CN114322106B - Air conditioning system - Google Patents
Air conditioning system Download PDFInfo
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- CN114322106B CN114322106B CN202210000948.1A CN202210000948A CN114322106B CN 114322106 B CN114322106 B CN 114322106B CN 202210000948 A CN202210000948 A CN 202210000948A CN 114322106 B CN114322106 B CN 114322106B
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Abstract
The invention relates to an air conditioning system, which is characterized in that the state and the quantity of a refrigerant stored in an outdoor electronic expansion valve and an indoor electronic expansion valve in front and behind a liquid accumulator and the state and the quantity of the refrigerant stored in a liquid pipe are controlled by the outdoor electronic expansion valve and the indoor electronic expansion valve, so that the quantity of the refrigerant in the system is regulated, the outdoor electronic expansion valve is firstly regulated to meet the condition that the supercooling degree of an outlet of an outdoor heat exchanger is within a target supercooling degree setting range in a refrigerating mode, and then the indoor electronic expansion valve is regulated to meet the condition that the superheating degree of an outlet of the indoor heat exchanger is within the target superheating degree setting range; when the indoor heat exchanger is used for heating, the indoor electronic expansion valve is firstly adjusted to meet the condition that the supercooling degree of the outlet of the indoor heat exchanger is within a target supercooling degree setting range, and then the outdoor electronic expansion valve is adjusted to meet the condition that the exhaust superheat degree of the compressor is within the target exhaust superheat degree setting range. The invention can solve the influence of different piping lengths on the refrigerant quantity of the system and ensure the performance of the unit.
Description
Technical Field
The invention relates to the technical field of air temperature regulation, in particular to an air conditioning system which can adapt to various online pipe lengths.
Background
The existing air conditioning system generally comprises an indoor unit and an outdoor unit, and the indoor unit and the outdoor unit are connected through a pipeline. Because of different installation environments, the lengths of the connecting pipelines between the indoor units and the outdoor units are different, so that the refrigerant quantity required to be filled in different pipeline lengths is different in order to achieve the best use effect. However, when the device is installed outside a factory, the condition of little filling or even no filling of the refrigerant often occurs, and the inaccurate filling amount of the refrigerant can cause the performance reduction of the unit.
Disclosure of Invention
The invention provides an air conditioning system, which solves the technical problem that the unit performance is reduced due to inaccurate refrigerant filling quantity of the existing air conditioning system.
In order to achieve the above purpose, the invention adopts the following technical scheme:
an air conditioning system comprises an outdoor unit and an indoor unit which are connected through a first pipeline and a second pipeline;
the outdoor unit comprises a compressor, a four-way valve, an outdoor heat exchanger, an outdoor electronic expansion valve and a liquid reservoir which are sequentially connected, wherein the liquid reservoir is connected with the first pipeline, and the four-way valve is connected with the second pipeline;
the indoor unit comprises a plurality of indoor modules which are connected in parallel, each indoor module comprises an indoor electronic expansion valve and an indoor heat exchanger which are connected in series, the indoor electronic expansion valve is connected with the first pipeline, and the indoor heat exchanger is connected with the second pipeline;
the air conditioning system further comprises a control module, wherein the control module is used for controlling the four-way valve to be switched to a refrigerating mode or a heating mode and controlling all electronic expansion valves to be adjusted to set opening degrees; the control module is further used for firstly adjusting the outdoor electronic expansion valve to meet the condition that the supercooling degree of the outlet of the outdoor heat exchanger is within a target supercooling degree setting range in a refrigerating mode, and then adjusting the indoor electronic expansion valve to meet the condition that the superheat degree of the outlet of the indoor heat exchanger is within the target superheat degree setting range; when the indoor heat exchanger is used for heating, the indoor electronic expansion valve is firstly adjusted to meet the condition that the supercooling degree of the outlet of the indoor heat exchanger is within a target supercooling degree setting range, and then the outdoor electronic expansion valve is adjusted to meet the condition that the exhaust superheat degree of the compressor is within the target exhaust superheat degree setting range.
Compared with the prior art, the technical scheme of the invention has the following technical effects: according to the air conditioning system, the state and the refrigerant quantity of the stored refrigerant and the state and the refrigerant quantity of the refrigerant stored in the liquid pipe are controlled through the outdoor electronic expansion valve and the indoor electronic expansion valve which are arranged in front of and behind the liquid accumulator, so that the refrigerant quantity in the system is regulated, the outdoor electronic expansion valve is firstly regulated to meet the condition that the supercooling degree of an outlet of the outdoor heat exchanger is in a target supercooling degree setting range in a refrigerating mode, and then the indoor electronic expansion valve is regulated to meet the condition that the superheating degree of an outlet of the indoor heat exchanger is in the target superheating degree setting range; when the indoor heat exchanger is used for heating, the indoor electronic expansion valve is firstly adjusted to meet the condition that the supercooling degree of the outlet of the indoor heat exchanger is within a target supercooling degree setting range, and then the outdoor electronic expansion valve is adjusted to meet the condition that the exhaust superheat degree of the compressor is within the target exhaust superheat degree setting range. The invention can solve the influence of different piping lengths on the refrigerant quantity of the system and ensure the performance of the unit.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required for the description of the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
Fig. 1 is a schematic diagram of an air conditioning system according to an embodiment of the present invention.
Fig. 2 is a schematic diagram of a cooling mode of an air conditioning system according to an embodiment of the present invention.
Fig. 3 is a pressure-enthalpy diagram of an air conditioning system according to an embodiment of the present invention corresponding to a short-pipe and long-pipe cooling mode.
Fig. 4 is a schematic diagram of a heating mode of an air conditioning system according to an embodiment of the present invention.
Fig. 5 is a pressure-enthalpy diagram of an air conditioning system according to an embodiment of the present invention corresponding to a heating mode of a short pipe and a long pipe.
FIG. 6 is a schematic diagram of a mode selection control according to an embodiment of the present invention.
Fig. 7 is a control diagram of a cooling mode according to an embodiment of the present invention.
