a plurality of outdoor heat exchangers arranged in parallel, a plurality of liquid pipe throttling devices, a plurality of outdoor fans, a defrosting branch, a plurality of gas side valves, a subcooler, and a gas-liquid separator, respectively.
The outdoor unit modules A and A' have the same structure, and the number of the outdoor heat exchangers in each outdoor unit module is at least two.
Referring to fig. 1, a system structure diagram of an air conditioner is shown, which includes an outdoor unit module, the outdoor unit module includes a compressor 1, a check valve 2, a flow path switching device 3, two outdoor heat exchangers 4-1 and 4-2 arranged in parallel, two liquid pipe throttling devices 6-1 and 6-2, two outdoor fans 5-1 and 5-2, a defrosting branch, two gas side valves 20-1 and 20-2, a subcooler 7, and a gas-liquid separator 14.
The flow path switching device 3 switches a flow path of the refrigerant discharged from the compressor 1 to the indoor unit or the outdoor heat exchanger. In the present application, the flow path switching device 3 is a four-way valve having four terminals C, D, S and E.
When the flow switching device 3 is powered off, the default C is connected with the default D, the default S is connected with the default E, the indoor heat exchangers 11-1 and 11-2 are used as evaporators, the outdoor heat exchangers 4-1 and 4-2 are used as condensers, and the air conditioner refrigerates.
When the four-way valve is electrified and reversed, C is connected with S, D is connected with E, so that the indoor heat exchangers 11-1 and 11-2 are used as condensers, the outdoor heat exchangers 4-1 and 4-2 are used as evaporators, and the air conditioner heats.
Referring to fig. 1, the number of the outdoor heat exchangers is the same as that of the outdoor fans and corresponds to one another.
The outdoor unit module comprises a flow switching device 3, an outdoor heat exchanger 4-1/4-2, an outdoor fan 5-1/5-2, a gas side valve 20-1/20-2 connected between a gas pipe of the outdoor heat exchanger 4-1/4-2 and the flow switching device 3, a subcooler 7 and a liquid pipe throttling device 6-1/6-2.
The subcooler 7 may be a plate heat exchanger or a sleeve heat exchanger.
Referring to fig. 1 again, the subcooler 7 includes a first heat exchange channel and a second heat exchange channel, the first heat exchange channel is a main path refrigerant channel, and the second heat exchange channel is an auxiliary path refrigerant channel.
The first heat exchanging channel comprises a first port a1 and a second port a2, the first port a1 is connected to indoor side pipe restrictions 10-1 and 10-2, and the second port a2 is connected to outdoor side pipe restrictions 6-1 and 6-2.
The second heat exchange passage includes a first port b1 and a second port b2, the first port b1 is communicated with the supplementary gas port of the compressor 1 through a solenoid valve 17 or communicated with the gas-liquid separator 14 through a solenoid valve 16, and a first throttling device 15 is provided on a pipe between the second port b2 and the second port a2 of the first heat exchange passage.
One end of the second throttling device 19-1 is connected with the connecting pipe of the main gas pipe of the outdoor heat exchanger 4-1, one end of the second throttling device 19-2 is connected with the connecting pipe of the main gas pipe of the outdoor heat exchanger 4-2, and the other end of the second throttling device 19-1 and the other end of the second throttling device 19-2 are respectively connected with the connecting positions of the first throttling device 15 and the second port b2 of the second heat exchange channel.
The compressor 1, the outdoor heat exchanger 4-1 (4-2), the first heat exchange channel of the subcooler 7 and the indoor heat exchanger 11-1 (11-2) form a refrigerant main circulation loop.
In the present application, the air side valves 20-1 and 20-1 are controllable valves such as solenoid valves and large-diameter two-way valves (e.g., reversible two-way valves with extremely small resistance), and do not have a throttling function.
The liquid pipe throttling device 6-1/6-2, the second throttling device 19-1/19-2 and the indoor side liquid pipe throttling device 10-1/10-2 can adopt an electronic expansion valve, a bidirectional thermal expansion valve and the like.
After a part of the refrigerant discharged from the compressor 1 is branched, it does not flow into the outdoor heat exchangers 4-1 and 4-2 through the defrost branch, respectively, at the same time, i.e., it flows into the outdoor heat exchangers 4-1 and 4-2 by turns.
Referring to fig. 1, a defrost branch 18-1 'is provided on a pipe between a discharge port of a compressor 1 and a liquid pipe side of an outdoor heat exchanger 4-1, and a defrost branch 18-2' is provided on a pipe between a discharge port of the compressor 1 and a liquid pipe side of an outdoor heat exchanger 4-2.
A gas pipe throttling device 18-1 is provided on the defrosting branch 18-1' for allowing part of the refrigerant discharged from the compressor 1 to be throttled to a suitable pressure by the gas pipe throttling device 18-1 to enter the outdoor heat exchanger 4-1 for heat exchange defrosting when being turned on.
