CN115727447A - Refrigerant circulating system, control method thereof and air conditioning equipment - Google Patents
Refrigerant circulating system, control method thereof and air conditioning equipment Download PDFInfo
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- CN115727447A CN115727447A CN202211427338.6A CN202211427338A CN115727447A CN 115727447 A CN115727447 A CN 115727447A CN 202211427338 A CN202211427338 A CN 202211427338A CN 115727447 A CN115727447 A CN 115727447A
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Abstract
The invention relates to a refrigerant circulating system, a control method thereof and air conditioning equipment, wherein the refrigerant circulating system comprises: a compressor; the gas-liquid separator is connected with the air suction port of the compressor; an outdoor heat exchanger; the energy storage equipment is configured to be switched between a first state and a second state, in the first state, the energy accumulator is communicated with the exhaust port of the compressor to store heat, in the second state, the first refrigerant inlet and outlet of the energy accumulator is communicated with the indoor heat exchanger to introduce the refrigerant to be evaporated, and the second refrigerant inlet and outlet of the energy accumulator is communicated with the gas-liquid separator to convey the evaporated refrigerant to the gas-liquid separator; and the controller is in signal connection with the energy storage equipment, so that when a first preset condition for judging that the circulating refrigerant in the condensation circulating system is insufficient is met, the energy storage equipment is switched to a second state, and the liquid refrigerant in the gas-liquid separator is evaporated by using the refrigerant heated by the energy accumulator.
Description
Technical Field
The invention relates to the technical field of refrigerant refrigeration, in particular to a refrigerant circulating system, a control method thereof and air conditioning equipment.
Background
After the air conditioner stops for a period of time in a low-temperature environment and operates in a defrosting or oil-returning mode, a large amount of refrigerant in the system is in a liquid state and is stored in a gas-liquid separator, an outdoor heat exchanger and other pipelines. When the heating cycle is started, the circulation quantity of the refrigerant is small, the running frequency of the compressor is also lower, and the time required for the liquid refrigerant to circulate in the system again is further prolonged. In this period, the heating effect is poor, low-temperature protection easily occurs to cause shutdown, the compressor sucks liquid refrigerant to cause liquid impact, and meanwhile, the lubricating effect of the refrigerant oil in the compressor is also reduced.
Disclosure of Invention
The invention aims to provide a refrigerant circulating system, a control method thereof and air conditioning equipment, which aim to solve the problem that the quantity of liquid refrigerants of an air conditioner after defrosting or oil return operation is large in the prior art.
According to an aspect of an embodiment of the present invention, there is provided a refrigerant circulation system including:
the compressor is used for providing a refrigerant to be condensed for the indoor heat exchanger;
the gas-liquid separator is connected with the air suction port of the compressor;
the outdoor heat exchanger is connected with the indoor heat exchanger to introduce the refrigerant to be evaporated and is connected with the gas-liquid separator to convey the evaporated refrigerant to the gas-liquid separator;
the energy storage equipment comprises an energy accumulator which is respectively connected with the compressor, the gas-liquid separator and the indoor heat exchanger, and is configured to be switched between a first state and a second state, wherein in the first state, the energy accumulator is communicated with an exhaust port of the compressor to store heat, in the second state, a first refrigerant inlet and outlet of the energy accumulator is communicated with the indoor heat exchanger to introduce a refrigerant to be evaporated, and a second refrigerant inlet and outlet of the energy accumulator is communicated with the gas-liquid separator to convey the evaporated refrigerant to the gas-liquid separator; and
and the controller is in signal connection with the energy storage equipment so as to switch the energy storage equipment to a second state when a first preset condition for judging that the refrigerant participating in circulation in the condensation circulation system is insufficient is met, so that the liquid refrigerant in the gas-liquid separator is evaporated by the refrigerant heated by the energy accumulator.
In some embodiments, the first preset condition comprises:
compressor discharge temperature T D -outdoor ambient temperature T env Less than or equal to the predetermined temperature difference A 1 (ii) a And/or
High pressure saturation temperature T H Outdoor ambient temperature T env Less than or equal to the predetermined temperature difference B 1 (ii) a And/or
Temperature T of gaseous refrigerant output by gas-liquid separator S Low pressure saturation temperature T L Less than or equal to the predetermined temperature difference C 1 。
In some embodiments, the refrigerant circulation system further includes a first control valve disposed in a pipe connecting the indoor heat exchanger and the outdoor heat exchanger,
the controller is in signal connection with the first control valve, so that when the first preset condition is met and the energy storage equipment is switched to the second state, the first control valve is closed to prevent the refrigerant condensed in the indoor heat exchanger from being conveyed to the outdoor heat exchanger.
In some embodiments, the controller is configured to open the first control valve when a second preset condition for determining that the liquid refrigerant in the gas-liquid separator is reduced to a predetermined amount is satisfied.
In some embodiments, the second predetermined condition comprises:
compressor discharge temperature T D -outdoor ambient temperature T env Greater than a predetermined temperature differenceA 2 Wherein the predetermined temperature difference A 2 The predetermined temperature difference A 1 (ii) a And/or
High pressure saturation temperature T H -outdoor ambient temperature T env Greater than a predetermined temperature difference B 2 Wherein the predetermined temperature difference B 2 > said predetermined temperature difference B 1 (ii) a And/or
Temperature T of gaseous refrigerant output by gas-liquid separator S Low pressure saturation temperature T L Greater than a predetermined temperature difference C 2 (ii) a And/or
Supercooling degree delta T of indoor heat exchanger sub > predetermined supercooling degree DeltaT 1 。
In some embodiments, the controller is further configured to obtain a heating load Q of the indoor heat exchanger in And according to heating load Q in Adjusting the predetermined temperature difference C 2 Wherein the heating load Q in At a predetermined temperature difference C 2 And (4) positively correlating.
In some embodiments, the controller is further configured to:
heating load Q of indoor heat exchanger in ＞Q 2 At a predetermined temperature difference C 2 Set to a predetermined temperature difference C 21 ；
Heating load Q of indoor heat exchanger in ∈(Q 1 ,Q 2 ]At a predetermined temperature difference C 2 Set to a predetermined temperature difference C 22 ；
Heating load Q of indoor heat exchanger in ≤Q 1 At a predetermined temperature difference C 2 Set to a predetermined temperature difference C 23 ，
Wherein, C 21 ＞C 22 ＞C 23 。
In some embodiments, the accumulator apparatus includes a second control valve disposed in a conduit connecting the indoor heat exchanger and the accumulator;
the controller is in signal connection with the second control valve to close the second control valve when a third preset condition for judging that the liquid refrigerant in the outdoor heat exchanger is reduced to a preset amount is met.
In some embodiments, the third preset condition comprises:
compressor discharge temperature T D Outdoor ambient temperature T env > predetermined temperature difference A 2 Wherein the predetermined temperature difference A 2 The predetermined temperature difference A 1 (ii) a And/or
High pressure saturation temperature T H -outdoor ambient temperature T env Greater than a predetermined temperature difference B 2 Wherein the predetermined temperature difference B 2 > said predetermined temperature difference B 1 (ii) a And/or
The temperature TS-low pressure saturation temperature TL of the gaseous refrigerant output by the gas-liquid separator is larger than the preset temperature difference C 2 (ii) a And/or
Supercooling degree delta T of indoor heat exchanger sub Greater than predetermined supercooling degree delta T 1 (ii) a And/or
The superheat degree delta Tsup of the outdoor heat exchanger is more than the preset superheat degree delta T 2 。
In some embodiments, the controller is further configured to obtain a heating load Q of the indoor heat exchanger in And according to the heating load Q in Adjusting predetermined degree of superheat Δ T 2 Wherein the heating load Q in With a predetermined degree of superheat Δ T 2 And (4) positively correlating.