Fig. 8 is a heating mode control diagram according to an embodiment of the present invention.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be directly connected or indirectly connected through an intermediate medium. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art. In the description of the above embodiments, 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 the like, 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 defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present invention, unless otherwise indicated, the meaning of "a plurality" is two or more.
An air conditioning system includes an outdoor unit and an indoor unit connected through a first pipe 10 and a second pipe 11.
The outdoor unit comprises a compressor 1, a four-way valve 4, an outdoor heat exchanger 5, an outdoor electronic expansion valve 8 and a liquid reservoir 6 which are sequentially connected, wherein the liquid reservoir 6 is connected with a first pipeline 10, and the four-way valve 4 is connected with a second pipeline 11.
The indoor unit comprises a plurality of indoor modules which are connected in parallel, each indoor module comprises an indoor electronic expansion valve 9-i and an indoor heat exchanger 7-i which are connected in series, the indoor electronic expansion valve 9-i is connected with a first pipeline 10, and the indoor heat exchanger 7-i is connected with a second pipeline 11.
The air conditioning system also comprises a control module, wherein the control module is used for controlling the four-way valve 4 to be switched to a refrigerating mode or a heating mode and controlling all electronic expansion valves to be adjusted to set opening; the control module is further used for firstly adjusting the outdoor electronic expansion valve 8 to meet the condition that the supercooling degree of the outlet of the outdoor heat exchanger 5 is within a target supercooling degree setting range in a refrigerating mode, and then adjusting the indoor electronic expansion valve 9-i to meet the condition that the superheat degree of the outlet of the indoor heat exchanger 7-i is within the target superheat degree setting range; when the indoor heat exchanger is used for heating, the indoor electronic expansion valve 9-i is firstly adjusted to meet the condition that the supercooling degree of the outlet of the indoor heat exchanger 7-i is within the target supercooling degree setting range, and then the outdoor electronic expansion valve 8 is adjusted to meet the condition that the exhaust superheat degree of the compressor is within the target exhaust superheat degree setting range.
The control module is also used for adjusting the indoor electronic expansion valve 9-i when the supercooling degree of the outlet of the indoor heat exchanger 7-i is in the target supercooling degree setting range in the heating mode so as to uniformly control the supercooling degree of the outlet of the indoor heat exchanger 7-i.
The air conditioning system further includes:
compressor discharge pressure sensor P1 for detecting compressor discharge pressure P p1 ；
Compressor discharge temperature sensor T1 for detecting compressor discharge temperature T t1 ；
A temperature sensor e1, which is positioned between the outdoor heat exchanger 5 and the outdoor electronic expansion valve 8, for detecting the temperature T e1 ；
A plurality of temperature sensors li positioned between the indoor electronic expansion valve 9-i and the indoor heat exchanger 7-i for detecting the temperature T li ；
A plurality of temperature sensors gi, which are positioned between the indoor heat exchanger 7-i and the second pipeline 11, for detecting the temperature T gi ；
A control module for determining a compressor discharge pressure P p1 Corresponding saturation temperature T sat ；
The control module is also used for not adjusting the electronic expansion valve when the first condition and the second condition are met in the refrigeration mode; at the position ofWhen the first condition is met and the second condition is not met, the opening of the ith indoor electronic expansion valve 9-i is adjusted until the first condition and the second condition are met; adjusting the opening degree of the outdoor electronic expansion valve 8 until the first condition is met when the first condition is not met; the first condition is: the supercooling degree delta T of the outlet of the outdoor heat exchanger 5 sc =T sat -T e1 At the target supercooling degree DeltaT sc0 Setting a range; the second condition is: ith superheat DeltaT shi = T gi -T li At the target superheat DeltaT sh0 Setting a range;
the control module is also used for not adjusting the electronic expansion valve when the third condition and the fourth condition are met in the heating mode; when the third condition is satisfied and the fourth condition is not satisfied, adjusting the opening degree of the outdoor electronic expansion valve 8 until the third condition and the fourth condition are satisfied; when the third condition is not met, the opening of the ith indoor electronic expansion valve 9-i is adjusted until the third condition is met; the third condition is: the i-th indoor heat exchanger 7-i outlet supercooling degree DeltaT sci =T sat -T li At the target supercooling degree DeltaT sc10 Setting a range; the fourth condition is: compressor discharge superheat deltat dSH =T t1 -T sat At the target exhaust superheat degree T dsh0 The setting range.
The control module is further used for judging whether the fourth condition is met when the third condition and the fifth condition are met in the heating mode, and adjusting the opening of the ith indoor electronic expansion valve 9-i until the third condition and the fifth condition are met when the third condition is not met; the fifth condition is: the i-th indoor heat exchanger 7-i outlet supercooling degree DeltaT sci =T sat -T li Average outlet supercooling degree delta T with indoor heat exchanger 7-i scave The difference is within a set range.
The control module is used for controlling the supercooling degree delta T of the outlet of the outdoor heat exchanger 5 in the refrigerating mode sc At the target supercooling degree DeltaT sc0 When the upper limit of the range is set, the opening of the outdoor electronic expansion valve 8 is controlled to be increased; supercooling degree delta T of outdoor heat exchanger sc At the target supercooling degree DeltaT sc0 When the lower limit of the set range is lower than the preset lower limit, the control is performedThe opening of the electronic expansion valve 8 outside the control chamber is reduced.
The control module is used for controlling the ith superheat degree delta T in the refrigeration mode shi At the target superheat DeltaT sh0 When the upper limit of the range is set above, the opening of the electronic expansion valve 9-i in the control room is increased; at the ith superheat DeltaT shi At the target superheat DeltaT sh0 When the lower limit of the set range is not more than, the opening of the electronic expansion valve 9-i in the control room is reduced.