A gas pipe throttling device 18-2 is arranged on the defrosting branch 18-2' and is used for throttling part of refrigerant discharged by the compressor 1 to a proper pressure through the gas pipe throttling device 18-2 when the defrosting branch is opened so as to enter the outdoor heat exchange 4-2 for heat exchange defrosting.
In order to avoid that the refrigerant flowing through the indoor heat exchangers 11-1 and 11-2 flows into the outdoor heat exchanger 4-1 or 4-2 after heat exchange when the outdoor heat exchanger 4-1 or 4-2 is defrosted without interruption, one ends of the defrosting branch circuits 18-1 'and 18-2' are respectively formed at the discharge port of the compressor 1 (specifically, the discharge port of the check valve 2), the other end of the defrosting branch circuit 18-1 'is connected to the main liquid pipe of the outdoor heat exchanger 4-1, and the other end of the defrosting branch circuit 18-2' is connected to the main liquid pipe of the outdoor heat exchanger 4-2.
The control device is used for controlling the on-off of the flow path switching device 3, the air side valves 20-1 and 20-2, the liquid pipe throttling devices 6-1 and 6-2, the second throttling devices 19-1 and 19-2 and the defrosting branches 18-1 'and 18-2' in the outdoor unit module (namely, controlling the on-off of the air pipe throttling devices 18-1 and 18-2).
[ operation mode of air conditioner ]
The air conditioner has a normal heating operation mode, a normal cooling operation mode, a reverse defrosting operation mode, and a shift defrosting operation mode.
Heating mode of operation in general
The heating operation mode is not different from the common heating operation mode of the air conditioner.
In some embodiments, when the air conditioner is in the normal heating operation mode, referring to fig. 1, the air side valves 20-1 and 20-2 in the outdoor unit module are both opened, the air pipe throttling devices 18-1 and 18-2 are both closed, the liquid pipe throttling devices 6-1 and 6-2 are both opened, the second throttling devices 19-1 and 19-2 are both closed, the first throttling device 15 is opened, the solenoid valve 17 is opened, the solenoid valve 16 is closed, and the outdoor fan is both opened.
In some embodiments, the flow switching device 3 is electrically switched to connect D and E and C and S, the compressor 1 compresses the low-temperature and low-pressure refrigerant into a high-temperature and high-pressure state, and the refrigerant discharged from the compressor 1 passes through the check valve 2 and D and E and enters the indoor heat exchangers 11-1 and 11-2 through the gas side stop valve 13 and the first extension pipe 12.
The refrigerant is condensed and released heat after heat exchange in the indoor heat exchangers 11-1 and 11-2 to become liquid refrigerant, and then the refrigerant enters the subcooler 7 and is divided into two paths after passing through the indoor machine side throttling devices 10-1 and 10-2, the second extension pipe 9 and the liquid side stop valve 8.
One path enters the low-pressure side of the subcooler 7 after being throttled by the first throttling device 15, exchanges heat with the high-pressure side, and then enters the air supplement port of the compressor 1 through the electromagnetic valve 17.
The other path of refrigerant is throttled to a low-temperature low-pressure gas-liquid two-state through the liquid pipe throttling devices 6-1 and 6-2, the two-phase refrigerant enters the outdoor heat exchangers 4-1 and 4-2 to be evaporated and absorbed and becomes a gas state, the refrigerant discharged from the outdoor heat exchangers 4-1 and 4-2 enters the gas-liquid separator 14 through C and S after passing through the gas side valves 20-1 and 20-2, and is finally sucked into the compressor 1 to be compressed, and the heating cycle is completed.
The refrigerant flow in the normal heating operation mode is in the direction indicated by the broken line arrow in fig. 1.
The outdoor fan is always on throughout the normal heating operation mode.
Normal cooling mode of operation
The normal cooling operation mode is the same as the normal cooling operation mode of the air conditioner.
In some embodiments, when the air conditioner is in a normal cooling operation mode, referring to fig. 1, both of the air side valves 20-1 and 20-2 in the outdoor unit module are opened, both of the air pipe throttles 18-1 and 18-2 are closed, both of the liquid pipe throttles 6-1 and 6-2 are opened, both of the second throttles 19-1 and 19-2 are closed, the first throttle 15 is opened, the solenoid valve 17 is closed, the solenoid valve 16 is opened, and both of the outdoor fans are opened.
The flow path switching device 3 is powered off, the default D and C are communicated, the default E and S are communicated, the compressor 1 compresses the low-temperature and low-pressure refrigerant into a high-temperature and high-pressure state, the refrigerant discharged by the compressor 1 passes through the one-way valves 2, the one-way valves D and C, the air-side valves 20-1 and 20-2 and then enters the outdoor heat exchangers 4-1 and 4-2.