In some embodiments, the controller is further configured to:
heating load Q of indoor heat exchanger in ＞Q 2 At a predetermined degree of superheat DeltaT 2 Set to a predetermined degree of superheat Δ T 21 ；
Heating load Q of indoor heat exchanger in ∈(Q 1 ,Q 2 ]At this time, the predetermined degree of superheat Δ T2 is set to the predetermined degree of superheat Δ T 22 ；
Heating load Q of indoor heat exchanger in ≤Q 1 At this time, the predetermined degree of superheat Δ T2 is set to the predetermined degree of superheat Δ T 23 ，
Wherein, delta T 21 ＞ΔT 22 ＞ΔT 23 。
According to another aspect of the present invention, an air conditioning apparatus is also provided, and the air conditioning apparatus includes the refrigerant circulation system.
According to another aspect of the present invention, there is provided a method for controlling the refrigerant circulation system, the method comprising:
step one, judging whether a first preset condition is met;
step two, if the first preset condition is met, controlling the energy storage equipment to be switched to a second state; if the first preset condition is not met, the communication between the energy accumulator and the indoor heat exchanger is cut off, and the indoor heat exchanger is communicated with the outdoor heat exchanger, so that the refrigerant condensed in the indoor heat exchanger is evaporated by the outdoor heat exchanger.
In some embodiments, step two further comprises disconnecting the indoor heat exchanger from the outdoor heat exchanger.
In some embodiments, the first preset condition includes:
compressor discharge temperature T D -outdoor ambient temperature T env Less than or equal to the predetermined temperature difference A 1 (ii) a And/or
High pressure saturation temperature T H -outdoor ambient temperature T env Less than or equal to the predetermined temperature difference B 1 (ii) a And/or
Temperature T of gaseous refrigerant output by gas-liquid separator S Low pressure saturation temperature T L Less than or equal to the predetermined temperature difference C 1 。
In some embodiments, the control method further comprises:
judging whether a second preset condition for judging that the liquid refrigerant in the gas-liquid separator is reduced to a preset amount is met or not;
if the second preset condition is met, controlling the indoor heat exchanger and the outdoor heat exchanger to be communicated while the energy storage equipment is in the second state so as to enable the energy accumulator and the outdoor heat exchanger to simultaneously evaporate the refrigerant condensed in the indoor heat exchanger; and if the second preset condition is not met, the energy storage equipment is kept in the second state, and meanwhile, the indoor heat exchanger and the outdoor heat exchanger are in a cut-off state.
In some embodiments, the second predetermined condition comprises:
compressor discharge temperature T D -outdoor ambient temperature T env > predetermined temperature difference A 2 Wherein the predetermined temperature difference A 2 > said predetermined temperature difference A 1 (ii) a And/or
High pressure saturation temperature T H -outdoor ambient temperature T env > predetermined temperature difference B 2 Wherein said predetermined temperature difference B 2 > said predetermined temperature difference B 1 (ii) a And/or
Temperature T of gaseous refrigerant output by gas-liquid separator S Low pressure saturation temperature T L > predetermined temperature difference C 2 (ii) a And/or
Supercooling degree delta T of indoor heat exchanger sub > predetermined supercooling degree DeltaT 1 。
In some embodiments, the control method further comprises:
step five, acquiring heating load Q of indoor heat exchanger in ；
Step six, according to the heating load Q in Adjusting the predetermined temperature difference C 2 Wherein the heating load Q in By a predetermined temperature difference C 2 Positive correlation;
wherein, the fifth step and the sixth step are carried out after the fourth step or between the second step and the third step.
In some embodiments, the control method further comprises:
heating load Q of indoor heat exchanger in ＞Q 2 At a predetermined temperature difference C 2 Set to a predetermined temperature difference C 21 ；
Heating load Q of indoor heat exchanger in ∈(Q 1 ,Q 2 ]At a predetermined temperature difference C 2 Set to a predetermined temperature difference C 22 ；
Heating load Q of indoor heat exchanger in ≤Q 1 At a predetermined temperature difference C 2 Set to a predetermined temperature difference C 23 ，
Wherein, C 21 ＞C 22 ＞C 23 。
In some embodiments, the control method further comprises:
step seven, judging whether a third preset condition for judging that the liquid refrigerant in the outdoor heat exchanger is reduced to a preset amount is met;
step eight, if a third preset condition is met, the communication between the energy accumulator and the indoor heat exchanger is cut off, and the communication between the indoor heat exchanger and the outdoor heat exchanger is kept, so that the refrigerant condensed in the indoor heat exchanger is evaporated by the outdoor heat exchanger; and if the third preset condition is not met, keeping the energy storage equipment in the second state, and communicating the indoor heat exchanger with the outdoor heat exchanger.
In some embodiments, the third preset condition comprises:
compressor discharge temperature T D -outdoor ambient temperature T env > predetermined temperature difference A 2 Wherein the predetermined temperature difference A 2 > said predetermined temperature difference A 1 (ii) a And/or
High pressure saturation temperature T H -outdoor ambient temperature T env > predetermined temperature difference B 2 Wherein said predetermined temperature difference B 2 > said predetermined temperature difference B 1 (ii) a And/or
Temperature T of gaseous refrigerant output by gas-liquid separator S Low pressure saturation temperature T L > predetermined temperature difference C 2 (ii) a And/or
Supercooling degree delta T of indoor heat exchanger sub > predetermined supercooling degree DeltaT 1 (ii) a And/or
Degree of superheat delta T of outdoor heat exchanger sup Greater than predetermined superheat degree Δ T 2 。
In some embodiments, step seven includes basing heating load Q on in Adjusting predetermined degree of superheat Δ T 2 Wherein the heating load Q in With a predetermined degree of superheat Δ T 2 And (4) positive correlation.
In some embodiments, the controller is further configured to:
heating load Q of indoor heat exchanger in ＞Q 2 At a predetermined degree of superheat DeltaT 2 Set to a predetermined degree of superheat Δ T 21 ；
Heating load Q of indoor heat exchanger in ∈(Q 1 ,Q 2 ]At this time, the predetermined degree of superheat Δ T2 is set to the predetermined degree of superheat Δ T 22 ；
Heating load Q of indoor heat exchanger in ≤Q 1 At this time, the predetermined degree of superheat Δ T2 is set to the predetermined degree of superheat Δ T 23 ，
Wherein, Δ T 21 ＞ΔT 22 ＞ΔT 23 。
By applying the technical scheme, the energy accumulator of the refrigerant circulating system can be used as an evaporator, and the refrigerant after heat exchange with the heat storage medium of the energy accumulator in the energy accumulator has higher temperature, so that the liquid refrigerant in the gas-liquid separator 102 can be gasified after the refrigerant is conveyed to the gas-liquid separator, and the gasified refrigerant enters the compressor to be compressed, thereby improving the amount of the refrigerant in a circulating state in the refrigerant circulating system.
Other features of the present invention and advantages thereof will become apparent from the following detailed description of exemplary embodiments thereof, which proceeds with reference to the accompanying drawings.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the embodiments or the description of the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the drawings without creative efforts.