The control module is used for controlling the supercooling degree delta T of the outlet of the ith indoor heat exchanger 7-i in the heating mode sci At the target supercooling degree DeltaT sc10 When the upper limit of the range is set above, the opening of the electronic expansion valve 9-i in the control room is increased; the supercooling degree DeltaT at the outlet of the ith indoor heat exchanger 7-i sci At the target supercooling degree DeltaT sc10 When the lower limit of the set range is not more than, the opening of the electronic expansion valve 9-i in the control room is reduced.
The control module is used for controlling the superheat delta T of the exhaust gas of the compressor in the refrigerating mode dSH At the target exhaust superheat degree T dsh0 When the upper limit of the range is set, the opening of the outdoor electronic expansion valve 8 is controlled to be increased; at the compressor discharge superheat deltat dSH At the target exhaust superheat degree T dsh0 When the lower limit of the set range is not higher than, the opening degree of the control outdoor electronic expansion valve 8 is reduced.
The control module is used for controlling the supercooling degree delta T of the outlet of the ith indoor heat exchanger 7-i in the heating mode sci Average outlet supercooling degree delta T with indoor heat exchanger 7-i scave When the difference is above the upper limit of the set range, the opening of the indoor electronic expansion valve 9-i is controlled to be increased; the supercooling degree DeltaT at the outlet of the ith indoor heat exchanger 7-i sci Average outlet supercooling degree DeltaT with indoor heat exchanger (7-i) scave When the difference is less than the lower limit of the set range, the opening of the electronic expansion valve (9-i) in the control room is reduced.
The control module is used for controlling the opening degree of the electronic expansion valve to be adjusted and then maintaining the set time.
The air conditioning system is suitable for the occasion that one outdoor unit corresponds to a plurality of indoor units or the occasion that one outdoor unit corresponds to one indoor unit. When one outdoor unit corresponds to a plurality of indoor units, the plurality of indoor heat exchangers can cope with different indoor load conditions.
As shown in fig. 1, the air conditioning system is composed of an outdoor unit and an indoor unit. The outdoor unit includes: the device comprises a compressor 1, an oil separator 2, a gas-liquid separator 3, a four-way valve 4, an outdoor heat exchanger 5, a medium-pressure liquid accumulator 6 and an outdoor electronic expansion valve 8; the indoor unit includes: indoor heat exchanger 7-1/7-2/… 7-i, indoor electronic expansion valve 9-1/9-2/. 9-i; the indoor unit and the outdoor unit are connected by a first pipe (liquid pipe) 10 and a second pipe (gas pipe) 11. The sensor comprises: the outdoor unit supercooling section outlet temperature sensor e1, the compressor exhaust port temperature sensor t1, the first indoor unit air pipe temperature sensor g1, the first indoor unit liquid pipe temperature sensor l1, the second indoor unit air pipe temperature sensor g2, the second indoor unit liquid pipe temperature sensor l2, the ith indoor unit air pipe temperature sensor gi, the ith indoor unit liquid pipe temperature sensor li and the compressor exhaust port pressure sensor p1.
The operation of the refrigeration mode of this embodiment is as shown in fig. 2: the high-temperature and high-pressure refrigerant gas discharged from the compressor 1 flows out through the oil separator 2 (the refrigerating machine oil separated by the oil separator 2 directly returns to the air inlet of the compressor 1 through the oil return capillary 12); the gaseous refrigerant separated from the oil enters the outdoor heat exchanger 5 through the four-way valve 4, and in the short-piping refrigeration cycle system, the refrigerant amount in the system is large, and the refrigerant becomes a supercooled liquid state with high temperature and high pressure after sufficient heat exchange. Because the supercooling degree of the outdoor heat exchanger is larger, the outdoor electronic expansion valve 8 is kept fully open or at a larger opening degree, and the refrigerant entering the medium-pressure liquid accumulator 6 is a high-pressure supercooling liquid refrigerant, so that more refrigerant is stored; the supercooled liquid refrigerant leaving from the liquid accumulator 6 flows through the liquid pipe 10 to enter two indoor units in two paths, is throttled into low-temperature low-pressure two-phase refrigerant by the indoor electronic expansion valves 9-1 and 9-2 respectively, and the two-phase refrigerant is evaporated into low-temperature low-pressure superheated gaseous refrigerant in the indoor heat exchangers 7-1 and 7-2; the low-temperature low-pressure superheated gaseous refrigerant flows out of the indoor heat exchanger, returns to the gas-liquid separator 3 through the gas pipe 11 and the four-way valve 4, and then flows into the air suction port of the compressor 1, thus completing the refrigeration cycle.
During long piping, the refrigerant is absent in the system, the outdoor electronic expansion valve 8 is used for throttling and keeping a smaller opening, the supercooling degree of the heat exchanger of the outdoor unit is guaranteed, meanwhile, the refrigerant entering the liquid reservoir 6 is a medium-pressure two-phase refrigerant, less refrigerant is stored, and the refrigerant is released into the system. The medium-pressure two-phase refrigerant leaving from the liquid storage 6 flows through the liquid pipe 10 to enter two indoor units in two paths, is throttled into low-temperature low-pressure two-phase refrigerant by the indoor electronic expansion valves 9-1 and 9-2 respectively, and is evaporated into low-temperature low-pressure superheated gaseous refrigerant in the indoor heat exchangers 7-1 and 7-2; the low-temperature low-pressure superheated gaseous refrigerant flows out of the indoor heat exchanger, returns to the gas-liquid separator 3 through the gas pipe 11 and the four-way valve 4, and then flows into the air suction port of the compressor 1, thus completing the refrigeration cycle.