After heat exchange is carried out on the outdoor heat exchangers 4-1 and 4-2, the heat is condensed and released to form liquid refrigerant, and then the liquid refrigerant is divided into two paths through the liquid pipe throttling devices 6-1 and 6-2.
One path of main refrigerant enters the subcooler 7.
The other path of the auxiliary refrigerant enters the subcooler 7 through the first throttling device 15, the main refrigerant exchanges heat with the auxiliary refrigerant, the auxiliary refrigerant enters the gas-liquid separator 14 through the electromagnetic valve 16, and the main refrigerant enters the indoor heat exchangers 11-1 and 11-2 through the liquid side stop valve 8 and the second extension pipe 9 to evaporate and absorb heat and become gaseous.
The refrigerants discharged from the indoor heat exchangers 11-1 and 11-2 pass through the first extension pipe 12, the gas side stop valve 13, and the four-way valves E and S, enter the gas-liquid separator 14, and are finally sucked into the compressor 1 to be compressed, thereby completing the refrigeration cycle.
The outdoor fan is always turned on throughout the normal cooling operation mode.
Reverse defrost mode of operation
When the control device of the air conditioner detects and judges that the outdoor heat exchanger 4-1 and/or 4-2 needs defrosting, the compressor 1 firstly reduces the frequency or directly stops, and the indoor fan and the outdoor fan stop running.
Then, the four-way valve is powered off and reversed, the compressor 1 is started, the outdoor heat exchangers 4-1 and 4-2 are used as condensers to perform defrosting, namely heating of all indoor units is stopped, and defrosting is performed on all the outdoor heat exchangers 4-1 and 4-2.
After defrosting is completed, the compressor 1 is stopped; then, the four-way valve is electrified and reversed, the compressor 1 is restarted, the outdoor fan is restarted, the indoor fan runs according to the cold air prevention program, and the air conditioner reenters the normal heating running mode.
The reverse defrosting operation mode has the advantages of clean defrosting, but also has a plurality of defects (1) that the heating operation is stopped during defrosting, the indoor temperature is obviously reduced, and the use comfort of users is influenced; (2) during defrosting, the flow direction of the refrigerant needs to be changed, and particularly during heating operation after defrosting, because a large amount of refrigerant is stored in the gas-liquid separator 14 during defrosting, the high-low pressure difference is slowly established after defrosting, the heating capacity is low, and the heating cycle capacity is seriously influenced.
Alternate defrost mode of operation
The alternate defrosting operation mode is operated under the conditions that the outdoor heat exchanger needs to be defrosted and the indoor unit still needs to have certain heating capacity, so that the air conditioner can keep heating continuously while the outdoor heat exchanger to be defrosted (namely, the defrosting heat exchanger) is defrosted, the fluctuation of indoor temperature is reduced, and the heating comfort of a user is enhanced.
And in the defrosting process, the defrosting pressure of the defrosting heat exchanger is controlled, the latent heat of the refrigerant is utilized for defrosting, compared with hot gas bypass defrosting, sensible heat defrosting is utilized, the defrosting efficiency is high, the defrosting time is short, the heat acquired by the indoor unit is large, and the user comfort level is high.
In the air conditioner with a single outdoor unit module, when a plurality of outdoor heat exchangers in the single outdoor unit module are defrosted, a plurality of outdoor heat exchangers to be defrosted execute a rotation defrosting operation mode.
In an air conditioner having a plurality of outdoor unit modules, a plurality of outdoor heat exchangers perform sequential rotation defrosting (i.e., only one outdoor heat exchanger performs defrosting at a time), a defrosting process is performed according to defrosting conditions, and defrosting is started, for example, in a preset order, and a control device performs control of the defrosting heat exchanger (i.e., the outdoor heat exchanger that is performing defrosting) and the remaining outdoor heat exchangers in the defrosting process.
In the air conditioner with a plurality of outdoor unit modules, when a plurality of outdoor heat exchangers in the outdoor unit modules are combined and rotated for defrosting (namely, one outdoor heat exchanger in each outdoor unit module is selected to form a plurality of outdoor heat exchange combinations for defrosting at the same time, but two outdoor heat exchangers belonging to the same outdoor unit module are not defrosted at the same time), a defrosting process is started according to defrosting conditions, defrosting is started according to a preset combination sequence for example, and in the defrosting process, a control device executes control over the defrosting heat exchanger and the rest of the outdoor heat exchangers.
The defrosting condition can be judged according to the existing judgment basis, for example, the running time of the compressor and the temperature difference between the ambient temperature and the outdoor unit coil temperature are taken as the criterion.
In the above-described various defrosting processes, if there is a defrosting heat exchanger in the outdoor unit module, the control of the devices related to the defrosting heat exchanger in the outdoor unit module where the defrosting heat exchanger is located is the same, and the remaining devices in the outdoor unit module are maintained in the same state as in the normal heating operation mode. In some embodiments, referring to fig. 1, the defrosting of the outdoor heat exchangers 4-1 and 4-2 in a single outdoor unit module will be described by way of example only.