Fig. 1 is a schematic structural diagram of a refrigerant circulation system according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of a coolant circulation system under a first operating condition according to an embodiment of the invention;
FIG. 3 is a schematic diagram of a refrigerant circulation system under a second operating condition according to an embodiment of the invention;
FIG. 4 illustrates a refrigerant cycle system under a third operating condition in accordance with an embodiment of the present invention;
FIG. 5 is a flow chart illustrating a control of the refrigerant cycle system according to an embodiment of the present invention;
fig. 6 is a control flow chart of a refrigerant circulation system according to another alternative embodiment of the present invention.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the invention, its application, or uses. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
As shown in fig. 1, the refrigerant circulation system of the present embodiment includes a compressor 101, a gas-liquid separator 102, an outdoor heat exchanger 105, an energy storage device 2, and a controller.
The compressor 101 is used for providing a refrigerant to be condensed to the indoor heat exchanger; the gas-liquid separator 102 is connected to a suction port of the compressor 101; the outdoor heat exchanger 105 is connected to the indoor heat exchanger to introduce a refrigerant to be evaporated and to the gas-liquid separator 102 to transfer the evaporated refrigerant to the gas-liquid separator 102.
The energy storage device 2 includes an energy storage 201 connected to the compressor 101, the gas-liquid separator 102, and the indoor heat exchanger, and the energy storage device 2 is configured to switch between a first state in which the energy storage 201 communicates with an exhaust port of the compressor 101 to store heat and a second state in which a first refrigerant inlet/outlet 201a of the energy storage 201 communicates with the indoor heat exchanger to introduce a refrigerant to be evaporated and a second refrigerant inlet/outlet 201b of the energy storage 201 communicates with the gas-liquid separator 102 to deliver the evaporated refrigerant to the gas-liquid separator 102.
The controller is in signal connection with the energy storage device 2 to switch the energy storage device 2 to the second state when a first preset condition for determining that the refrigerant participating in circulation in the condensing cycle system is insufficient is satisfied, so as to heat the liquid refrigerant in the refrigerant evaporation gas-liquid separator 102 by using the energy accumulator 201.
In this embodiment, the accumulator 201 of the refrigerant circulation system may be used as an evaporator, and the refrigerant after heat exchange with the heat storage medium of the accumulator 201 in the accumulator 201 has a relatively high temperature, so that the above-mentioned refrigerant may gasify the liquid refrigerant in the gas-liquid separator 102 after being delivered to the gas-liquid separator 102, and the gasified refrigerant may enter the compressor 101 to be compressed, thereby increasing the amount of the refrigerant in a circulating state in the refrigerant circulation system.
The refrigerant circulating system further comprises a reversing valve 104, the reversing valve 104 comprises an inlet communicated with the exhaust port of the compressor 101, a return port connected with the gas-liquid separator 102, a first working port capable of being selectively communicated with one of the inlet and the return port and a second working port communicated with the other of the inlet and the return port, and the first working port is used for being connected with the indoor heat exchanger.
The first working port is connected to the outdoor heat exchanger 104, and the second working port is used for connecting to the indoor heat exchanger. In some embodiments, the refrigerant circulation system further comprises a gas side pipe 4 for connecting the second working port and the indoor heat exchanger. The refrigerant circulation system further comprises a liquid side pipeline 3 for connecting the indoor heat exchanger and the outdoor heat exchanger.
The refrigerant circulation system further includes a first control valve 106 connected to the outdoor heat exchanger 105, and optionally, the first control valve 106 includes a throttle valve. A first control valve 106 is located in the liquid side line 3. The refrigerant circulation system further includes a subcooler 103 in the liquid side pipe 3 and a subcooling throttling device 107 for throttling the refrigerant entering the subcooler 103.
The compressor 101, the outdoor heat exchanger 105, and the direction change valve 104 are disposed in the outdoor unit 1 of the refrigerant cycle system.
In this embodiment, the first refrigerant inlet/outlet port 201a of the accumulator 201 may selectively communicate with one of the indoor heat exchanger and the outdoor heat exchanger 105, and the second refrigerant inlet/outlet port 201b of the accumulator 201 may selectively communicate with one of the gas outlet port of the compressor 101 and the gas-liquid separator 102.
When the energy storage device 2 is in the first state, the first refrigerant inlet/outlet 201a of the energy storage 201 is communicated with the outdoor heat exchanger 105, and the second refrigerant inlet/outlet 201b of the energy storage 201 is communicated with the exhaust gas of the compressor 101, as shown in fig. 2, the gas exhausted by the compressor 101 enters the second refrigerant inlet/outlet 201b of the energy storage 201 to exchange heat with the heat storage medium in the energy storage 201, the refrigerant after exchanging heat with the heat storage medium is throttled by the first control valve 106 and then enters the outdoor heat exchanger 105 to be evaporated, and the evaporated refrigerant returns to the compressor 101 through the gas-liquid separator 102 to be compressed again.
When the energy storage device 2 is in the second state, the first refrigerant inlet/outlet 201a of the energy storage 201 is communicated with the indoor heat exchanger, and one of the second refrigerant inlet/outlet 201b of the energy storage 201 is communicated with the gas-liquid separator 102, as shown in fig. 3, the refrigerant compressed by the compressor 101 is conveyed into the indoor heat exchanger to be condensed, the condensed refrigerant enters, the first refrigerant inlet/outlet 201a of the energy storage 201, the refrigerant evaporated in the energy storage 201 enters the gas-liquid separator 102 through the second refrigerant inlet/outlet 201b, and the gas at the separation position of the gas-liquid separator 102 enters the compressor 101 to be compressed again.
The energy storage device 2 further comprises a first communication line 204 and a second communication line 213. One end of the first communication pipe 204 communicates with the first refrigerant inlet/outlet 201a, the other end communicates with the liquid side pipe 3, and the second control valve 206 is provided in the first communication pipe 204.
One end of the second communication pipeline 213 is communicated with the first refrigerant inlet/outlet 201a, and the other end is communicated with the liquid side pipeline 3, and the joint of the second communication pipeline 213 and the liquid side pipeline 3 is farther from the outdoor heat exchanger 105 than the joint of the first communication pipeline 204 and the liquid side pipeline 3 in the flowing direction of the liquid side pipeline 3.
The refrigerant circulation system further includes a first on-off valve 211 and a first check valve 209. The first switch valve 211 is arranged in the liquid side pipeline 3 and is positioned between the joint of the first communication pipeline 204 and the liquid side pipeline 3 and the joint of the second communication pipeline 213 and the liquid side pipeline 3; the first check valve 209 is disposed in the second communication pipe 213, and an inlet end of the first check valve 209 communicates with the first refrigerant inlet/outlet 201a of the accumulator 201. The first on-off valve 211 is used to control the on-off of a section of the liquid side pipeline 3 bypassing the accumulator 201.
The refrigerant circulation system further includes a third communication pipeline 202 and a fourth communication pipeline 203. One end of the third communication pipeline 202 is communicated with the exhaust port of the compressor 101 or the gas-side pipeline 4, and the other end is communicated with the second refrigerant inlet/outlet 201b of the energy accumulator 201; one end of the fourth communication pipe 203 communicates with the second refrigerant inlet/outlet 201b of the accumulator 201, and the other end communicates with the gas-liquid separator 102.
The refrigerant circulation system further includes a second on/off valve 208 and a third on/off valve 210. A second on-off valve 208 is provided in the third communication line 202; a third on/off valve 210 is provided in the fourth communication line 203.