The corresponding pressure enthalpy diagram of the refrigeration operation in this embodiment is shown in fig. 3: the exhaust corresponding state point of the compressor is B; condensing the outdoor heat exchanger, and then changing the state point from B to C; for a short piping, the supercooling degree of the outdoor heat exchanger is large, the outdoor electronic expansion valve 8 is kept fully opened or at a large opening degree, and the refrigerant enters the medium-pressure liquid reservoir 6 in a supercooling liquid state from the state point C to the state point D through the outdoor electronic expansion valve 8; the inlet and outlet pressure loss of the medium-pressure liquid storage device is very small, and the point D and the point E can be approximately set as the same state point; the supercooled liquid refrigerant passes through the connecting liquid pipe 10 between the outdoor unit and the indoor unit, and the state point is from E to F; through the indoor electronic expansion valves 9-1 and 9-2, the state point is changed from F to G, and the supercooled liquid refrigerant with high temperature and high pressure is changed into a two-phase refrigerant with low temperature and low pressure; the state point of the low-temperature low-pressure two-phase refrigerant is changed from G to state point H after the indoor heat exchangers 7-1 and 7-2 evaporate; the overheated gaseous refrigerant returns to the gas-liquid separator 3 through the connecting air pipe 11 and the four-way valve 4 between the indoor unit and the outdoor unit, and because the pressure loss of the section is smaller, the outlet H point of the indoor evaporator and the inlet A point of the gas-liquid separator can be approximately set as the same state point; the superheated gaseous refrigerant then flows into the suction port of the compressor 1, thus completing the refrigeration cycle.
For the long piping, when the control of the embodiment is adopted, the refrigerant is absent in the system, the throttle of the outdoor electronic expansion valve 8 keeps a small opening degree, and the supercooling degree of the heat exchanger of the outdoor unit is ensured. The supercooled liquid refrigerant passes through the outdoor electronic expansion valve 8, the state point is from C to D, and the refrigerant enters the medium-pressure liquid reservoir 6 in a medium-pressure two-phase state; the inlet and outlet pressure loss of the medium-pressure liquid storage device is very small, and the point D and the point E can be approximately set as the same state point; the two-phase refrigerant passes through the connecting liquid pipe 10 between the outdoor unit and the indoor unit, and the state point is from E to F; through the indoor electronic expansion valves 9-1 and 9-2, the state point is changed from F to G, and the medium-pressure two-phase state refrigerant is changed into low-temperature low-pressure two-phase state refrigerant; for long piping, when ordinary control is adopted, the refrigerant is absent in the system, the outdoor electronic expansion valve 8 is fully opened, and the heat exchanger of the outdoor unit has no supercooling degree. The gas-liquid two-phase refrigerant passes through the outdoor electronic expansion valve 8, the state point is from C '. Fwdarw.state point D', and the refrigerant enters the medium-pressure liquid reservoir 6 in a two-phase state; the inlet and outlet pressure loss of the medium-pressure liquid storage device is very small, and the point D 'and the point E' can be approximately set as the same state point; the two-phase refrigerant passes through the connecting liquid pipe 10 between the outdoor unit and the indoor unit, and the state point is from E '. Fwdarw.state point F'; through the indoor electronic expansion valves 9-1 and 9-2, the state point is changed from F '. Fwdarw.state point G', and the medium-pressure two-phase state refrigerant is changed into low-temperature low-pressure two-phase state refrigerant; the low-temperature low-pressure two-phase state refrigerant is changed into superheated gaseous refrigerant after being evaporated in the indoor heat exchangers 7-1 and 7-2, and the state point is changed from G to H; the overheated gaseous refrigerant returns to the gas-liquid separator 3 through the connecting air pipe 11 and the four-way valve 4 between the indoor unit and the outdoor unit, and because the pressure loss of the section is smaller, the outlet H point of the indoor evaporator and the inlet A point of the gas-liquid separator can be approximately set as the same state point; the superheated gaseous refrigerant then flows into the suction port of the compressor 1, thus completing the refrigeration cycle. Compared with the long piping connection of the common control, the embodiment controls the supercooling degree to be increased when the long piping is connected, the dryness of the refrigerant to be reduced, the refrigerating capacity to be increased, the refrigerating effect to be enhanced and the comfort to users to be improved.
The heating mode of this embodiment operates as shown in fig. 4: the high-temperature high-pressure gaseous refrigerant discharged from the compressor 1 flows out through the oil separator 2 (the refrigerating machine oil separated by the oil separator 2 directly returns to the air suction port of the compressor 1 through the oil return capillary tube 12); the high-temperature high-pressure gaseous refrigerant flowing out of the oil separator 2 enters two indoor units 7-1 and 7-2 in two paths through the four-way valve 4 and the air pipe 11. For the short-piping refrigeration cycle system, the amount of refrigerant in the system is large, the high-temperature and high-pressure gaseous refrigerant is condensed into the high-temperature and high-pressure supercooled liquid refrigerant after fully exchanging heat, and because the supercooling degree of the indoor heat exchanger is large, the indoor electronic expansion valves 9-1 and 9-2 keep full opening or large opening, and the refrigerant in the liquid inlet pipe 10 and the medium-pressure liquid accumulator 6 is the high-pressure supercooled liquid refrigerant, so that the stored refrigerant is large. The supercooled liquid refrigerant leaving from the accumulator 6 is throttled by the outdoor electronic expansion valve 8 into a low-temperature low-pressure two-phase state refrigerant, and the two-phase state refrigerant is evaporated into a low-temperature low-pressure superheated gaseous refrigerant in the outdoor heat exchanger 5; the low-temperature low-pressure superheated gaseous refrigerant flows out of the outdoor heat exchanger, returns to the gas-liquid separator 3 through the four-way valve 4, and then flows into the air suction port of the compressor 1, thus completing the heating cycle of the present invention.
During long piping, the refrigerant is absent in the system, the supercooling degree of the heat exchanger of the indoor unit is guaranteed by keeping the throttle of the indoor electronic expansion valves 9-1 and 9-2 at a smaller opening degree, and meanwhile, the refrigerant entering the liquid pipe 10 and the medium-pressure liquid storage 6 is a medium-pressure two-phase refrigerant, less refrigerant is stored, and the refrigerant is released into the system. The medium-pressure two-phase refrigerant leaving from the liquid accumulator 6 is throttled by the outdoor electronic expansion valve 8 into a low-temperature low-pressure two-phase state refrigerant, and the two-phase state refrigerant is evaporated into a low-temperature low-pressure superheated gaseous refrigerant in the outdoor heat exchanger 5; the low-temperature low-pressure superheated gaseous refrigerant is discharged from the outdoor heat exchanger, returns to the gas-liquid separator 3 through the four-way valve 4, and then flows into the air suction port of the compressor 1, thus completing the heating cycle of the present invention.