S1: the process begins.
S2: the air conditioner performs a general heating operation mode.
S3: and judging whether the outdoor heat exchangers 4-1 and 4-2 meet defrosting conditions, if so, entering S4, and if not, continuing to execute a normal heating operation mode of S2.
S4: and sequentially executing a rotation defrosting operation mode aiming at the plurality of defrosting heat exchangers.
The outdoor heat exchangers 4-1 and 4-2 are alternately defrosted according to the frosting amount of the outdoor heat exchangers 4-1 and 4-2 to be defrosted (i.e., defrosting heat exchangers).
The outdoor heat exchangers 4-1 and 4-2 can be sequentially defrosted according to the sequence of the frost formation amount from large to small.
The judgment of the frosting amount can be performed by detecting an index indicative of the frosting amount by a detecting means (not shown), for example, at least one of the heating capacity of the outdoor heat exchangers 4-1 and 4-2, the evaporation temperature of the refrigerant, the indoor unit blow-out temperature, the liquid pipe temperature of the outdoor heat exchanger, and the like, and predicting the frosting amount of the outdoor heat exchangers 4-2 and 4-2 according to the variation of the detection value.
For example, the frost formation amount is determined by the liquid pipe temperature of the outdoor heat exchanger, and the frost formation amount increases as the liquid pipe temperature of the outdoor heat exchanger decreases.
If the frosting amount of the outdoor heat exchanger 4-1 is larger than that of the outdoor heat exchanger 4-2, the outdoor heat exchanger 4-1 should be defrosted first to avoid that the normal operation of the outdoor heat exchanger 4-1 is influenced by excessive frosting. The outdoor heat exchanger 4-2 is in a normal heating operation mode at this time.
That is, the outdoor heat exchanger 4-1 is performed as a defrosting heat exchanger, and the outdoor heat exchanger 4-2 is performed as an evaporator.
After the defrosting of the outdoor heat exchanger 4-1 is completed and the normal heating operation mode is entered, the outdoor heat exchanger 4-2 is defrosted.
That is, the switching of the outdoor heat exchanger 4-1 is performed as a defrosting heat exchanger, and the outdoor heat exchanger 4-2 is performed as an evaporator.
The process of defrosting the defrosting heat exchanger is described as follows.
S41: and controlling the flow path switching device 3 to be powered on, controlling the defrosting branch to enable the refrigerant discharged by the compressor 1 to be communicated with the defrosting heat exchanger, controlling to close a liquid pipe throttling device and an air side valve which are communicated with the defrosting heat exchanger, controlling to open a second throttling device, and executing the rest outdoor heat exchanger as an evaporator.
The outdoor heat exchanger 4-1 in the outdoor unit module is used as a defrosting heat exchanger to execute, and a defrosting process is started, and the outdoor heat exchanger 4-2 is used as an evaporator to execute, so that a normal heating operation process is kept.
And keeping the flow path switching device 3 powered on, controlling an air pipe throttling device 18-1 on the defrosting branch 18-1' to be opened, closing an outdoor fan 5-1 corresponding to the outdoor heat exchanger 4-1, closing the air pipe throttling device 6-1, closing the air side valve 20-1 and closing the first throttling device 15, opening the second throttling device 19-1, and keeping the rest devices in the same state as in the normal heating operation mode.
Referring again to fig. 1, the dotted arrows indicate a refrigerant flow direction when the outdoor heat exchanger 4-1/4-2 is in the normal heating operation mode, and the solid arrows indicate a refrigerant flow direction when the outdoor heat exchanger 4-1 is in the defrosting mode.
When entering the alternate defrosting operation mode, the compressor 1 compresses a low-temperature and low-pressure refrigerant into a high-temperature and high-pressure state, and discharges the high-temperature and high-pressure refrigerant through the check valve 2.
A part of high-temperature and high-pressure refrigerant enters the indoor heat exchangers 11-1 and 11-2 through the flow switching device 3D and E, the gas side stop valve 13 and the first extension pipe 12, is condensed and releases heat after heat exchange in the indoor heat exchangers 11-1 and 11-2 to form liquid refrigerant, and then enters the subcooler 7 through the indoor machine side throttling devices 10-1 and 10-2, the second extension pipe 9 and the liquid side stop valve 8.
Then the gas is throttled to a low-temperature low-pressure gas-liquid two-state through a liquid pipe throttling device 6-2, and then enters an outdoor heat exchanger 4-2 to be evaporated and absorb heat, so that the gas is changed into a gas state.
The refrigerant from the outdoor heat exchanger 4-2 passes through the gas-side valve 20-2, enters the gas-liquid separator 14 through the C and the S, and is finally sucked into the compressor 1 for compression.