The other end of the third communication pipeline 202 is communicated with a first communication pipeline 204 communicating the first refrigerant inlet/outlet 201a with the liquid side pipeline 3, the connection point between the other end of the third communication pipeline 202 and the first communication pipeline 204 is located between the liquid side pipeline 3 and the second control valve 206 in the flow direction of the first communication pipeline 204, the refrigerant circulation system further includes a fifth communication pipeline 205, one end of the fifth communication pipeline 205 is communicated with the first communication pipeline 204, and the other end of the fifth communication pipeline 205 is communicated with the second refrigerant inlet/outlet 201b of the accumulator 201.
The connection of the fifth communication pipe 205 with the first communication pipe 204 is between the liquid-side pipe 3 and the second control valve 206 in the flow direction of the first communication pipe 204.
The refrigerant circulation system further includes a fourth on-off valve 212 and a second check valve 207. A fourth switching valve 212 is provided in the fifth communication pipe 205; the second check valve 207 is provided in the first communication pipe 204 and is located between the liquid-side pipe 3 and the fifth communication pipe 205 in the flow direction of the first communication pipe 204.
As shown in fig. 2, when the energy storage device 2 is in the first state, the gaseous refrigerant discharged from the compressor 1 enters the second refrigerant inlet/outlet 201b of the energy storage 201 through the third communication pipe 202, the first communication pipe 204 and the fifth communication pipe 205, and the refrigerant after exchanging heat with the heat storage medium in the energy storage 201 returns to the compressor 101 through the second communication pipe 213, the liquid side pipe 3, the first control valve 106, the outdoor heat exchanger 105 and the gas-liquid separator 102.
As shown in fig. 3 and 4, when the energy storage device 2 is in the second state, the gas discharged from the compressor 101 is delivered to the indoor heat exchanger through the reversing valve 104 and the gas-side pipeline 4, the refrigerant condensed by the indoor heat exchanger enters the first refrigerant inlet/outlet 201a of the energy accumulator 201 through the liquid-side pipeline 3, the first communication pipeline 204 and the second control valve 206, and the refrigerant exchanges heat with the heat storage medium in the energy accumulator 201 and then returns to the compressor 101 through the fourth communication pipeline 203 and the gas-liquid separator 102 to be compressed again.
The first preset condition includes:
compressor discharge temperature T D -outdoor ambient temperature T env Less than or equal to the predetermined temperature difference A 1 ；
High pressure saturation temperature T H -outdoor ambient temperature T env Less than or equal to the predetermined temperature difference B 1 ；
Temperature T of gaseous refrigerant output by gas-liquid separator S Low pressure saturation temperature T L Less than or equal to the predetermined temperature difference C 1 。
In the working process of the refrigerant circulating system, one of the indoor heat exchanger and the outdoor heat exchanger 105 is used as a condenser, the other one is used as an evaporator, the refrigerant compressed by the compressor 101 is conveyed to the condenser for condensation, the condensed refrigerant is conveyed to the evaporator for evaporation after being throttled, the evaporated refrigerant is conveyed to the gas-liquid separator 102, and the gaseous refrigerant separated by the gas-liquid separator 102 is conveyed to the air suction port of the compressor 101 for recompression.
In the present embodiment, the high pressure saturation temperature T H The saturation temperature of the refrigerant in the condenser during condensation, low-pressure saturation temperature T L The saturation temperature of the evaporator at which the refrigerant evaporates.
In some embodiments, the refrigerant circulation system further includes a first control valve 106, the first control valve 106 is disposed in a pipeline connecting the indoor heat exchanger and the outdoor heat exchanger 105, and the controller is in signal connection with the first control valve 106 to close the first control valve 106 to prevent the refrigerant condensed in the indoor heat exchanger from being delivered to the outdoor heat exchanger 105 when the first preset condition is met and the energy storage device 2 is switched to the second state.
As shown in fig. 3, when the first preset condition is satisfied, the energy storage device 2 is switched to the second state, and the indoor heat exchanger is used as a condenser to condense the refrigerant compressed by the compressor 101. Only the accumulator 201 of the accumulator 201 and the outdoor heat exchanger 105 is used as an evaporator, the refrigerant exchanges heat with the energy storage medium and evaporates in the accumulator 201, and the evaporated refrigerant with a high temperature is conveyed to the gas-liquid separator 102 and vaporizes the refrigerant in the gas-liquid separator 102.
In some embodiments, the controller is configured to open the first control valve 106 when a second preset condition for determining that the liquid refrigerant in the gas-liquid separator 102 decreases to a predetermined amount is satisfied.
As shown in fig. 4, when the second preset condition is satisfied, the energy storage device 2 is switched to the second state, and the indoor heat exchanger is used in the condenser to condense the refrigerant compressed by the compressor 101. The accumulator 201 and the outdoor heat exchanger 105 both serve as evaporators, the refrigerant exchanges heat with the energy storage medium in the accumulator 201 and evaporates, and the evaporated refrigerant with a higher temperature is conveyed to the gas-liquid separator 102 and vaporizes the refrigerant in the gas-liquid separator 102.
In some embodiments, the second predetermined condition comprises:
compressor discharge temperature T D -outdoor ambient temperature T env > predetermined temperature difference A 2 Wherein the predetermined temperature difference A 2 > said predetermined temperature difference A 1 ；
High pressure saturation temperature T H -outdoor ambient temperature T env > predetermined temperature difference B 2 Wherein said predetermined temperature difference B 2 > said predetermined temperature difference B 1 ；
Temperature T of gaseous refrigerant output by gas-liquid separator S Low pressure saturation temperature T L > predetermined temperature difference C 2 ；
Supercooling degree delta T of indoor heat exchanger sub > predetermined supercooling degree DeltaT 1 。
In some embodiments, the controller is further configured to obtain a heating load Q of the indoor heat exchanger in And according to the heating load Q in Adjusting the predetermined temperature difference C 2 Wherein the heating load Q in By a predetermined temperature difference C 2 And (4) positively correlating.
In some embodiments, the controller is further configured to:
heating load Q of indoor heat exchanger in ＞Q 2 At a predetermined temperature difference C 2 Set to a predetermined temperature difference C 21 ；
Heating load Q of indoor heat exchanger in ∈(Q 1 ,Q 2 ]At a predetermined temperature difference C 2 Set to a predetermined temperature difference C 22 ；
Heating load Q of indoor heat exchanger in ≤Q 1 At a predetermined temperature difference C 2 Set to a predetermined temperature difference C 23 ，
Wherein, C 21 ＞C 22 ＞C 23 。
In some embodiments, the energy storage apparatus 2 comprises a second control valve 206, the second control valve 206 being provided in the conduit connecting the indoor heat exchanger and the accumulator 201; the controller is in signal connection with the second control valve 206 to close the second control valve 206 when a third preset condition for determining that the liquid refrigerant in the outdoor heat exchanger 105 is reduced to a predetermined amount is satisfied.
When the third preset condition is satisfied, the accumulator 201 and the indoor heat exchanger are disconnected, and the indoor heat exchanger is used as a condenser to condense the refrigerant compressed by the compressor 101. Only the outdoor heat exchanger 105 of the accumulator 201 and the outdoor heat exchanger 105 is used as an evaporator, and the refrigerant cycle system operates in a normal heating mode.