The pressure enthalpy diagram corresponding to the heating operation in this embodiment is shown in fig. 6: the corresponding state point of the exhaust gas of the compressor is B, the state is close to the inlet point H of the indoor heat exchanger, and the two points are set as the same state point; the state point of the indoor heat exchanger after condensation is changed from H to a state point G; for a short piping, the supercooling degree of the indoor heat exchanger is larger, the indoor electronic expansion valves 9-1 and 9-2 are kept fully opened or have larger opening degrees, and the state point is changed from G to the state point F through the indoor electronic expansion valves 9-1 and 9-2; the refrigerant passes through a connecting liquid pipe 10 between the outdoor unit and the indoor unit in a supercooled liquid state and enters the medium-pressure liquid storage 6, and the state point is from F to E; the inlet and outlet pressure loss of the medium-pressure liquid storage device is very small, and the E point and the D point can be approximately set as the same state point; the supercooled liquid refrigerant flowing out of the liquid accumulator is throttled by the outdoor electronic expansion valve 8, and the state point is changed from D to C, and the supercooled liquid refrigerant with high temperature and high pressure is changed into a two-phase refrigerant with low temperature and low pressure; the state point of the low-temperature low-pressure two-phase state refrigerant after the outdoor heat exchanger 5 evaporates is from C to state point A; the superheated gaseous refrigerant then flows into the suction port of the compressor 1, thus completing the heating cycle.
For the long piping, when the control of the embodiment is adopted, the refrigerant is absent in the system, the throttle of the indoor electronic expansion valves 9-1 and 9-2 is kept at a small opening degree, and the supercooling degree of the indoor unit heat exchanger is ensured. The supercooling liquid refrigerant throttles through the indoor electronic expansion valves 9-1 and 9-2, the state point is from G to state point F, the refrigerant passes through the connecting liquid pipe 10 between the outdoor unit and the indoor unit in a medium-pressure two-phase state and enters the medium-pressure liquid storage 6, and the state point is from F to state point E; the inlet and outlet pressure loss of the medium-pressure liquid storage device is very small, and the E point and the D point can be approximately set as the same state point; the refrigerant from the liquid accumulator passes through the outdoor electronic expansion valve 8 to be throttled, the state point is changed from D to C, and the medium-pressure two-phase state refrigerant is changed into low-temperature low-pressure two-phase state refrigerant; (for long piping, when the common control is adopted, the refrigerant is absent in the system, the indoor electronic expansion valves 9-1 and 9-2 are fully opened, the outlet of the indoor unit heat exchanger is not supercooled, the gas-liquid two-phase state refrigerant passes through the indoor electronic expansion valves 9-1 and 9-2, the state point is from the G '. Fwdarw.state point F ', the refrigerant passes through the connecting liquid pipe 10 between the outdoor unit and the indoor unit in a two-phase state and enters the medium-pressure liquid storage 6, the state point is from the F '. Fwdarw.state point E '; the pressure loss of the inlet and the outlet of the medium-pressure liquid storage is very small, the E ' point and the D ' point can be approximately set to be the same state point, the refrigerant coming out of the liquid storage is throttled through the outdoor electronic expansion valve 8, the state point is from the D '. Fwdarw.state point C ', the medium-pressure two-phase state refrigerant is changed into low-temperature low-pressure two-phase state refrigerant, and the low-temperature low-pressure two-phase state refrigerant is evaporated by the outdoor heat exchanger 5, and the state point is from the C ' -. State point A; the superheated gaseous refrigerant then flows into the suction port of the compressor 1, thus completing the heating cycle. Compared with the long piping connection of the common control, the embodiment controls the supercooling degree to be increased when the long piping is connected, the refrigerant dryness to be reduced, the heating quantity to be increased, the heating effect to be enhanced and the comfort to the user to be improved.
Next, a control flow of the air conditioning system will be described, and fig. 6 is a flowchart for determining a system operation mode. Fig. 7 is a flowchart of a cooling operation mode, and fig. 8 is a flowchart of a heating operation mode.
In fig. 6, the control system determines an operation mode in step S1. The control of the step S2 to the cooling mode or the control of the step S3 to the heating mode is performed according to the selection of the user.
In the cooling mode control of fig. 7, in step S4, the control system switches the four-way valve 4 to the cooling mode (as shown in fig. 3), and changes the outdoor electronic expansion valve 8 and the indoor electronic expansion valves 9-1, 9-2 … -i to the initial opening degrees. In the cooling mode, the outdoor electronic expansion valve 8 is supercooled in steps S5 and S6, and the indoor electronic expansion valve 9-1/9-2/… 9-i is superheating controlled in steps S7 and S8.
In step S5, the control system determines the pressure P detected by the pressure sensor P1 p1 Corresponding saturation temperature T sat Temperature T detected by temperature sensor e1 e1 The difference DeltaT between the temperatures of (2) sc (ΔT sc =T sat - T e1 ) Whether or not to be at target supercooling degree DeltaT sc0 If the processing is within the set range (yes in S5), the processing proceeds to step S7; if the set range is out (no in S5), the process proceeds to step S6. In step S6, the outdoor heat exchanger supercooling degree DeltaT sc At the target supercooling degree DeltaT sc0 Setting the upper limit of the range, and opening the outdoor electronic expansion valve 8; supercooling degree delta T of outdoor heat exchanger sc At the target supercooling degree DeltaT sc0 In the case that the lower limit of the range is set, the outdoor electronic expansion valve 8 is throttled; after the opening degree of the outdoor electronic expansion valve 8 is changed, the control system maintains the opening degree of the outdoor electronic expansion valve 8 for an appropriate time, and again performs the determination in step S5.
