CN112665216A - Heat pump system and defrosting mode thereof - Google Patents
Heat pump system and defrosting mode thereof Download PDFInfo
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- CN112665216A CN112665216A CN202011359766.0A CN202011359766A CN112665216A CN 112665216 A CN112665216 A CN 112665216A CN 202011359766 A CN202011359766 A CN 202011359766A CN 112665216 A CN112665216 A CN 112665216A
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- 238000010257 thawing Methods 0.000 title claims abstract description 105
- 239000007788 liquid Substances 0.000 claims abstract description 67
- 238000010438 heat treatment Methods 0.000 claims abstract description 63
- 230000001502 supplementing effect Effects 0.000 claims abstract description 22
- 239000003507 refrigerant Substances 0.000 claims description 68
- 230000009467 reduction Effects 0.000 claims description 9
- 238000004378 air conditioning Methods 0.000 abstract description 3
- 238000010586 diagram Methods 0.000 description 17
- 239000000203 mixture Substances 0.000 description 9
- 230000007246 mechanism Effects 0.000 description 7
- 238000000034 method Methods 0.000 description 6
- 230000008569 process Effects 0.000 description 4
- 239000013589 supplement Substances 0.000 description 4
- 238000005057 refrigeration Methods 0.000 description 3
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Abstract
The invention relates to the field of defrosting of an air conditioner, in particular to a heat pump system and a defrosting mode thereof.A gas-liquid separator is connected with an outdoor heat exchanger and an indoor heat exchanger, the indoor heat exchanger is provided with an auxiliary heating device and an internal fan, a compressor air supplementing port is communicated with a compressor air suction port through a bypass branch, a defrosting control valve group is arranged on the bypass branch, the gas-liquid separator is connected with an outlet pipe communicated with the bypass branch, a compressor air exhaust port is connected with a four-way reversing valve used for switching between a heating mode and a defrosting mode, and the four-way reversing valve comprises a first valve port communicated with the indoor heat exchanger, a second valve port communicated with the compressor air exhaust port, a third valve port communicated with the outdoor heat. According to the invention, through designing the air conditioning system, continuous heat supply to the indoor can be realized during defrosting, indoor comfort during defrosting is ensured, indoor temperature fluctuation during defrosting can be reduced, and thermal comfort is improved.
Description
Technical Field
The invention relates to the field of air conditioner defrosting, in particular to a heat pump system and a defrosting mode.
Background
When the heat pump air conditioner operates in a heating mode under an outdoor low-temperature environment, the surface temperature of an outdoor heat exchanger is low, and when the surface temperature is lower than 0 ℃, the surface of the heat exchanger is easy to frost, so that the heating effect of the air conditioner is seriously influenced. The existing heat pump system defrosting mode mainly comprises refrigeration cycle defrosting. The refrigeration cycle defrosting is that the system is switched from the heating cycle to the refrigeration cycle through the four-way reversing valve during defrosting so as to defrost, and an indoor heat exchanger is used as an evaporator during defrosting, so that heat can be absorbed from the indoor space, and thermal comfort and user experience during defrosting are seriously influenced.
According to the invention, through designing the air conditioning system, continuous heat supply to the indoor can be realized during defrosting, indoor comfort during defrosting is ensured, indoor temperature fluctuation during defrosting can be reduced, and thermal comfort is improved.
Disclosure of Invention
In order to solve the above problems, the present invention provides a heat pump system and a defrosting method. The invention is realized by adopting the following scheme:
a heat pump system comprises a compressor, a four-way reversing valve, an indoor heat exchanger, an outdoor heat exchanger and a bypass branch, wherein the gas-liquid separator is connected with the outdoor heat exchanger and the indoor heat exchanger, the indoor heat exchanger is provided with an auxiliary heating device and an inner fan, the compressor is provided with an air supplementing port, an air suction port and an exhaust port, the air supplementing port of the compressor is communicated with the air suction port of the compressor through the bypass branch, the bypass branch is provided with a defrosting control valve group, the gas-liquid separator is connected with an outlet pipe communicated with the bypass branch, the exhaust port of the compressor is connected with the four-way reversing valve used for switching between a heating mode and a defrosting mode, the four-way reversing valve comprises a first valve port, a second valve port, a third valve port and a fourth valve port, the first valve port is communicated with the indoor heat exchanger, the second valve port, the fourth valve port is communicated with a suction port of the compressor. The auxiliary heating device of the indoor unit is started during defrosting, and hot air can be continuously blown out during defrosting through the control of the rotating speed of the inner fan.