In some embodiments, the third preset condition comprises:
compressor discharge temperature T D -outdoor ambient temperature T env Greater than a predetermined temperature difference A 2 Wherein the predetermined temperature difference A 2 The predetermined temperature difference A 1 ；
High pressure saturation temperature T H -outdoor ambient temperature T env Greater than a predetermined temperature difference B 2 Wherein the predetermined temperature difference B 2 The predetermined temperature difference B 1 ；
Temperature T of gaseous refrigerant output by gas-liquid separator S Low pressure saturation temperature T L > predetermined temperature difference C 2 ；
Supercooling degree delta T of indoor heat exchanger sub > predetermined supercooling degree DeltaT 1 ；
Degree of superheat delta T of outdoor heat exchanger sup Greater than predetermined superheat degree Δ T 2 。
In some embodiments, the controller is further configured to obtain a heating load Q of the indoor heat exchanger in And according to heating load Q in Adjusting predetermined degree of superheat Δ T 2 Wherein the heating load Q in With a predetermined degree of superheat Δ T 2 And (4) positively correlating.
In some embodiments, the controller is further configured to:
heating load Q of indoor heat exchanger in ＞Q 2 At a predetermined degree of superheat DeltaT 2 Set to a predetermined degree of superheat Δ T 21 ；
Heating load Q of indoor heat exchanger in ∈(Q 1 ,Q 2 ]At this time, the predetermined degree of superheat Δ T2 is set to the predetermined degree of superheat Δ T 22 ；
Heating load Q of indoor heat exchanger in ≤Q 1 At this time, the predetermined degree of superheat Δ T2 is set to the predetermined degree of superheat Δ T 23 ，
Wherein, delta T 21 ＞ΔT 22 ＞ΔT 23 。
According to another aspect of the present invention, an air conditioning apparatus is further provided, and the air conditioning apparatus includes the refrigerant circulation system.
According to another aspect of the present invention, there is provided a method for controlling the refrigerant circulation system, the method comprising:
step one, judging whether a first preset condition is met;
step two, if the first preset condition is met, controlling the energy storage equipment 2 to be switched to a second state; if the first preset condition is not satisfied, the communication between the accumulator 201 and the indoor heat exchanger is cut off, and the indoor heat exchanger and the outdoor heat exchanger 105 are communicated, so that the refrigerant condensed in the indoor heat exchanger is evaporated by the outdoor heat exchanger 105.
In this embodiment, the accumulator 201 of the refrigerant circulation system may be used as an evaporator, and the refrigerant after heat exchange with the heat storage medium of the accumulator 201 in the accumulator 201 has a high temperature, so that the refrigerant is conveyed to the gas-liquid separator 102 to gasify the liquid refrigerant in the gas-liquid separator 102, and the gasified refrigerant enters the compressor 101 to be compressed, thereby increasing the amount of the refrigerant in a circulation state in the refrigerant circulation system.
In some embodiments, step two further comprises cutting off the communication between the indoor heat exchanger and the outdoor heat exchanger 105.
As shown in fig. 3, when the first preset condition is satisfied, the energy storage device 2 is switched to the second state, and the indoor heat exchanger is used as a condenser to condense the refrigerant compressed by the compressor 101. Only the accumulator 201 of the accumulator 201 and the outdoor heat exchanger 105 is used as an evaporator, the refrigerant exchanges heat with the energy storage medium and evaporates in the accumulator 201, and the evaporated refrigerant with a high temperature is conveyed to the gas-liquid separator 102 and vaporizes the refrigerant in the gas-liquid separator 102.
In some embodiments, the first preset condition includes:
compressor discharge temperature T D -outdoor ambient temperature T env Less than or equal to the predetermined temperature difference A 1 ；
High pressure saturation temperature T H -outdoor ambient temperature T env Less than or equal to the predetermined temperature difference B 1 ；
Temperature T of gaseous refrigerant output by gas-liquid separator S Low pressure saturation temperature T L Less than or equal to the predetermined temperature difference C 1 。
In some embodiments, the control method further comprises:
judging whether a second preset condition for judging that the liquid refrigerant in the gas-liquid separator 102 is reduced to a preset amount is met;
and step four, if the second preset condition is met, controlling the indoor heat exchanger and the outdoor heat exchanger 105 to be communicated while enabling the energy storage equipment 2 to be in the second state, so that the energy accumulator 201 and the outdoor heat exchanger 105 simultaneously evaporate the refrigerant condensed in the indoor heat exchanger. As shown in fig. 4, when the second preset condition is satisfied, the energy storage device 2 is switched to the second state, and the indoor heat exchanger is used in the condenser to condense the refrigerant compressed by the compressor 101. The accumulator 201 and the outdoor heat exchanger 105 both serve as evaporators, the refrigerant exchanges heat with the energy storage medium in the accumulator 201 and evaporates, and the evaporated refrigerant with a higher temperature is conveyed to the gas-liquid separator 102 and vaporizes the refrigerant in the gas-liquid separator 102.
If the second preset condition is not met, the energy storage device 2 is kept in the second state, and meanwhile the space between the indoor heat exchanger and the outdoor heat exchanger 105 is in a cut-off state.
In some embodiments, the second predetermined condition comprises:
compressor discharge temperature T D -outdoor ambient temperature T env > predetermined temperature difference A 2 Wherein the predetermined temperature difference A 2 > said predetermined temperature difference A 1 ；
High pressure saturation temperature T H Outdoor ambient temperature T env > predetermined temperature difference B 2 Wherein the predetermined temperature difference B 2 > said predetermined temperature difference B 1 ；
Temperature T of gaseous refrigerant output by gas-liquid separator S Low pressure saturation temperature T L > predetermined temperature difference C 2 ；
Supercooling degree delta T of indoor heat exchanger sub > predetermined supercooling degree DeltaT 1 。
In some embodiments, the control method further comprises:
step five, acquiring heating load Q of indoor heat exchanger in ；
Step six, according to the heating load Q in Adjusting the predetermined temperature difference C 2 Wherein the heating load Q in By a predetermined temperature difference C 2 Positive correlation;
wherein, the fifth step and the sixth step are carried out after the fourth step or between the second step and the third step.
In some embodiments, the control method further comprises:
heating load Q of indoor heat exchanger in ＞Q 2 At a predetermined temperature difference C 2 Set to a predetermined temperature difference C 21 ；
Heating load Q of indoor heat exchanger in ∈(Q 1 ,Q 2 ]At a predetermined temperature difference C 2 Set to a predetermined temperature difference C 22 ；
Heating load Q of indoor heat exchanger in ≤Q 1 At a predetermined temperature difference C 2 Set to a predetermined temperature difference C 23 ，
Wherein, C 21 ＞C 22 ＞C 23 。
In some embodiments, the control method further comprises:
step seven, judging whether a third preset condition for judging that the liquid refrigerant in the outdoor heat exchanger 105 is reduced to a preset amount is met;
step eight, if a third preset condition is met, the communication between the energy accumulator 201 and the indoor heat exchanger is cut off, and the communication between the indoor heat exchanger and the outdoor heat exchanger 105 is kept, so that the outdoor heat exchanger 105 evaporates the refrigerant condensed in the indoor heat exchanger; if the third preset condition is not satisfied, the energy storage device 2 is kept in the second state, and the indoor heat exchanger and the outdoor heat exchanger 105 are communicated.
When the third preset condition is satisfied, the accumulator 201 and the indoor heat exchanger are disconnected, and the indoor heat exchanger is used as a condenser to condense the refrigerant compressed by the compressor 101. Only the outdoor heat exchanger 105 of the accumulator 201 and the outdoor heat exchanger 105 is used as an evaporator, and the refrigerant cycle system operates in a normal heating mode.