The other part of the high-temperature and high-pressure refrigerant is throttled to a proper pressure by the air pipe throttling device 18-1 on the defrosting branch 18-1', and then a part of the refrigerant is shunted to enter the outdoor heat exchanger 4-1 for heat exchange and defrosting.
The defrosted refrigerant enters the low-pressure side of the subcooler 7 after being throttled by the second throttling device 19-1, exchanges heat with the refrigerant at the high-pressure side, enters an air supplement port of the compressor 1 through the electromagnetic valve 17 or enters the gas-liquid separator 14 through the electromagnetic valve 16.
In the present application, when the discharge pressure of the compressor 1 during defrosting is greater than a set value (for example, 3 MPa), the electromagnetic valve 17 is closed and the electromagnetic valve 16 is opened, and at this time, the defrosted refrigerant enters the low-pressure side of the subcooler 7 after being throttled by the second throttling device 19-1, exchanges heat with the high-pressure side refrigerant, enters the gas-liquid separator 14 through the electromagnetic valve 16, and is finally sucked into the compressor 1.
If the exhaust pressure of the compressor 1 is less than or equal to a set value (for example, 3 MPa) during defrosting, the electromagnetic valve 16 is closed and the electromagnetic valve 17 is opened, at this time, the defrosted refrigerant enters the low-pressure side of the subcooler 7 after being throttled by the second throttling device 19-1, exchanges heat with the high-pressure side refrigerant and enters the air supplementing port of the compressor 1 through the electromagnetic valve 17 for supplementing air, so that the enthalpy difference is increased, the unit capacity and the heating energy efficiency are improved, and the indoor thermal comfort of a user is improved.
In the application, the opening degree of the second throttling device 19-1 is controlled and adjusted according to the supercooling degree of the outlet of the outdoor heat exchanger 4-1 and the target supercooling degree range of the outlet, so that the supercooling degree of the outlet of the outdoor heat exchanger 4-1 tends to be maintained in the target supercooling degree range of the outlet; according to the defrosting pressure of the outdoor heat exchanger 4-1 and the target defrosting pressure range, the opening degree of the air pipe throttling device 18-1 is controlled and adjusted to ensure that the defrosting pressure of the defrosting heat exchanger 4-1 tends to be maintained in the target defrosting pressure range, the defrosting pressure is ensured, the outlet of the defrosting heat exchanger is controlled to be in a two-phase state or a liquid state by utilizing latent heat for defrosting, the defrosting time is shortened, the defrosting speed and efficiency are improved, the supercooling degree of the outlet of the outdoor heat exchanger 4-1 is ensured, the unit energy efficiency is improved, and the indoor thermal comfort is improved.
In defrosting the outdoor heat exchanger 4-1, how to control the opening degree of the second throttling device 19-1 and the opening degree of the air pipe throttling device 18-1 is described in detail with reference to fig. 2.
Before entering the defrosting process, it is necessary to set the initial opening degree of the second throttle device 19-1 and the air pipe throttle device 18-1, for example, since the second throttle device 19-1 and the air pipe throttle device 18-1 are both off before defrosting, it is necessary to set the initial opening degree of the air pipe throttle device 25-1 at the time of defrosting (for example, fully open) before defrosting.
S1': the target outlet supercooling degree range of the outdoor heat exchanger 4-1 and the target defrosting pressure range are set.
In the present application, there is a range for the target supercooling degree T1sco, for example, 0 ℃ C. ltoreq. T1 sco. ltoreq.10 ℃.
A target outlet supercooling degree range (Tdsho-. lambda., Tdsho + lambda.) is set, for example, 0. degreeCto.lamda.ltoreq.3 ℃ in accordance with the target supercooling degree T1 sco.
In the present application, the target defrosting pressure Pfo is a function Pfo = f (Ta) of the ambient temperature Ta, and the function Pfo = f (Ta) may be a preset function determined when the air conditioner is commissioned.
When the ambient temperature sensor detects the ambient temperature Ta, the target defrosting pressure Pfo can be obtained from the function f (Ta).
A target defrosting pressure range (Pfo-delta, Pfo + delta) is set based on the target defrosting pressure Pfo, for example, 0MPa < delta < 0.5 MPa.
S2': and calculating the supercooling Te1sc of the outlet of the outdoor heat exchanger 4-1.
The outlet supercooling degree Te1sc of the outdoor heat exchanger 4-1 is calculated by the defrosting pressure Pm (detected by the pressure sensor 222) and the outlet temperature Te1 (detected by the temperature sensor 233) of the outdoor heat exchanger 4-1.
That is, Te1sc = Te1-Tec, where Tec is the corresponding saturation temperature at the defrost pressure Pm, obtainable by prior art inquiry.