Preferably, a large stop valve is arranged on a pipeline of the indoor heat exchanger connected with the four-way reversing valve, and a small stop valve is arranged on a pipeline of the indoor heat exchanger connected with the gas-liquid separator.
Preferably, the bypass branch comprises an air supply section connected with an air supply port of the compressor and an air suction section connected with an air suction port of the compressor, the air supply section and the air suction section are provided with defrosting control valve groups, and the outlet pipe is communicated with the joint of the air supply section and the air suction section.
Preferably, an indoor throttling device is arranged on a pipeline between the gas-liquid separator and the small stop valve.
Preferably, the indoor throttle device is arranged to be in a closed state when the heat pump system is operating in the defrost mode.
Preferably, an outdoor throttling device is arranged on a pipeline of the gas-liquid separator connected with the outdoor heat exchanger.
Preferably, the defrosting control valve group is an electromagnetic three-way valve arranged at the joint of the outlet pipe, the air supplementing section and the air suction section.
Preferably, the defrosting control valve group comprises a first electromagnetic two-way valve arranged on the air supply section and a second electromagnetic two-way valve arranged on the air suction section.
The defrosting mode of the heat pump system is as follows: when the tube temperature of the outdoor heat exchanger is lower than the frosting temperature, judging that the heat pump system operates in a defrosting mode, otherwise, judging that the heat pump system keeps operating in a heating mode; when the heat pump system operates in a heating mode, the bypass branch is controlled to cut off the air suction section and keep the air replenishing section smooth, the switching four-way reversing valve enables the second valve port to be communicated with the first valve port and the third valve port to be communicated with the fourth valve port, and the large stop valve and the small stop valve are in an open state; when the heat pump system operates in a defrosting mode, the bypass branch is controlled to cut off the air supplementing section and keep the air suction section unblocked, the four-way switching valve enables the first valve port to be communicated with the fourth valve port and the second valve port to be communicated with the third valve port, the indoor throttling device is in a closed state, and the auxiliary heating device is started.
Preferably, when the heat pump system is switched from the defrosting mode to the heating mode, the compressor operates at the defrosting frequency after the compressor operates in a frequency reducing mode or stops operating for a preset time t1, and the indoor throttling device is closed and the four-way reversing valve is reversed when the compressor operates in the frequency reducing mode or stops operating for a preset time t 1; when the heat pump system is switched to a defrosting mode from a heating mode, the compressor operates at a defrosting frequency after the compressor operates in a frequency reduction mode or stops operating for a preset time T1, the indoor throttling device is closed and the four-way reversing valve is reversed when the compressor operates in a frequency reduction mode or stops operating for a preset time T1, Tc is detected when the compressor operates in a frequency reduction mode or stops operating for a preset time T1, if Tc is greater than or equal to T1, the inner fan operates at a preset rotating speed V1, if Tc is less than T1, the inner fan operates at a preset rotating speed V2, V1 is greater than V2, Tc is the temperature of a refrigerant in a pipeline in the indoor heat exchanger, and T1 is a preset temperature threshold.
Compared with the prior art, the invention has the following beneficial effects:
according to the invention, by designing the air conditioning system, the compressor of the heat pump system is not stopped during defrosting, continuous heat supply can be carried out indoors during defrosting, and the influence of defrosting on indoor thermal comfort is reduced, so that the indoor environment temperature during defrosting is ensured, and the thermal comfort of the air conditioner is improved.
Drawings
FIG. 1 is a system cycle of a heat pump system provided by the present invention;
FIG. 2 is a diagram of a system cycle during a heating mode of the heat pump system provided in FIG. 1;
FIG. 3 is a diagram of a system cycle during a defrost mode of the heat pump system provided in FIG. 1;
FIG. 4 is a system cycle of a heat pump system provided by the present invention;
FIG. 5 is a diagram of a system cycle during a heating mode of the heat pump system provided in FIG. 4;
FIG. 6 is a diagram of a system cycle during a defrost mode of the heat pump system provided in FIG. 4;
FIG. 7 is a system cycle of a heat pump system provided by the present invention;
FIG. 8 is a diagram of a system cycle during a heating mode of the heat pump system provided in FIG. 7;
FIG. 9 is a diagram of a system cycle during a defrost mode of the heat pump system provided in FIG. 7;
FIG. 10 is a system cycle of a heat pump system provided by the present invention;
FIG. 11 is a diagram of a system cycle during a heating mode of the heat pump system provided in FIG. 10;
fig. 12 is a diagram of a system cycle during a defrost mode of the heat pump system provided in fig. 10.