In some embodiments, the third preset condition comprises:
compressor discharge temperature T D -outdoor ambient temperature T env > predetermined temperature difference A 2 Wherein the predetermined temperature difference A 2 > said predetermined temperature difference A 1 ；
High pressure saturation temperature T H -outdoor ambient temperature T env > predetermined temperature difference B 2 Wherein the predetermined temperature difference B 2 The predetermined temperature difference B 1 ；
Temperature T of gaseous refrigerant output by gas-liquid separator S Low pressure saturation temperature T L > predetermined temperature difference C 2 ；
Supercooling degree delta T of indoor heat exchanger sub Greater than predetermined supercooling degree delta T 1 ；
Degree of superheat delta T of outdoor heat exchanger sup Greater than predetermined superheat degree Δ T 2 。
In some embodiments, step seven includes basing heating load Q on in Adjusting predetermined degree of superheat Δ T 2 Wherein the heating load Q in With a predetermined degree of superheat Δ T 2 And (4) positive correlation.
In some embodiments, the controller is further configured to:
heating load Q of indoor heat exchanger in ＞Q 2 At a predetermined degree of superheat DeltaT 2 Set to a predetermined degree of superheat Δ T 21 ；
Heating load Q of indoor heat exchanger in ∈(Q 1 ,Q 2 ]At this time, the predetermined degree of superheat Δ T2 is set to the predetermined degree of superheat Δ T 22 ；
Heating load Q of indoor heat exchanger in ≤Q 1 At this time, the predetermined degree of superheat Δ T2 is set to the predetermined degree of superheat Δ T 23 ，
Wherein, delta T 21 ＞ΔT 22 ＞ΔT 23 。
As shown in fig. 5, a specific control flow of the present embodiment is described below:
s100: when the air conditioner is started for heating, the following data are counted to be used as a criterion for judging whether the air conditioner needs to enter the refrigerant migration operation: compressor discharge temperature T D Outdoor ambient temperature T env High pressure saturation temperature T H Average supercooling degree delta T of indoor unit sub 105 superheat degree delta T of outdoor heat exchanger sup Low pressure saturation temperature T L Gas-liquid separator 102 outlet pipe temperature T S 。
S101: if the following condition is satisfied, it is determined that the refrigerant migration operation needs to be performed, and S103 is executed. If not, the process proceeds to S102. Wherein, A, B, C value can be set according to system requirements.
S102: and judging that the amount of the liquid refrigerant in the system does not influence the normal operation, and switching to the conventional heating operation.
S103: and judging that the refrigerant migration operation is required. At this time, the indoor load demand Qin is calculated.
S104: and judging the indoor heating load requirement condition at the moment. If Q is satisfied in ＞Q 2 At the time of the system judgmentIn the high load state, the process proceeds to S105, if Q is not satisfied in ＞Q 2 The process proceeds to S109, and it is continuously determined what state the indoor heating load demand is in.
S105: at this time, the independent heat release operation is performed, that is, the heating operation is performed by opening only the second control valve 206 of the accumulator 201, closing the first control valve 106, and using only the accumulator 201 as the evaporator. At this time, the indoor heat exchanger continuously supplies heat to the indoor space, and the refrigerant is condensed in the indoor heat exchanger, enters the energy accumulator 201, exchanges heat with the energy storage material which stores a large amount of heat in the energy accumulator 201 to be evaporated, forms a gaseous refrigerant with a higher temperature, enters the gas-liquid separator 102 which stores a large amount of liquid refrigerant, is mixed with the liquid refrigerant, and exchanges heat. The gaseous refrigerant in the gas-liquid separator 102 is advantageous to evaporate into a gaseous state as soon as possible due to the high temperature of the gaseous refrigerant, and enters a heating cycle. Meanwhile, the outdoor heat exchanger 105 is bypassed, and the liquid refrigerant in the outdoor heat exchanger 105 is not processed for the moment, thereby reducing the circulation resistance of the refrigerant.
S106: while running S105, a condition judgment is made. If the preset condition 1 is satisfied, it is determined that the liquid refrigerant existing in the gas-liquid separator 102 has been transferred, and the process proceeds to S107. If the preset condition 1 is not satisfied, the independent heat release operation of S105 is continued. The preset condition 1 is as follows:
s107: the parallel heat release operation is entered, that is, the second control valve 206 is opened, and simultaneously, the first control valve 106 is gradually opened to gradually increase the evaporation load borne by the outdoor heat exchanger 105 by using the accumulator 201 and the outdoor heat exchanger 105 as evaporators. In the process, the refrigerant gradually enters the outdoor heat exchanger 105 and the corresponding pipeline to gradually evaporate the refrigerant in the outdoor heat exchanger 105, and because the evaporation loads of the energy accumulator 201 and the outdoor heat exchanger 105 can be distributed through the opening degree of the expansion valve, the liquid refrigerant in the outdoor heat exchanger 105 can be gradually evaporated while the normal operation of the system is ensured, and the negative influence on the indoor heating effect is reduced.
S108: while running S107, a condition judgment is made. If the preset condition 4 is satisfied, it is determined that the refrigerant in the outdoor heat exchanger 105 and the corresponding pipeline has been completely evaporated, and the conventional heating operation of S102 is performed. If the preset condition 4 is not met, the parallel heat release operation of S107 is continued. The preset condition 4 is:
s109: the process proceeds to S104, and the indoor heating load demand at this time is continuously determined. If Q is satisfied in ∈(Q 1 ,Q 2 ]If the system is in the medium load state, the process proceeds to S110, and if not, qin ∈ (Q) is satisfied 1 ,Q 2 ]The process proceeds to S114, and it is continuously determined what state the indoor heating load demand is in at that time.
S110: at this time, the independent heat release operation is performed in the same manner as in S105.
S111: while running S110, a condition judgment is made. If the preset condition 2 is satisfied, it is determined that the liquid refrigerant existing in the gas-liquid separator 102 has been completely transferred, and the process proceeds to S112. If the preset condition 2 is not satisfied, the independent heat release operation of S110 is continued. The preset condition 2 is:
s112: the parallel heat release operation is performed, as in S107.
S113: while running S112, a condition judgment is made. If the preset condition 5 is satisfied, it is determined that the refrigerant in the outdoor heat exchanger 105 and the corresponding pipeline has been completely evaporated, and the process proceeds to the conventional heating operation of S102. If the preset condition 5 is not satisfied, the parallel heat release operation of S112 is continued. The preset condition 5 is as follows:
s114: the process proceeds to S109, and the situation of the indoor heating load demand at this time is continuously determined. If Qin is less than or equal to Q1, the system is judged to be in a low load state at the moment, and the process enters S115.
S115: at this time, the independent heat release operation is performed in the same manner as in S105.
S116: while S115 is being executed, a condition judgment is performed. If the preset condition 3 is satisfied, it is determined that the liquid refrigerant existing in the gas-liquid separator 102 has been transferred, and the process proceeds to S117. If the preset condition 3 is not satisfied, the independent heat release operation of S115 is continued. The preset condition 3 is:
s117: the parallel heat release operation is performed, as in S107.
S118: while running S117, a condition determination is made. If the preset condition 6 is met, it is determined that the refrigerant in the outdoor heat exchanger 105 and the corresponding pipeline is completely evaporated, and the process proceeds to the conventional heating operation of S102. If the preset condition 6 is not satisfied, the parallel heat release operation of S117 is continued. The preset condition 6 is as follows:
under the condition of higher load, in the independent heat release operation, the refrigerant demand circulating in the system is more, so more refrigerant is transferred from the gas-liquid separator 102 to enter the circulation, and the gas-liquid separator 102 needs to have higher outlet pipe temperature. In the parallel heat-releasing operation, in order to ensure proper liquid refrigerant treatment of the outdoor heat exchanger 105, a high superheat degree of the outdoor heat exchanger 105 should be ensured. Under low load conditions, the exit tube temperature of the gas-liquid separator 102 may be low, and the degree of superheat may be low.