In step S7, the temperature T detected by the temperature sensor g1 g1 Temperature T detected by temperature sensor l1 l1 The difference is the outlet superheat delta T of the indoor heat exchanger 7-1 SH1 （ΔT SH1 = T g1 - T l1 ) Temperature T detected by temperature sensor g2 g2 Temperature T detected by temperature sensor l2 l2 The difference is the outlet superheat delta T of the indoor heat exchanger 7-2 SH2 （ΔT SH2 = T g2 - T l2 ) The control system determines the temperature T detected by the temperature sensor gi gi Temperature T detected by temperature sensor li li The difference is the outlet superheat delta T of the indoor heat exchanger 7-i SHi （ΔT SHi = T gi - T li ) Whether or not to be at target superheat deltat SH0 Is within a set range of (2). If the degree of superheat DeltaT SHi If the control is within the set range (yes in S7), ending the control; if the set range is out (no in S7), the process proceeds to step S8. In step S8, the control system controls the operation to control the target superheat DeltaT SH0 If the setting range of the valve is less than the lower limit, the indoor electronic expansion valve 9-i is throttled, and if the setting range is more than the upper limit, the indoor electronic expansion valve 9-i is opened; after the opening degree of the indoor electronic expansion valve 9-i is changed, the control system maintains the opening degree of the indoor electronic expansion valve 9-i for an appropriate time, and then the determination is performed again in step S5.
By the control, the supercooling degree delta T can be reduced sc And the superheat degree delta T SHi When the system is operated in a refrigeration mode, the system refrigerant quantity of the short piping is sufficient, the supercooling degree is large enough, the outdoor electronic expansion valve 8 is kept in a fully opened or open state, supercooled liquid refrigerant enters the medium-pressure liquid reservoir 6 and the connecting liquid pipe 10 and stores more refrigerant quantity in the liquid reservoir and the liquid pipe, and the refrigerant quantity in the system is correspondingly reduced; the system refrigerant quantity of the long piping is insufficient, the supercooling degree is smaller or the supercooling degree is not enough, the outdoor electronic expansion valve 8 throttles, the medium-pressure two-phase refrigerant enters the medium-pressure liquid reservoir 6 and the connecting liquid pipe 10 and stores less refrigerant quantity in the liquid reservoir and the liquid pipe, and the refrigerant quantity in the system is correspondingly increased; when the long and short piping is replaced, the refrigeration cycle device changes the density of the refrigerant entering the medium-pressure liquid storage tank 6 and the liquid pipe 10 by whether the outdoor electronic expansion valve 8 throttles, thereby changing the quality of the refrigerant stored in the liquid storage tank and the liquid pipe, and finally adjusting the refrigerant quantity in the system to adapt to the pairing system with different piping lengthsAnd the requirement of optimal refrigerant quantity is unified, and the device is suitable for different requirements of different parts on the refrigerant quantity under different online schemes of different working conditions.
In fig. 6, the control system determines an operation mode in step S1. And controlling the heating mode in the step S3 according to the selection of a user. In the heating mode control of fig. 7, in step S104, the control system switches the four-way valve 4 to the heating mode (as shown in fig. 4), and changes the outdoor electronic expansion valve 8 and the indoor electronic expansion valves 9-1, 9-2 … -i to the initial opening degrees. In the heating mode, the degree of supercooling of the indoor electronic expansion valve 9-1/9-2/… -i is controlled in steps S105 and S106, the degree of supercooling uniformity of the indoor electronic expansion valve 9-1/9-2/… 9-i is controlled in steps S107 and S108, and the degree of superheat of the compressor discharge of the outdoor electronic expansion valve 8 is controlled in steps S109 and S110.
In step S105, the pressure P detected by the pressure sensor P1 p1 Corresponding saturation temperature T sat Temperature T detected by temperature sensor l1 l1 The temperature difference of (2) is the supercooling degree delta T of the outlet of the indoor heat exchanger sc1 (ΔT sc1 =T sat- T l1 ) Pressure P detected by pressure sensor P1 p1 Corresponding saturation temperature T sat Temperature T detected by temperature sensor l2 l2 The difference in temperature is the supercooling degree DeltaT sc2 (ΔT sc2 =T sat- T l2 ) The control system determines the pressure P detected by the pressure sensor P1 p1 Corresponding saturation temperature T sat With the temperature T detected by the temperature sensor li on the ith indoor unit li The difference DeltaT between the temperatures of (2) sci (ΔT sci =T sat- T li ) Whether or not to be at target supercooling degree DeltaT sc10 Within the range, if within the set range (yes in S105), the process advances to step S107; if the set range is out (no in S105), the process advances to step S106. In step S106, the indoor heat exchanger supercooling degree Δt sci At the target supercooling degree DeltaT sc10 When the upper limit of the range is set, the indoor electronic expansion valve 9-i is opened; supercooling degree delta T of indoor heat exchanger sci At the target supercooling degree DeltaT sc10 When the lower limit of the range is set to be less than or equal to the lower limit, the indoor space is closedThe electronic expansion valve 9-i throttles; after the opening degree of the indoor electronic expansion valve 9-i is changed, the control system maintains the opening degree of the indoor electronic expansion valve 9-i for an appropriate time, and then the determination is performed again in step S105.
In step S107, the average outlet supercooling degree Δt of the i indoor units scave =(ΔT sc1 +ΔT sc2 +…ΔT sci ) I, the control system judges the outlet supercooling degree delta T of the ith indoor unit sci From the average outlet subcooling degree DeltaT scave Whether the difference is at [ -1,1]If within the set range (yes in S107), advancing the process to step S109; if it is out of the set range (no in S107), the process advances to step S108. In step S108, the outlet supercooling degree Δt of the i-th indoor unit sci From the average outlet subcooling degree DeltaT scave When the difference is greater than 1, opening the indoor electronic expansion valve 9-i; outlet supercooling degree delta T of ith indoor unit sci From the average outlet subcooling degree DeltaT scave Throttling the indoor electronic expansion valve 9-i when the difference is smaller than-1; after the opening degree of the indoor electronic expansion valve 9-i is changed, the control system maintains the opening degree of the indoor electronic expansion valve 9-i for an appropriate time, and then the determination is performed again in step S105.