Fig. 1 to 3 include: an indoor heat exchanger 101, an auxiliary heating device 102, an inner fan 103, a large stop valve 104, a four-way reversing valve 105, a compressor 106, an electromagnetic three-way valve 107, an outdoor heat exchanger 108, an outer fan 109, an outdoor throttling device 110, a gas-liquid separator 111, an indoor throttling device 112 and a small stop valve 113;
fig. 4 to 6 include: the system comprises an indoor heat exchanger 201, an auxiliary heating device 202, an inner fan 203, a large stop valve 204, a four-way reversing valve 205, a compressor 206, a first electromagnetic two-way valve 207, a second electromagnetic two-way valve 208, an outdoor heat exchanger 209, an outer fan 210, an outdoor throttling device 211, a gas-liquid separator 212, an indoor throttling device 213 and a small stop valve 214.
Fig. 7 to 9 include: an indoor heat exchanger 301, an auxiliary heating device 302, an inner fan 303, a large stop valve 304, a four-way reversing valve 305, a compressor 306, an electromagnetic two-way valve 307, an outdoor heat exchanger 308, an outer fan 309, a gas-liquid separator 310, an indoor throttling device 311, a small stop valve 312 and a throttling device 313;
fig. 10 to 12 include: the system comprises an indoor heat exchanger 401, an auxiliary heating device 402, an inner fan 403, a large stop valve 404, a four-way reversing valve 405, a compressor 406, a throttling device 407, an outdoor heat exchanger 408, an outer fan 409, a gas-liquid separator 410, an indoor throttling device 411 and a small stop valve 412.
Detailed Description
To facilitate an understanding of the present invention for those skilled in the art, the present invention will be described in further detail below with reference to specific embodiments and accompanying drawings.
Example 1
Referring to fig. 1 to 3, the heat pump system provided by the present invention includes a compressor 106, a four-way reversing valve 105, an indoor heat exchanger 101, an outdoor heat exchanger 108, and a bypass branch, where the gas-liquid separator 111 is connected to the outdoor heat exchanger 108 and the indoor heat exchanger 101, the indoor heat exchanger 101 is provided with an auxiliary heating device 102 and an inner fan 103, the inner fan 103 is used to drive air around the indoor heat exchanger 101 and the auxiliary heating device 102 to flow, the outdoor heat exchanger 108 is provided with an outer fan 109 used to drive air around the outdoor heat exchanger 108 to flow, the compressor 106 is provided with an air supplement port, an air suction port, and an exhaust port, the compressor 106 is used to compress a refrigerant entering from the air supplement port and the air suction port, the refrigerant is compressed to form a high-temperature and high-pressure gaseous refrigerant, the refrigerant is discharged from the exhaust port, the air supplement port of the compressor, the gas-liquid separator 111 is connected with an outlet pipe communicated with a bypass branch, the exhaust port of the compressor 106 is connected with a four-way reversing valve 105 used for switching between a heating mode and a defrosting mode, the four-way reversing valve 105 comprises a first valve port, a second valve port, a third valve port and a fourth valve port, the first valve port is communicated with the indoor heat exchanger 101, the second valve port is communicated with the exhaust port of the compressor 106, the third valve port is communicated with the outdoor heat exchanger 108, the fourth valve port is communicated with the suction port of the compressor 106, a large stop valve 104 is arranged on a pipeline of the indoor heat exchanger 101 connected with the four-way reversing valve 105, a small stop valve 113 is arranged on a pipeline of the indoor heat exchanger 101 connected with the gas-liquid separator 111, an indoor throttling device 112 is arranged on a pipeline between the gas-liquid separator 111 and the small stop valve 113, and an outdoor throttling device, the bypass branch comprises an air supplementing section connected with an air supplementing port of the compressor 106 and an air suction section connected with an air suction port of the compressor 106, the air supplementing section and the air suction section are provided with defrosting control valve groups, and the outlet pipe is communicated with the joint of the air supplementing section and the air suction section.
The outdoor heat exchanger and the indoor heat exchanger can be tube-fin heat exchangers, microchannel heat exchangers and the like, and are selected according to the use condition.
The indoor throttle device 112 is configured to: when the heat pump system is operating in the defrost mode, the indoor throttle 112 is in a closed state.
The outdoor throttling device 110 can select a throttling mechanism such as a capillary tube, an electronic expansion valve, a throttling short tube and the like, and the indoor throttling device 112 can select a throttling mechanism such as an electronic expansion valve, an electromagnetic valve and the like matched with the capillary tube.