S3': comparing whether the outlet supercooling degree Te1sc is in the target outlet supercooling degree range;
s31': if the outlet supercooling degree Te1sc is within the target outlet supercooling degree range, keeping the opening degree of the second throttling device 19-1 and executing to S4'; if not, the opening degree of the second throttle device 19-1 is adjusted, and the process proceeds to S4'.
The process of specifically adjusting the opening degree of the second throttle device 19-1 is described as follows.
S32': if the outlet supercooling degree Te1sc is greater than the upper limit value of the target outlet supercooling degree range, the opening degree of the second throttling means 19-1 is increased by one adjustment step number, and execution is performed to S4'.
That is, the next opening degree EV19-1(n +1) = EV19-1(n) + Δ EV19-1 of the second throttle device 19-1, where Δ EV19-1 is the number of adjustment steps, where the number of adjustment steps may be selected to be 0.1% -10% pls (i.e., the number of steps) of the total opening degree.
S33': if the outlet supercooling degree Te1sc is less than the lower limit value of the target outlet supercooling degree range, the opening degree of the second throttling means 19-1 is decreased by one adjustment step number, and execution is carried out to S4'.
That is, the next opening degree EV19-1(n +1) = EV19-1(n) - Δ EV19-1 of the second throttle device 19-1, where Δ EV19-1 is the number of adjustment steps, where the number of adjustment steps may be selected to be 0.1% -10% pls (i.e., the number of steps) of the total opening degree.
S4': whether the defrost pressure Pm is within the target defrost pressure range is compared, if yes, the amount of refrigerant passing through the defrost branch 18-1 'is maintained and is performed to S42, and if no, the amount of refrigerant passing through the defrost branch 18-1' is adjusted and is performed to S42.
The amount of refrigerant passing through the defrost branch 18-1 'is adjusted by controlling the opening of the air pipe throttling device 18-1 on the defrost branch 18-1', as follows.
S41': if the defrost pressure Pm is within the target defrost pressure range, the opening degree of the air pipe throttle device 18-1 is maintained, and the process goes to S42.
S42': if the defrost pressure Pm is greater than the upper limit value of the target defrost pressure range, the opening degree of the air pipe throttling device 18-1 is decreased by one adjustment step number, and the process goes to S42.
That is, the next opening degree EV18-1(n +1) = EV18-1(n) - Δ EV18-1 of the tracheal throttle device 18-1, where Δ EV18-1 is the number of adjustment steps, where the number of adjustment steps may be selected to be 0.1% -10% pls (i.e., the number of steps) of the total opening degree.
S43': if the defrost pressure Pm is less than the lower limit value of the target defrost pressure range, the opening degree of the air pipe throttling device 18-1 is increased by one adjustment step number, and the process goes to S42.
That is, the next opening degree EV18-1(n +1) = EV18-1(n) + Δ EV18-1 of the tracheal throttle device 18-1, where Δ EV18-1 is the number of adjustment steps, where the number of adjustment steps may be selected to be 0.1% -10% pls (i.e., the number of steps) of the total opening degree.
S42: and judging whether the defrosting is finished or not, if so, exiting the defrosting process, otherwise, returning to S2', and readjusting the opening degrees of the second throttling device 19-1 and the air pipe throttling device 18-1.
As the defrosting end condition, it may be determined whether the defrosting time period T1 reaches a first preset time T1, or whether the outlet temperature Te1 of the outdoor heat exchanger 4-1 is greater than or equal to a first preset temperature Tef (e.g., 2 ℃ < Tef < 20 ℃) and is maintained for a certain time period T; and if one of the two conditions is met, indicating that the defrosting is finished, otherwise, continuing to judge.
Of course, the defrosting end condition is not limited to this, and for example, it may be determined by using whether or not the air pipe temperature Tg of the outdoor heat exchanger 4-1 is equal to or higher than the set temperature Tn and whether or not the suction pressure Ps of the compressor 1 is equal to or higher than the set pressure Po; alternatively, the number of times of adjustment for adjusting the opening degrees of the second throttle device 19-1 and the pipe throttle device 18-1, and the like may be used.
Although S3 'is performed before S4' as described above, the order of S3 'and S4' is not limited, i.e., S4 'may also be performed before S3'.
And after the defrosting of the outdoor heat exchanger 4-1 is finished, the defrosting process is quitted, and then the normal heating operation process is carried out.
The outdoor heat exchanger 4-1 exits the defrosting process and enters a normal heating operation process, which specifically comprises the following steps:
(1) controlling the air pipe throttling device 18-1 on the defrosting branch 18-1' to be closed;
(2) opening an outdoor fan 5-1 corresponding to the outdoor heat exchanger 4-1;
(3) opening the pipe throttling device 6-1;
(4) opening the air side valve 20-1;
(5) the second throttle device 19-1 is closed.
During defrosting, the indoor side throttling devices 10-1 and 10-2 maintain control before defrosting, and the liquid pipe throttling device 6-2 maintains normal heating control, namely, the outlet superheat degree of the outdoor heat exchanger 11-2 is controlled within 0-2 ℃.