In step S109, the control system determines the temperature T detected by the temperature sensor T1 t1 With pressure P detected by pressure sensor P1 p1 Corresponding saturation temperature T sat The difference is the superheat delta T of the compressor dSH （ΔT dSH = T t1 - T sat ) Whether or not the target exhaust superheat degree DeltaT is reached dSH0 Is within a set range of (2). If the degree of superheat DeltaT of the exhaust gas dSH If the control is within the set range (yes in S109), the control is ended; if the set range is out (no in S109), the process proceeds to step S110. In step S110, the control system sets the target exhaust superheat T dSH0 The outdoor electronic expansion valve 8 is throttled when the lower limit of the set range is below, and the outdoor electronic expansion valve 8 is opened when the upper limit is above; after changing the opening of the outdoor electronic expansion valve 8, the control system maintains the opening of the outdoor electronic expansion valve 8 for a proper time, and then passes through the steps againStep S105 performs determination.
By the control, the supercooling degree delta T of all indoor units can be controlled sci The indoor units are maintained in the target range, and the supercooling degree control difference of all the indoor units is small, so that the phenomenon of drift of the refrigerants of all the indoor units can be effectively prevented; the control also controls the compressor discharge superheat delta T dSH And the system is maintained in the target range, and the system reliability is ensured. When the heating mode is operated, the system refrigerant quantity of the short piping is sufficient, the supercooling degree is large enough, the indoor electronic expansion valve 9-i is kept in a full-open or opening state, supercooled liquid refrigerant enters the connecting liquid pipe 10 and the medium-pressure liquid storage 6 and stores more refrigerant quantity in the liquid pipe and the liquid storage, and the refrigerant quantity in the system is correspondingly reduced; the system refrigerant quantity of the long piping is insufficient, the supercooling degree is smaller or the supercooling degree is not, the indoor electronic expansion valve 9-i throttles, the medium-pressure two-phase refrigerant enters the connecting liquid pipe 10 and the medium-pressure liquid storage device 6 and stores less refrigerant quantity in the liquid pipe and the liquid storage device, and the refrigerant quantity in the system is correspondingly increased; when the heating mode of the refrigeration cycle device is operated in the replacement of long and short piping, the density of the refrigerant entering the liquid pipe 10 and the medium-pressure liquid storage tank 6 is changed through whether the indoor electronic expansion valve 9-i throttles, so that the quality of the refrigerant stored in the liquid pipe and the medium-pressure liquid storage tank is changed, and finally the refrigerant quantity in the system can be regulated to adapt to the requirements of different piping lengths on the optimal refrigerant quantity of the system and the different requirements of different components on the refrigerant quantity under different online schemes of different working conditions.
The foregoing is merely illustrative of the present invention, and the present invention is not limited thereto, and any changes or substitutions easily contemplated by those skilled in the art within the scope of the present invention should be included in the scope of the present invention. Therefore, the protection scope of the invention is subject to the protection scope of the claims.
Claims (8)
1. An air conditioning system includes an outdoor unit and an indoor unit connected by a first pipe (10) and a second pipe (11); it is characterized in that the method comprises the steps of,
the outdoor unit comprises a compressor (1), a four-way valve (4), an outdoor heat exchanger (5), an outdoor electronic expansion valve (8) and a liquid reservoir (6) which are sequentially connected, wherein the liquid reservoir (6) is connected with the first pipeline (10), and the four-way valve (4) is connected with the second pipeline (11);
the indoor unit comprises a plurality of indoor modules which are connected in parallel, each indoor module comprises an indoor electronic expansion valve (9-i) and an indoor heat exchanger (7-i) which are connected in series, the indoor electronic expansion valve (9-i) is connected with the first pipeline (10), and the indoor heat exchanger (7-i) is connected with the second pipeline (11);
the air conditioning system further comprises a control module, wherein the control module is used for controlling the four-way valve (4) to be switched to a refrigerating mode or a heating mode and controlling all electronic expansion valves to be adjusted to set opening degrees; the control module is further used for firstly adjusting the outdoor electronic expansion valve (8) to meet the condition that the supercooling degree of the outlet of the outdoor heat exchanger (5) is within a target supercooling degree setting range in a refrigerating mode, and then adjusting the indoor electronic expansion valve (9-i) to meet the condition that the superheating degree of the outlet of the indoor heat exchanger (7-i) is within the target superheating degree setting range; when the indoor heat exchanger is used for heating, the indoor electronic expansion valve (9-i) is firstly adjusted to meet the condition that the outlet supercooling degree of the indoor heat exchanger (7-i) is within a target supercooling degree setting range, and then the outdoor electronic expansion valve (8) is adjusted to meet the condition that the exhaust superheat degree of the compressor is within the target exhaust superheat degree setting range;
the air conditioning system further includes:
a compressor discharge pressure sensor P1 for detecting the compressor discharge pressure P p1 ；
Compressor discharge temperature sensor T1 for detecting said compressor discharge temperature T t1 ；
A temperature sensor e1, which is positioned between the outdoor heat exchanger (5) and the outdoor electronic expansion valve (8) and is used for detecting the temperature T e1 ；
A plurality of temperature sensors li, which are positioned between the indoor electronic expansion valve (9-i) and the indoor heat exchanger (7-i) and are used for detecting the temperature T li ；
A plurality of temperature sensors gi, which are positioned between the indoor heat exchanger (7-i) and the second pipeline (11) and are used for detecting the temperature T gi ；
A control module for determining the compressor discharge pressure P p1 Corresponding saturation temperature T sat ；
The control module is also used for not adjusting the electronic expansion valve when the first condition and the second condition are met in the refrigeration mode; when the first condition is met and the second condition is not met, the opening degree of the ith indoor electronic expansion valve (9-i) is adjusted until the first condition and the second condition are met; when the first condition is not met, the opening degree of the outdoor electronic expansion valve (8) is adjusted until the first condition is met; the first condition is: the supercooling degree delta T of the outlet of the outdoor heat exchanger (5) sc =T sat -T e1 At the target supercooling degree DeltaT sc0 Setting a range; the second condition is: ith superheat DeltaT shi = T gi -T li At the target superheat DeltaT sh0 Setting a range;
the control module is also used for adjusting the opening of the ith indoor electronic expansion valve (9-i) until the third condition is met when the third condition is not met in the heating mode; when the third condition is met and the fifth condition is not met, adjusting and adjusting the opening of the ith indoor electronic expansion valve (9-i) until the third condition and the fifth condition are met; when the third condition and the fifth condition are met and the fourth condition is not met, adjusting the opening degree of the outdoor electronic expansion valve (8) until the third condition, the fifth condition and the fourth condition are met; when the third condition, the fourth condition and the fifth condition are met, the electronic expansion valve is not regulated; the third condition is: the outlet supercooling degree delta T of the ith indoor heat exchanger (7-i) sci =T sat -T li At the target supercooling degree DeltaT sc10 Setting a range; the fourth condition is: compressor discharge superheat deltat dSH =T t1 -T sat At the target exhaust superheat degree T dsh0 Setting a range; the fifth condition is: the outlet supercooling degree delta T of the ith indoor heat exchanger (7-i) sci =T sat -T li Average outlet supercooling degree DeltaT with indoor heat exchanger (7-i) scave The difference is within a set range.