The defrosting control valve set of the embodiment is an electromagnetic three-way valve 107 arranged at the joint of the outlet pipe, the air supplementing section and the air suction section.
The defrosting mode of the heat pump system is as follows: when the temperature of the outdoor heat exchanger 108 is lower than the frosting temperature, judging that the heat pump system operates in a defrosting mode, otherwise, judging that the heat pump system keeps operating in a heating mode; when the heat pump system operates in a heating mode, a bypass branch is controlled to cut off a suction section and keep an air replenishing section unblocked, the switching four-way reversing valve 105 enables a second valve port to be communicated with a first valve port and a third valve port to be communicated with a fourth valve port, and the large stop valve 104 and the small stop valve 113 are in an open state; when the heat pump system operates in a defrosting mode, the bypass branch is controlled to cut off the air supply section and keep the air suction section unblocked, the switching four-way reversing valve 105 enables the first valve port to be communicated with the fourth valve port and the second valve port to be communicated with the third valve port, the large stop valve indoor throttling device 112 is in a closed state, and the auxiliary heating device 102 is started.
When the heat pump system is switched from a defrosting mode to a heating mode, the compressor 106 operates at a defrosting frequency after the compressor 106 operates in a frequency reducing mode or stops operating for a preset time t1, the indoor throttling device 112 is closed when the compressor 106 operates in a frequency reducing mode or stops operating for a preset time t1, and the four-way reversing valve 105 is reversed; when the heat pump system is switched to the defrosting mode from the heating mode, the compressor 106 operates at the defrosting frequency after the compressor 106 operates in a frequency reduction mode or stops operating for a preset time T1, the indoor throttling device 112 is closed and the four-way reversing valve 105 is reversed when the compressor 106 operates in the frequency reduction mode or stops operating for a preset time T1, Tc is detected when the compressor 106 operates in the frequency reduction mode or stops operating for a preset time T1, if Tc is greater than or equal to T1, the inner fan 103 operates at a preset rotating speed V1, if Tc is less than T1, the inner fan 103 operates at a preset rotating speed V2, V1 is greater than V2, Tc is the temperature of a refrigerant in a pipeline in the indoor heat exchanger 101, and T1 is a preset temperature.
Referring to fig. 1 to 3, fig. 1, 2 and 3 are a system configuration diagram, a system cycle diagram in a heating mode and a system cycle diagram in a defrosting mode of a heat pump system, respectively, where the defrosting control valve set of the present embodiment is an electromagnetic three-way valve 107 disposed at a connection of an outlet pipe, an air supply section and an air suction section, and a heating mode flow and a defrosting mode flow of the heat pump system are as follows:
as shown in fig. 2, during the heating mode, when the heat pump system operates in the heating mode, the liquid refrigerant in the outdoor heat exchanger 108 exchanges heat with the outdoor environment, absorbs heat in the environment and vaporizes, the generated low-pressure refrigerant vapor flows into the third port of the four-way reversing valve 105, the refrigerant flows into the suction port of the compressor 106 through the fourth port of the four-way reversing valve 105, and the low-pressure refrigerant is sucked into the compressor 106, compressed and discharged at high pressure. The high-temperature high-pressure gaseous refrigerant discharged from the compressor 106 enters the second valve port of the four-way reversing valve 105, the refrigerant enters the indoor heat exchanger 101 through the first valve port of the four-way reversing valve 105, the gaseous refrigerant in the outdoor heat exchanger 108 is cooled by indoor air, heat is released to the indoor environment and then condensed into high-pressure liquid, the high-pressure liquid is throttled by the indoor throttling device 112 and then changed into a low-pressure low-temperature gas-liquid two-phase mixture, the low-pressure low-temperature gas-liquid two-phase mixture enters the gas-liquid separator 111, at the moment, the electromagnetic three-way valve 107 only connects the outlet of the gaseous refrigerant of the gas-liquid separator 111 with the air supplementing port of the compressor 106, the gaseous refrigerant enters the compressor 106 from the air supplementing port of the compressor 106 after being discharged from the gas-.