Similarly, in order to ensure that the outlet superheat degree of the outdoor heat exchanger 4-1 is controlled when the outdoor heat exchanger 4-1 is in a normal heating operation process after defrosting is finished and the defrosting process is exited, for example, the outdoor fan 5-1 and the liquid pipe throttling device 6-1 are opened, the second throttling device 19-1 and the air pipe throttling device 18-1 are closed, the air side valve 20-1 is opened, and the opening degree of the liquid pipe throttling device 6-1 is controlled, so that the outlet superheat degree of the outdoor heat exchanger 11-1 is within 0-2 ℃.
Thereafter, the outdoor heat exchanger 4-2 serves as a defrosting heat exchanger to enter a defrosting process, and the outdoor heat exchanger 4-1 serves as an evaporator to maintain a normal heating operation process.
Keeping the flow path switching device 3 powered on, controlling the air pipe throttling device 18-2 on the defrosting branch 18-2' to open, closing the outdoor fan corresponding to the outdoor heat exchanger 4-2, closing the liquid pipe throttling device 6-2, closing the air side valve 20-2, keeping the first throttling device 15 closed, opening the second throttling device 19-2, and keeping the rest devices in the same state as in the normal heating operation mode.
The defrosting process of the outdoor heat exchanger 4-2 is referred to as the defrosting process of the outdoor heat exchanger 4-1.
When the outdoor heat exchanger 4-2 is defrosted, the outdoor heat exchanger 4-1 performs a normal heating operation process.
In the air conditioner with the single outdoor unit module, after the outdoor heat exchangers 4-1 and 4-2 are alternately defrosted for multiple times, a reverse defrosting operation mode is performed to thoroughly defrost the outdoor heat exchangers 4-1 and 4-2. Of course, the reverse defrost mode of operation may be selected under other conditions.
[ separation of wind field ]
Since the corresponding outdoor fan of the outdoor heat exchanger 4-2 is kept in operation when the outdoor heat exchanger 4-1 performs defrosting, in order to avoid the situation that the wind field generated by the outdoor fan blows over the outdoor heat exchanger 4-1 and the outdoor heat exchanger 4-1 cannot effectively defrost, in the present application, referring to fig. 1, a separating device 101 for separating the wind field is provided (see patent document No. 202010279447.2 and entitled "outdoor unit of air conditioner" in this section).
In the present application, the outdoor fans are respectively and independently controlled by the control device, and the outdoor heat exchanger 4-1 and the outdoor fan thereof form a first wind field, and the outdoor heat exchanger 4-2 and the outdoor fan thereof form a second wind field, and the partition device 101 is used to separate the first wind field and the second wind field.
That is, when the outdoor fan corresponding to the outdoor heat exchanger 4-1 operates and the outdoor fan corresponding to the outdoor heat exchanger 4-2 does not operate, it does not blow the wind to the outdoor heat exchanger 4-2, and when the outdoor fan corresponding to the outdoor heat exchanger 4-2 operates and the outdoor fan corresponding to the outdoor heat exchanger 4-1 does not operate, it does not blow the wind to the outdoor heat exchanger 4-1.
Thus, when the outdoor heat exchanger 4-1 performs defrosting, since the partition 101 separates the first wind field and the second wind field, the first wind field is not affected even if the outdoor fan of the outdoor heat exchanger 4-2 is still operated.
Therefore, the situation that the air blows over the surface of the outdoor heat exchanger 4-1 when defrosting is carried out is effectively avoided, the situation that the defrosting cannot be effectively carried out due to overlarge condensation load when the outdoor temperature is low is further prevented, and uninterrupted heating of a full-temperature area can be realized.
In addition, when the outdoor fan corresponding to the outdoor heat exchanger 4-1 stops running (namely the outdoor heat exchanger 4-1 is defrosting), the rotating speed of the outdoor fan corresponding to the outdoor heat exchanger 4-2 can be properly increased, the heating effect is further enhanced, the indoor temperature fluctuation is reduced, and the heating capacity of the air conditioner and the heating comfort of users are greatly improved.
And when the outdoor heat exchanger 4-1 exits the defrosting process and enters a normal heating operation process, the outdoor fan corresponding to the outdoor heat exchanger 4-1 is correspondingly opened and the outdoor fan of the outdoor heat exchanger 4-2 is closed.
The above embodiments are only used to illustrate the technical solution of the present invention, and not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be apparent to those skilled in the art that modifications may be made to the embodiments described in the foregoing embodiments, or that equivalents may be substituted for elements thereof; such modifications and substitutions do not depart from the spirit and scope of the present invention, which is claimed.