Therefore, the following relationship should be applied according to the difference between the high load, the medium load and the low load:
as shown in fig. 6, in another embodiment of the present invention, S200, S201, S202, S204, S206 are the same as S100, S101, S105, S107, S102 in the preferred embodiment, respectively.
The different aspect is that the alternative no longer distinguishes high, medium and low loads, but uses the same set of judgment criteria to evaluate whether to stop independent heat release or parallel heat release. Preset condition 1 in S203 in the alternative is:
the preset condition 2 in S205 in the alternative is:
in this embodiment, in order to solve the problem that a large amount of liquid refrigerant is accumulated in the outdoor heat exchanger 105 during the heating start-up phase of the air conditioning system, the heat stored in the accumulator 201 is used to quickly evaporate and gasify the liquid refrigerant in the gas-liquid separator 102 while ensuring the heating effect, so that the liquid refrigerant is in a state of being circulated and heated, and the liquid refrigerant in the gas-liquid separator 102 is properly treated. And then, gradually evaporating and gasifying the refrigerant in the outdoor heat exchanger 105 to enable the whole system pipeline to be in a normal heating state. And then the accumulator is stopped from being used, and the normal heating state is entered.
The above description is only exemplary of the present invention and should not be taken as limiting the invention, as any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (23)
1. A refrigerant circulation system, comprising:
the compressor (101) is used for providing a refrigerant to be condensed for the indoor heat exchanger;
a gas-liquid separator (102) connected to an intake port of the compressor (101);
an outdoor heat exchanger (105) connected with the indoor heat exchanger to introduce a refrigerant to be evaporated and connected with the gas-liquid separator (102) to convey the evaporated refrigerant to the gas-liquid separator (102);
the energy storage device (2) comprises an energy accumulator (201) which is respectively connected with the compressor (101), the gas-liquid separator (102) and the indoor heat exchanger, the energy storage device (2) is configured to be switched between a first state and a second state, in the first state, the energy accumulator (201) is communicated with an exhaust port of the compressor (101) to store heat, in the second state, a first refrigerant inlet/outlet (201 a) of the energy accumulator (201) is communicated with the indoor heat exchanger to introduce a refrigerant to be evaporated, and a second refrigerant inlet/outlet (201 b) of the energy accumulator (201) is communicated with the gas-liquid separator (102) to convey the evaporated refrigerant to the gas-liquid separator (102); and
and the controller is in signal connection with the energy storage equipment (2) so as to switch the energy storage equipment (2) to the second state when a first preset condition for judging that the circulating refrigerant in the condensation circulating system is insufficient is met, so that the liquid refrigerant in the gas-liquid separator (102) is evaporated by the refrigerant heated by the energy accumulator (201).
2. The refrigerant circulation system as claimed in claim 1, wherein the first predetermined condition comprises:
compressor discharge temperature T D -outdoor ambient temperature T env Less than or equal to the predetermined temperature difference A 1 (ii) a And/or
High pressure saturation temperature T H -outdoor ambient temperature T env Less than or equal to the predetermined temperature difference B 1 (ii) a And/or
Temperature T of gaseous refrigerant output by gas-liquid separator S Low pressure saturation temperature T L Less than or equal to the predetermined temperature difference C 1 。
3. The refrigerant cycle system as set forth in claim 1, further comprising a first control valve (106), said first control valve (106) being disposed in a pipe connecting said indoor heat exchanger and said outdoor heat exchanger (105),
the controller is in signal connection with the first control valve (106) so as to close the first control valve (106) to prevent refrigerant condensed in the indoor heat exchanger from being conveyed to the outdoor heat exchanger (105) when the first preset condition is met and the energy storage equipment (2) is switched to the second state.
4. The refrigerant cycle system as claimed in claim 3, wherein the controller is configured to open the first control valve (106) when a second preset condition for determining that the liquid refrigerant in the gas-liquid separator (102) is reduced to a predetermined amount is satisfied.
5. The refrigerant circulation system as claimed in claim 4, wherein the second predetermined condition comprises:
compressor discharge temperature T D -outdoor ambient temperature T env > predetermined temperature difference A 2 Wherein the predetermined temperature difference A 2 > said predetermined temperature difference A 1 (ii) a And/or
High pressure saturation temperature T H -outdoor ambient temperature T env > predetermined temperature difference B 2 Wherein the predetermined temperature difference B 2 > said predetermined temperature difference B 1 (ii) a And/or
Temperature T of gaseous refrigerant output by gas-liquid separator S Low pressure saturation temperature T L > predetermined temperature difference C 2 (ii) a And/or
Supercooling degree delta T of indoor heat exchanger sub > predetermined supercooling degree DeltaT 1 。
6. The refrigerant cycle system of claim 5, wherein the controller is further configured to obtain a heating load Q of the indoor heat exchanger in And according to the heating load Q in Adjusting the predetermined temperature difference C 2 Wherein the heating load Q in And the predetermined temperatureDifference C 2 And (4) positively correlating.
7. The coolant circulation system of claim 6, wherein the controller is further configured to:
heating load Q of the indoor heat exchanger in ＞Q 2 While keeping the predetermined temperature difference C 2 Set to a predetermined temperature difference C 21 ；
Heating load Q of the indoor heat exchanger in ∈(Q 1 ,Q 2 ]While keeping the predetermined temperature difference C 2 Set to a predetermined temperature difference C 22 ；
Heating load Q of the indoor heat exchanger in ≤Q 1 While keeping the predetermined temperature difference C 2 Set to a predetermined temperature difference C 23 ，
Wherein, C 21 ＞C 22 ＞C 23 。
8. Refrigerant cycle system according to any of claims 1 to 7, characterized in that the energy storage device (2) comprises a second control valve (206), the second control valve (206) being arranged in a line connecting the indoor heat exchanger and the energy accumulator (201);
the controller is in signal connection with the second control valve (206) to close the second control valve (206) when a third preset condition for determining that the liquid refrigerant in the outdoor heat exchanger (105) is reduced to a predetermined amount is met.
9. The refrigerant circulation system as claimed in claim 7, wherein the third predetermined condition comprises:
compressor discharge temperature T D -outdoor ambient temperature T env Greater than a predetermined temperature difference A 2 Wherein the predetermined temperature difference A 2 > said predetermined temperature difference A 1 (ii) a And/or
High pressure saturation temperature T H -outdoor ambient temperature T env > predetermined temperature difference B 2 Wherein the predetermined temperature difference B 2 > said predetermined temperature difference B 1 (ii) a And/or
Temperature T of gaseous refrigerant output by gas-liquid separator S Low pressure saturation temperature T L > predetermined temperature difference C 2 (ii) a And/or
Supercooling degree delta T of indoor heat exchanger sub > predetermined supercooling degree DeltaT 1 (ii) a And/or
Degree of superheat delta T of outdoor heat exchanger sup Greater than predetermined superheat degree Δ T 2 。
10. The refrigerant cycle system of claim 9, wherein the controller is further configured to obtain a heating load Q of the indoor heat exchanger in And according to the heating load Q in Adjusting the predetermined degree of superheat Δ T 2 Wherein the heating load Q in And the predetermined degree of superheat DeltaT 2 And (4) positively correlating.