The system cycle of the heat pump system during the defrosting mode is as shown in fig. 3, and when the temperature of the tube of the outdoor heat exchanger 108 is reduced to a certain temperature, it is determined that the outdoor heat exchanger 108 is frosted more heavily, and defrosting is required. When defrosting starts, the compressor 106 firstly reduces the frequency or stops, and then rises to the defrosting frequency after the four-way reversing valve 105 reverses and the indoor throttling device 112 is closed, only a small amount of refrigerant or no refrigerant flows back to the indoor heat exchanger 101 at the moment, and most of the refrigerant only circulates at the outdoor machine side. The refrigerant flows out from the outdoor heat exchanger 108 and is throttled by the outdoor throttling device 110, the generated vapor-liquid mixture enters the gas-liquid separator 111, the refrigerant cannot flow back to the indoor heat exchanger 101 due to the closing of the indoor throttling device 112, the liquid refrigerant is stored in the gas-liquid separator 111, at the moment, the electromagnetic three-way valve 107 only connects the air outlet of the gas-liquid separator 111 with the suction port of the compressor 106, the vapor refrigerant enters the compressor 106 from the suction port of the compressor 106, and the high-temperature refrigerant vapor discharged by the compressor 106 enters the outdoor heat exchanger 108 for defrosting, and the steps are repeated. After defrosting is finished, the compressor 106 also starts to reduce the frequency or stop, and after the four-way reversing valve 105 is reversed and the indoor throttling device 112 is started, the frequency is increased to restore normal heating. Meanwhile, the auxiliary heating device is turned on during defrosting, the inner fan 103 continuously rotates, heat emitted by the auxiliary heating device 102 is blown to the indoor, the indoor temperature is not reduced during defrosting, and the thermal comfort during defrosting is improved.
This system has the following advantages: firstly, because the gas-liquid separator 111 is arranged in the system, the dryness of the refrigerant entering the evaporator in the refrigerating or heating process is reduced, and the refrigerating or heating effect of the system is improved. In addition, only a small amount of refrigerants or no refrigerants return to the indoor heat exchanger 101 during defrosting, most refrigerants in the system are circularly used for defrosting outside the room, low-temperature refrigerants during defrosting cannot enter the indoor heat exchanger 101 in a large amount, fluctuation of indoor temperature during defrosting can be effectively reduced, the auxiliary heating device 102 of the indoor unit is started during defrosting, the inner fan 103 blows heat emitted by the auxiliary heating device 102 to the indoor space, heat is not absorbed from the indoor space during defrosting, heating comfort is improved, and the purpose of constant-heating defrosting can be achieved.
Because only a very small amount of refrigerant flows into the indoor heat exchanger 101 during defrosting, the inner pipe temperature drops a little bit under the suction action of the compressor 106, which affects the outlet air temperature during defrosting, and in order to solve the problem, the control method of the inner fan 103 is provided as follows, which can effectively increase the inner pipe temperature before defrosting and ensure the outlet air temperature during defrosting:
before defrosting, the system detects the temperature of the inner pipe, if the temperature of the inner pipe is lower than a preset value T, the inner fan 103 reduces the rotating speed to store heat for the evaporator, defrosting is not started temporarily, and if the temperature of the inner pipe rises to be close to the preset value T or the heat storage time reaches a preset value T, the defrosting mode is normally started.
In addition, for the heat pump system, three additional embodiments are proposed as follows:
example 2
Referring to fig. 4 to 6, fig. 4, 5, and 6 are a system configuration diagram of a heat pump system, a system cycle diagram in a heating mode, and a system cycle diagram in a defrosting mode, respectively, where a defrosting control valve set of the present embodiment includes a first electromagnetic two-way valve 207 disposed on a gas supply section and a second electromagnetic two-way valve 208 disposed on a gas suction section, and the present embodiment is different from embodiment 1 in that two electromagnetic two-way valves are used instead of an electromagnetic three-way valve. The connection and disconnection of the air suction section and the air supply section of the bypass branch are controlled by the opening and closing of the two electromagnetic two-way valves.
The outdoor throttling device 211 can be selected from the throttling mechanisms such as a capillary tube, an electronic expansion valve and a throttling short tube, and the indoor throttling device 213 can be selected from the throttling mechanisms such as an electronic expansion valve, an electromagnetic valve and an electromagnetic valve which are matched with the capillary tube. The heating mode process and the defrosting mode process of the heat pump system are respectively as follows:
in the heating mode, as shown in fig. 5, the system cycle of the heat pump system of the present invention is that the liquid refrigerant in the outdoor heat exchanger 209 exchanges heat with the outdoor environment, absorbs heat in the environment and is gasified, and the generated low-pressure refrigerant vapor is sucked by the compressor 206 and is compressed and then discharged at high pressure. The high-temperature high-pressure gaseous refrigerant discharged from the compressor 206 enters the indoor heat exchanger 201, is cooled by indoor air, is condensed into high-pressure liquid after releasing heat to the indoor environment, is throttled by the indoor throttling device 213 and then becomes a low-pressure low-temperature gas-liquid two-phase mixture, and then enters the gas-liquid separator 212, at this time, the second electromagnetic two-way valve 208 is closed, the first electromagnetic two-way valve 207 is opened to communicate the gas outlet of the gas-liquid separator 212 with the gas supplementing port of the compressor 206, the gaseous refrigerant is discharged from the gas-liquid separator 212 and then enters the compressor 206 from the gas supplementing port of the compressor 206, and the liquid refrigerant flows back to the outdoor heat exchanger 209 to continue heating circulation.