Claims (10)
1. An air conditioner, comprising:
at least one indoor unit;
at least one outdoor unit module, each outdoor unit module includes:
a compressor;
a flow path switching device for switching a flow path of the refrigerant discharged from the compressor;
a plurality of outdoor heat exchangers arranged in parallel;
the subcooler comprises a main path refrigerant channel and an auxiliary path refrigerant channel, wherein a first throttling device is arranged between the main path refrigerant channel and the auxiliary path refrigerant channel;
a plurality of liquid pipe throttling devices which are respectively connected with each outdoor heat exchanger and the main path refrigerant channel;
a plurality of air-side valves each connecting the flow path switching device and each outdoor heat exchanger;
the second throttling devices are arranged between the air side of each outdoor heat exchanger and one end of the first throttling device, which is connected with the auxiliary refrigerant channel;
a defrosting branch path that branches a part of the refrigerant discharged from the compressor and selects one of the plurality of outdoor heat exchangers in response to the branching of the part of the refrigerant and allows the refrigerant to flow therein;
and a control device for controlling the flow path switching devices, the liquid pipe throttling devices, the second throttling devices, the gas side valves, the first throttling devices and the defrosting branches, so that the outdoor heat exchanger to be defrosted is used as a defrosting heat exchanger, and the rest of the outdoor heat exchangers are used as evaporators.
2. The air conditioner according to claim 1,
the main refrigerant channel comprises a first port and a second port, the first port is communicated with the indoor unit, and the second port is connected with the liquid pipe throttling devices of the outdoor heat exchangers;
the auxiliary refrigerant channel comprises a first port and a second port, one end of the first throttling device is connected to the connecting position between the liquid pipe throttling device of each outdoor heat exchanger and the second port of the first heat exchange channel, the other end of the first throttling device is connected to the connecting position between the second throttling device of each outdoor heat exchanger and the second port of the second heat exchange channel, and the first port of the second heat exchange channel is connected with the compressor or the gas-liquid separator.
3. The air conditioner according to claim 2,
the first throttling device is an electronic expansion valve, a two-way thermal expansion valve or a combination of a throttling capillary tube and a one-way valve.
4. The air conditioner according to claim 1,
the gas side valve is an electromagnetic valve or a large-caliber two-way valve.
5. The air conditioner according to claim 1,
the liquid pipe throttling device and the second throttling device are electronic expansion valves respectively.
6. The air conditioner according to claim 1, wherein the defrosting branch is provided with:
and the air pipe throttling device is connected with the control device and is used for switching on and off the corresponding defrosting branch when the air pipe throttling device controls the on and off.
7. The air conditioner according to claim 6,
the air pipe throttling device is an electronic expansion valve.
8. The air conditioner according to any one of claims 1 to 7,
when the defrosting heat exchanger defrosts, the control device controls the flow path switching device to be powered on; controlling the defrosting branch to enable the refrigerant discharged by the compressor to be communicated with the defrosting heat exchanger; controlling to close a liquid pipe throttling device and a gas side valve which are communicated with the defrosting heat exchanger; and controlling the second throttling device to be opened.
9. The air conditioner of any one of claims 1 to 7, wherein the outdoor unit module further comprises:
the outdoor fans respectively correspond to the outdoor heat exchangers and are connected with the control device, and each outdoor fan and the corresponding outdoor heat exchanger form a wind field;
a separation device for separating adjacent wind farms;
and when the defrosting is performed by turns, the control device controls to close the outdoor fan corresponding to the defrosting heat exchanger.
10. The air conditioner according to claim 9,
when the outdoor heat exchangers in the outdoor unit modules are defrosting, the control device controls and increases the rotating speed of the outdoor fans corresponding to the other outdoor heat exchangers which are not defrosting in the outdoor unit modules.
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| CN202022817794.4U CN213841111U (en) | 2020-11-30 | 2020-11-30 | Air conditioner |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113739275A (en) * | 2021-08-03 | 2021-12-03 | 青岛海信日立空调系统有限公司 | Air conditioning system |
| CN113916041A (en) * | 2021-10-18 | 2022-01-11 | 珠海格力电器股份有限公司 | Fin structure, heat exchange device and air conditioner |
| CN114165844A (en) * | 2021-11-26 | 2022-03-11 | 青岛海信日立空调系统有限公司 | Air conditioner |
-
2020
- 2020-11-30 CN CN202022817794.4U patent/CN213841111U/en active Active
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113739275A (en) * | 2021-08-03 | 2021-12-03 | 青岛海信日立空调系统有限公司 | Air conditioning system |
| CN113739275B (en) * | 2021-08-03 | 2022-12-13 | 青岛海信日立空调系统有限公司 | Air conditioning system |
| CN113916041A (en) * | 2021-10-18 | 2022-01-11 | 珠海格力电器股份有限公司 | Fin structure, heat exchange device and air conditioner |
| CN114165844A (en) * | 2021-11-26 | 2022-03-11 | 青岛海信日立空调系统有限公司 | Air conditioner |
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