11. The coolant circulation system of claim 10, wherein the controller is further configured to:
heating load Q of the indoor heat exchanger in ＞Q 2 While the predetermined degree of superheat DeltaT is set 2 Set to a predetermined degree of superheat Δ T 21 ；
Heating load Q of the indoor heat exchanger in ∈(Q 1 ,Q 2 ]The predetermined degree of superheat DeltaT 2 is set to the predetermined degree of superheat DeltaT 22 ；
Heating load Q of the indoor heat exchanger in ≤Q 1 The predetermined degree of superheat DeltaT 2 is set to the predetermined degree of superheat DeltaT 23 ，
Wherein, Δ T 21 ＞ΔT 22 ＞ΔT 23 。
12. An air conditioning apparatus, characterized by comprising the refrigerant circulation system according to any one of claims 1 to 11.
13. A method for controlling a refrigerant cycle system as claimed in any one of claims 1 to 11, comprising:
step one, judging whether the first preset condition is met;
step two, if the first preset condition is met, controlling the energy storage equipment (2) to be switched to the second state; if the first preset condition is not met, the communication between the energy accumulator (201) and the indoor heat exchanger is cut off, the indoor heat exchanger is communicated with the outdoor heat exchanger (105), and the refrigerant condensed in the indoor heat exchanger is evaporated by the outdoor heat exchanger (105).
14. The control method according to claim 13, wherein the second step further comprises cutting off communication between the indoor heat exchanger and the outdoor heat exchanger (105).
15. The control method according to claim 13, wherein the first preset condition includes:
compressor discharge temperature T D -outdoor ambient temperature T env Less than or equal to the predetermined temperature difference A 1 (ii) a And/or
High pressure saturation temperature T H -outdoor ambient temperature T env Less than or equal to the predetermined temperature difference B 1 (ii) a And/or
Temperature T of gaseous refrigerant output by gas-liquid separator S Low pressure saturation temperature T L Less than or equal to the predetermined temperature difference C 1 。
16. The control method according to claim 13, characterized by further comprising:
judging whether a second preset condition for judging that the liquid refrigerant in the gas-liquid separator (102) is reduced to a preset amount is met or not;
if the second preset condition is met, controlling the indoor heat exchanger and the outdoor heat exchanger (105) to be communicated while the energy storage equipment (2) is in the second state, so that the energy accumulator (201) and the outdoor heat exchanger (105) can simultaneously evaporate the refrigerant condensed in the indoor heat exchanger; if the second preset condition is not met, the energy storage equipment (2) is kept in the second state, and meanwhile the space between the indoor heat exchanger and the outdoor heat exchanger (105) is in a cut-off state.
17. The control method according to claim 16, characterized in that the second predetermined condition includes:
compressor discharge temperature T D -outdoor ambient temperature T env > predetermined temperature difference A 2 Wherein the predetermined temperature difference A 2 > said predetermined temperature difference A 1 (ii) a And/or
High pressure saturation temperature T H -outdoor ambient temperature T env > predetermined temperature difference B 2 Wherein said predetermined temperature difference B 2 > said predetermined temperature difference B 1 (ii) a And/or
Temperature T of gaseous refrigerant output by gas-liquid separator S Low pressure saturation temperature T L > predetermined temperature difference C 2 (ii) a And/or
Supercooling degree delta T of indoor heat exchanger sub > predetermined supercooling degree DeltaT 1 。
18. The control method according to claim 17, characterized by further comprising:
step five, acquiring the heating load Q of the indoor heat exchanger in ；
Step six, according to the heating load Q in Adjusting the predetermined temperature difference C 2 Wherein the heating load Q in At a temperature different from said predetermined temperature C 2 Positive correlation;
wherein the fifth step and the sixth step are performed before the fourth step.
19. The control method according to claim 18, characterized by further comprising:
heating load Q of the indoor heat exchanger in ＞Q 2 While keeping the predetermined temperature difference C 2 Set to a predetermined temperature difference C 21 ；
Heating load Q of the indoor heat exchanger in ∈(Q 1 ,Q 2 ]While keeping the predetermined temperature difference C 2 Set to a predetermined temperature difference C 22 ；
Heating load Q of the indoor heat exchanger in ≤Q 1 While keeping the predetermined temperature difference C 2 Set to a predetermined temperature difference C 23 ，
Wherein, C 21 ＞C 22 ＞C 23 。
20. The control method according to claim 13, characterized by further comprising:
step seven, judging whether a third preset condition for judging that the liquid refrigerant in the outdoor heat exchanger (105) is reduced to a preset amount is met;
step eight, if the third preset condition is met, the communication between the energy accumulator (201) and the indoor heat exchanger is cut off, and the indoor heat exchanger and the outdoor heat exchanger (105) are kept communicated, so that the outdoor heat exchanger (105) evaporates the refrigerant condensed in the indoor heat exchanger; if the third preset condition is not met, the energy storage equipment (2) is kept in the second state, and meanwhile the indoor heat exchanger is communicated with the outdoor heat exchanger (105).
21. The control method according to claim 20, characterized in that the third preset condition includes:
compressor discharge temperature T D -outdoor ambient temperature T env > predetermined temperature difference A 2 Wherein the predetermined temperature difference A 2 > said predetermined temperature difference A 1 (ii) a And/or
High pressure saturation temperature T H -outdoor ambient temperature T env > predetermined temperature difference B 2 Wherein said predetermined temperature difference B 2 > said predetermined temperature difference B 1 (ii) a And/or
Temperature T of gaseous refrigerant output by gas-liquid separator S Low pressure saturation temperature T L > predetermined temperature difference C 2 (ii) a And/or
Supercooling degree delta T of indoor heat exchanger sub > predetermined supercooling degree DeltaT 1 (ii) a And/or
Degree of superheat delta T of outdoor heat exchanger sup Greater than predetermined superheat degree Δ T 2 。
22. The control method according to claim 21, wherein the seventh step includes a step of adjusting the heating load Q according to the heating load Q in Adjusting the predetermined degree of superheat Δ T 2 Wherein the heating load Q in With said predetermined degree of superheat Δ T 2 And (4) positively correlating.
23. The control method of claim 22, wherein the controller is further configured to:
heating load Q of the indoor heat exchanger in ＞Q 2 While the predetermined degree of superheat DeltaT is set 2 Set to a predetermined degree of superheat Δ T 21 ；
Heating load Q of the indoor heat exchanger in ∈(Q 1 ,Q 2 ]While setting the predetermined degree of superheat DeltaT 2 to the predetermined degree of superheat DeltaT 22 ；
Heating load Q of the indoor heat exchanger in ≤Q 1 The predetermined degree of superheat DeltaT 2 is set to the predetermined degree of superheat DeltaT 23 ，
Wherein, delta T 21 ＞ΔT 22 ＞ΔT 23 。
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|---|---|---|---|
| CN202211427338.6A CN115727447A (en) | 2022-11-15 | 2022-11-15 | Refrigerant circulating system, control method thereof and air conditioning equipment |
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|---|---|---|---|
| CN202211427338.6A CN115727447A (en) | 2022-11-15 | 2022-11-15 | Refrigerant circulating system, control method thereof and air conditioning equipment |
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| CN115727447A true CN115727447A (en) | 2023-03-03 |
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| CN202211427338.6A Pending CN115727447A (en) | 2022-11-15 | 2022-11-15 | Refrigerant circulating system, control method thereof and air conditioning equipment |
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