In defrosting mode, as shown in fig. 6, when the system cycle of the heat pump system of the present invention is started, the compressor 206 is first turned down or stopped, and then turned over by the four-way reversing valve 205 and the indoor throttling device 213 is closed, and then the system cycle is raised to a defrosting frequency, during which only a small amount of refrigerant or no refrigerant flows back to the indoor heat exchanger 201, and most of the refrigerant circulates only at the outdoor unit side. The refrigerant flows out of the outdoor heat exchanger 209 and is throttled by the outdoor throttling device 211, the generated vapor-liquid mixture enters the gas-liquid separator 212, the refrigerant cannot flow back to the indoor heat exchanger 201 due to the closing of the indoor throttling device 213, the liquid refrigerant is stored in the gas-liquid separator 212, the first electromagnetic two-way valve 207 is closed at the moment, the second electromagnetic two-way valve 208 is opened to connect the air outlet of the gas-liquid separator 212 with the suction port of the compressor 206, the vapor refrigerant enters the compressor 206 from the suction port of the compressor 206, and the high-temperature refrigerant steam discharged by the compressor 206 enters the outdoor heat exchanger 209 to be defrosted in. After defrosting is completed, the compressor 206 also starts to reduce the frequency or stop, and after the four-way reversing valve 205 is reversed and the indoor throttling device 213 is opened, the frequency is increased to restore normal heating.
Example 3
Referring to fig. 7 to 9, fig. 7, 8 and 9 are respectively a system configuration diagram of a heat pump system, a system cycle diagram in a heating mode and a system cycle diagram in a defrosting mode, and this embodiment is different from embodiment 1 in that the compressor 306 in this embodiment is not provided with an air supplement port, the compressor 306 is provided with only an exhaust port and an air suction port, the air suction port of the compressor 306 is connected to the gas-liquid separator 310 through an outlet pipe, the outlet pipe is provided with only one throttling device 313 and an electromagnetic two-way valve 307, a fourth valve port of the four-way reversing valve 305 is communicated with the air suction port of the compressor 306, and the communication and disconnection of a bypass branch connecting the compressor 306 and the gas-liquid separator 310 are controlled by opening and closing the electromagnetic two-way valve.
The throttling device 313 can select a capillary tube, an electronic expansion valve, a throttling short tube and other throttling mechanisms, the indoor throttling device 311 can select an electronic expansion valve, an electromagnetic valve and a capillary tube and other throttling mechanisms, and the throttling device 313 can select a capillary tube, an electronic expansion valve, a capillary short tube and other throttling mechanisms. The heating process and the defrosting process of the heat pump system are respectively as follows:
during the heating mode, as shown in fig. 8, the system cycle of the heat pump system of the present invention is that the liquid refrigerant in the outdoor heat exchanger 308 exchanges heat with the outdoor environment to absorb the heat in the environment and gasify the heat, and the generated low-pressure refrigerant vapor is sucked by the compressor 306 and then discharged at high pressure after being compressed. The high-temperature high-pressure gaseous refrigerant discharged from the compressor 306 enters the indoor heat exchanger 301, is cooled by indoor air, is condensed into high-pressure liquid after releasing heat to the indoor environment, is throttled by the indoor throttling device 311 to become a low-pressure low-temperature gas-liquid two-phase mixture, then enters the gas-liquid separator 310, at the moment, the electromagnetic two-way valve 307 is closed, the bypass pipeline is not communicated, the gaseous refrigerant is gathered at the top of the gas-liquid separator 310, and the liquid refrigerant flows back to the outdoor heat exchanger 308 to continue heating circulation.