2. An air conditioning system according to claim 1, characterized in that the control module is further configured to adjust the indoor electronic expansion valve (9-i) to control uniformity of the indoor heat exchanger (7-i) outlet subcooling when the indoor heat exchanger (7-i) outlet subcooling is within a target subcooling setting range in heating mode.
3. An air conditioning system according to claim 1, characterized in that the control module is adapted to, in the cooling mode, at the outdoor heat exchanger (5) outlet subcooling Δt sc At the target supercooling degree DeltaT sc0 When the upper limit of the range is set to be more than or equal to the upper limit of the range, controlling the opening degree of the outdoor electronic expansion valve (8) to be increased; supercooling degree delta T of outdoor heat exchanger sc At the target supercooling degree DeltaT sc0 And when the lower limit of the set range is less than or equal to the lower limit of the set range, controlling the opening degree of the outdoor electronic expansion valve (8) to be reduced.
4. The air conditioning system of claim 1, wherein the control module is configured to, in the cooling mode, provide a degree of superheat Δt at an i-th degree of superheat shi At the target superheat DeltaT sh0 When the upper limit of the range is set to be more than or equal to the upper limit of the range, controlling the opening of the indoor electronic expansion valve (9-i) to be increased; at the ith superheat DeltaT shi At the target superheat degree delta Ts h0 And when the lower limit of the set range is less than or equal to the lower limit of the set range, controlling the opening degree of the indoor electronic expansion valve (9-i) to be reduced.
5. An air conditioning system according to claim 1, characterized in that the control module is adapted to, in heating mode, at the i-th indoor heat exchanger (7-i) outlet subcooling Δt sci At the target supercooling degree DeltaT sc10 When the upper limit of the range is set to be more than or equal to the upper limit of the range, controlling the opening of the indoor electronic expansion valve (9-i) to be increased; the supercooling degree DeltaT at the outlet of the ith indoor heat exchanger (7-i) sci At the target supercooling degree DeltaT sc10 And when the lower limit of the set range is less than or equal to the lower limit of the set range, controlling the opening degree of the indoor electronic expansion valve (9-i) to be reduced.
6. The air conditioning system of claim 1, wherein the control module is configured to, in the cooling mode, provide a degree of superheat at the compressor discharge dSH At the target exhaust superheat degree T dsh0 When the upper limit of the range is set to be more than or equal to the upper limit of the range, controlling the opening degree of the outdoor electronic expansion valve (8) to be increased; at the compressor discharge superheat deltat dSH At the target exhaust superheat degree T dsh0 And when the lower limit of the set range is less than or equal to the lower limit of the set range, controlling the opening degree of the outdoor electronic expansion valve (8) to be reduced.
7. An air conditioning system according to claim 1, characterized in that the control module is adapted to control the degree of supercooling Δt at the outlet of the ith indoor heat exchanger (7-i) during heating mode sci Average outlet supercooling degree DeltaT with indoor heat exchanger (7-i) scave When the difference is above the upper limit of the set range, controlling the opening of the indoor electronic expansion valve (9-i) to be increased; the supercooling degree DeltaT at the outlet of the ith indoor heat exchanger (7-i) sci Average outlet supercooling degree DeltaT with indoor heat exchanger (7-i) scave When the difference is less than the lower limit of the set range, the opening degree of the indoor electronic expansion valve (9-i) is controlled to be reduced.
8. The air conditioning system according to any of claims 3-7, wherein the control module is configured to control the opening degree of the electronic expansion valve to be adjusted for a set time.
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| CN202210000948.1A CN114322106B (en) | 2022-01-04 | 2022-01-04 | Air conditioning system |
| PCT/CN2022/130394 WO2023103675A1 (en) | 2021-12-07 | 2022-11-07 | Air conditioner |
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| CN202210000948.1A CN114322106B (en) | 2022-01-04 | 2022-01-04 | Air conditioning system |
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| WO2023103675A1 (en) * | 2021-12-07 | 2023-06-15 | 青岛海信日立空调系统有限公司 | Air conditioner |
| CN114893902B (en) * | 2022-04-25 | 2023-09-19 | 青岛海信日立空调系统有限公司 | Air conditioning system and control method thereof |
| WO2023207050A1 (en) * | 2022-04-25 | 2023-11-02 | 青岛海信日立空调系统有限公司 | Air-conditioning system and control method for air-conditioning system |
| WO2024040915A1 (en) * | 2022-08-22 | 2024-02-29 | 青岛海信日立空调系统有限公司 | Air conditioner |
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