During the operation in the defrosting mode, the system cycle of the heat pump system of the present invention is as shown in fig. 9, and at the beginning, the compressor 306 first decreases the frequency or stops, and then increases to the defrosting frequency after the four-way reversing valve 305 reverses and the indoor throttling device 311 is closed, during which only a small amount of refrigerant or no refrigerant flows back to the indoor heat exchanger 301, and most of the refrigerant circulates only at the outdoor machine side. The gas-liquid mixture generated after the refrigerant flows out of the outdoor heat exchanger 308 enters the gas-liquid separator 310, the refrigerant cannot flow back to the indoor heat exchanger 301 due to the closing of the indoor throttling device 311, the liquid refrigerant is stored in the gas-liquid separator 310, at the moment, the electromagnetic two-way valve 307 is opened to connect the air outlet of the gas-liquid separator 310 with the air suction port of the compressor 306, the gas-state refrigerant enters the compressor 306 from the air suction port of the compressor 306 after being throttled by the throttling device 313, and the high-temperature refrigerant steam discharged by the compressor 306 enters the outdoor heat exchanger 308 to be defrosted. After defrosting is finished, the compressor 306 also starts to reduce the frequency or stop, and after the four-way reversing valve 305 reverses and the indoor throttling device 311 is started, the frequency is increased to restore normal heating.
Example 4
The outlet pipe is connected, the fourth valve port of the four-way reversing valve 405 is communicated with the suction port of the compressor 406, only one throttling device 407 is arranged on the outlet pipe, and the gas refrigerant outlet of the gas-liquid separator 410 is directly communicated with the suction port of the compressor 406 through the throttling device 407.
The throttle device 407 may be a capillary tube, an electronic expansion valve, a throttle sleeve, or other throttle device, and the indoor throttle device 411 may be an electronic expansion valve, an electromagnetic valve, or other throttle device in cooperation with a capillary tube. The heating process and the defrosting process of the heat pump system are respectively as follows:
in the system cycle of the heat pump system during the heating mode operation, as shown in fig. 11, the liquid refrigerant in the outdoor heat exchanger 408 exchanges heat with the outdoor environment to absorb heat in the environment and gasify the heat, and the generated low-pressure refrigerant vapor is sucked by the compressor 406 and is compressed and then discharged at high pressure. The high-temperature high-pressure gaseous refrigerant discharged from the compressor 406 enters the indoor heat exchanger 401, is cooled by indoor air, is condensed into high-pressure liquid after releasing heat to the indoor environment, is throttled by the indoor throttling device 411 to become a low-pressure low-temperature gas-liquid two-phase mixture, then enters the gas-liquid separator 410, is throttled by the throttling device 407, enters the compressor 406 from the suction port of the compressor 406, and flows back to the outdoor heat exchanger 408 to continue the heating cycle.
The system cycle of the heat pump system during the defrosting mode operation is as shown in fig. 12, and at the beginning, the compressor 406 first decreases the frequency or stops, and then increases to the defrosting frequency after the four-way reversing valve 405 reverses and the indoor throttling device 411 is closed, only a small amount of refrigerant or no refrigerant flows back to the indoor heat exchanger 401 during the period, and most of the refrigerant circulates only at the outdoor machine side. The vapor-liquid mixture generated after the refrigerant flows out of the outdoor heat exchanger 408 enters the gas-liquid separator 410, the refrigerant cannot flow back to the indoor heat exchanger 401 due to the closing of the indoor throttling device 411, the liquid refrigerant is stored in the gas-liquid separator 410, the vapor refrigerant enters the compressor 406 from the suction port of the compressor 406 after being throttled by the throttling device 407, and the high-temperature refrigerant vapor discharged by the compressor 406 enters the outdoor heat exchanger 408 for defrosting, and so on. After defrosting is finished, the compressor 406 also firstly reduces the frequency or stops, and then increases the frequency to recover normal heating after the four-way reversing valve 405 reverses and the indoor throttling device 411 is opened.
In the description of the present invention, it is to be understood that the indicated orientations or positional relationships are based on the orientations or positional relationships shown in the drawings and are only for convenience in describing the present invention and simplifying the description, but are not intended to indicate or imply that the indicated devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and are not to be construed as limiting the present invention.
Furthermore, the terms "first", "second", etc. are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless specifically defined otherwise.
In the present invention, unless otherwise expressly stated or limited, the terms "connected," "secured," and the like are to be construed broadly, e.g., as meaning permanently attached, removably attached, or integral to one another; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
While the invention has been described in conjunction with the specific embodiments set forth above, it is evident that many alternatives, modifications, and variations will be apparent to those skilled in the art in light of the foregoing description. Accordingly, it is intended to embrace all such alternatives, modifications, and variations that fall within the scope of the included claims.
Claims (10)
1. A heat pump system, characterized by: the system comprises a compressor, a four-way reversing valve, an indoor heat exchanger, an outdoor heat exchanger and a bypass branch, wherein the gas-liquid separator is connected with the outdoor heat exchanger and the indoor heat exchanger, the indoor heat exchanger is provided with an auxiliary heating device and an internal fan, the compressor is provided with an air supplementing port, an air suction port and an exhaust port, the air supplementing port of the compressor is communicated with the air suction port of the compressor through the bypass branch, the bypass branch is provided with a defrosting control valve group, the gas-liquid separator is connected with an outlet pipe communicated with the bypass branch, the exhaust port of the compressor is connected with the four-way reversing valve used for switching between a heating mode and a defrosting mode, the four-way reversing valve comprises a first valve port, a second valve port, a third valve port and a fourth valve port, the first valve port is communicated with the indoor heat exchanger, the, the fourth valve port is communicated with a suction port of the compressor.
2. The heat pump system of claim 1, wherein: the pipeline of the indoor heat exchanger connected with the four-way reversing valve is provided with a large stop valve, and the pipeline of the indoor heat exchanger connected with the gas-liquid separator is provided with a small stop valve.
3. The heat pump system of claim 1, wherein: the bypass branch comprises an air supplementing section connected with an air supplementing port of the compressor and an air suction section connected with an air suction port of the compressor, the air supplementing section and the air suction section are provided with defrosting control valve groups, and the outlet pipe is communicated with the joint of the air supplementing section and the air suction section.
4. The heat pump system of claim 2, wherein: and an indoor throttling device is arranged on a pipeline between the gas-liquid separator and the small stop valve.
5. The defrosting mode of a heat pump system according to claim 4, characterized in that: the indoor throttle is configured to be in a closed state when the heat pump system is operating in a defrost mode.
6. The heat pump system of claim 1, wherein: and an outdoor throttling device is arranged on a pipeline of the gas-liquid separator connected with the outdoor heat exchanger.
7. The heat pump system of claim 3, wherein: the defrosting control valve group is an electromagnetic three-way valve arranged at the joint of the outlet pipe, the air supplementing section and the air suction section.
8. The heat pump system of claim 3, wherein: the defrosting control valve group comprises a first electromagnetic two-way valve arranged on the air supply section and a second electromagnetic two-way valve arranged on the air suction section.
9. A defrosting mode of a heat pump system is characterized in that: the heat pump system is the heat pump system according to claims 1 to 7, when the outdoor heat exchanger tube temperature is lower than the frosting temperature, the heat pump system is judged to be operated in a defrosting mode, otherwise, the heat pump system is judged to be kept operated in a heating mode; when the heat pump system operates in a heating mode, the bypass branch is controlled to cut off the air suction section and keep the air replenishing section smooth, the switching four-way reversing valve enables the second valve port to be communicated with the first valve port and the third valve port to be communicated with the fourth valve port, and the large stop valve and the small stop valve are in an open state; when the heat pump system operates in a defrosting mode, the bypass branch is controlled to cut off the air supplementing section and keep the air suction section unblocked, the four-way switching valve enables the first valve port to be communicated with the fourth valve port and the second valve port to be communicated with the third valve port, the indoor throttling device is in a closed state, and the auxiliary heating device is started.
10. A defrosting mode of a heat pump system according to claim 9, characterized in that: when the heat pump system is switched from a defrosting mode to a heating mode, the compressor operates at a defrosting frequency after the compressor operates in a frequency reducing mode or stops operating for a preset time t1, and the indoor throttling device is closed and the four-way reversing valve is reversed when the compressor operates in a frequency reducing mode or stops operating for a preset time t 1; when the heat pump system is switched to a defrosting mode from a heating mode, the compressor operates at a defrosting frequency after the compressor operates in a frequency reduction mode or stops operating for a preset time T1, the indoor throttling device is closed and the four-way reversing valve is reversed when the compressor operates in a frequency reduction mode or stops operating for a preset time T1, Tc is detected when the compressor operates in a frequency reduction mode or stops operating for a preset time T1, if Tc is greater than or equal to T1, the inner fan operates at a preset rotating speed V1, if Tc is less than T1, the inner fan operates at a preset rotating speed V2, V1 is greater than V2, Tc is the temperature of a refrigerant in a pipeline in the indoor heat exchanger, and T1 is a preset temperature threshold.
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| CN202011359766.0A CN112665216A (en) | 2020-11-27 | 2020-11-27 | Heat pump system and defrosting mode thereof |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202011359766.0A CN112665216A (en) | 2020-11-27 | 2020-11-27 | Heat pump system and defrosting mode thereof |
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| CN112665216A true CN112665216A (en) | 2021-04-16 |
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Application publication date: 20210416 |