CN216744986U - Air source heat pump unit for avoiding cold and heat offset during defrosting - Google Patents
Air source heat pump unit for avoiding cold and heat offset during defrosting Download PDFInfo
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- CN216744986U CN216744986U CN202122298880.3U CN202122298880U CN216744986U CN 216744986 U CN216744986 U CN 216744986U CN 202122298880 U CN202122298880 U CN 202122298880U CN 216744986 U CN216744986 U CN 216744986U
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Abstract
The utility model belongs to the technical field of heat pump units, and particularly relates to an air source heat pump unit for avoiding cold and heat offset during defrosting. The technical scheme is as follows: the utility model provides an avoid air source heat pump set that cold and hot offset during defrosting, includes the compression unit, and the compression unit has indoor heat exchanger unit through the pipe connection, and the other end of indoor heat exchanger unit and the parallel connection have a plurality of outdoor heat exchanger units between the compression unit, are connected with the solenoid valve on the pipeline of outdoor heat exchanger unit, are connected with the solenoid valve between the pipeline of pipeline between compression unit and the indoor heat exchanger unit and the pipeline of outdoor heat exchanger unit. The utility model provides an air source heat pump unit for avoiding cold and heat offset during defrosting.
Description
Technical Field
The utility model belongs to the technical field of heat pump units, and particularly relates to an air source heat pump unit for avoiding cold and heat offset during defrosting.
Background
The policy of 'carbon peak reaching' and 'carbon neutralization' in China ensures that heat and cold for buildings can be electrified comprehensively in the future. Compared with a ground source heat pump, the air source heat pump has the advantages of flexible installation, low initial investment and the like, and is important equipment for clean heat supply in China. However, when the evaporator surface temperature of the air source heat pump is lower than the dew point temperature of air during operation in winter heating conditions, the fin surfaces gradually frost. The frost layer increases the heat exchange resistance between air and a refrigerant, and reduces the total heat transfer coefficient; meanwhile, the frost layer blocks the gaps of the fins, so that the flow resistance of air is increased, and the air quantity of the fan is reduced; when the frosting is serious, the unit may be shut down for protection. Experimental results of brayan et al show that frosting on the surface of the heat exchanger can result in a reduction of the heat exchange by about 40%. According to the research result of sanders, the unit performance of the air source heat pump is reduced by 35% under the frosting working condition. In the research of Beijing university of industry, the heat supply of the unit is reduced by 29 percent when the outdoor heat exchanger frosts. Therefore, how to defrost efficiently is a key problem to be solved urgently in the application of heat pump technology.
The conventional common defrosting modes of the air source heat pump mainly comprise electric heating defrosting, reverse defrosting, hot gas bypass defrosting and heat storage defrosting. Electrical heating defrosting: the heat exchanger is stable and effective, does not influence indoor heating, but has large power consumption and low conversion efficiency. ② reverse circulation defrosting: when defrosting, heat supply is stopped, heat is absorbed from indoor or heat supply heating media, indoor temperature is obviously reduced, heat supply quality is seriously affected (the indoor temperature is reduced by 2-7 ℃ during reverse defrosting), and cold and heat are offset. Hot gas bypass defrosting: the steam of the high-temperature refrigerating machine is sent into the outdoor heat exchanger for defrosting, the defrosting energy comes from the compressor to do work, the defrosting can provide less heat, the defrosting time is long, and the energy consumption is high. Fourthly, heat storage defrosting: the independent energy accumulator is arranged, when the heat pump supplies heat normally, part of heat is stored in the heat accumulator, when defrosting is performed, the heat accumulator supplies heat to defrost, the indoor temperature can be prevented from dropping, but reverse circulation defrosting is essential, and cold and heat can still be offset. If water is used for heat storage, the unit has larger volume; if phase change heat storage is adopted, the phase change material has poor stability, short life span and high manufacturing cost. Through analysis and calculation, cold and heat offset exists during reverse defrosting or heat storage defrosting, namely, the heat of indoor air or hot water or phase change heat storage absorbed by defrosting is about 1/3-1/2, which is the power consumption of a former unit, so that the actual energy consumption of defrosting is improved by 40-50%, and the advantages of an air source heat pump are greatly weakened.
Disclosure of Invention
In order to solve the above problems in the prior art, an object of the present invention is to provide an air source heat pump unit that avoids the cold-heat offset during defrosting.
The technical scheme adopted by the utility model is as follows:
the utility model provides an avoid air source heat pump set that cold and hot offset during defrosting, includes the compression unit, and the compression unit has indoor heat exchanger unit through the pipe connection, and the other end of indoor heat exchanger unit and the parallel connection have a plurality of outdoor heat exchanger units between the compression unit, are connected with the solenoid valve on the pipeline of outdoor heat exchanger unit, are connected with the solenoid valve between the pipeline of pipeline between compression unit and the indoor heat exchanger unit and the pipeline of outdoor heat exchanger unit.
The utility model connects multiple groups of outdoor heat exchanger units in parallel, thereby defrosting one or more outdoor heat exchangers in the normal heat supply state. When defrosting is carried out on one outdoor heat exchanger, the electromagnetic valve is remotely switched, so that the outdoor heat exchanger and the indoor heat exchanger can be used as condensers, and the other outdoor heat exchangers can be used as evaporators. At this time, when the outdoor heat exchanger is defrosted, normal indoor heat supply is not affected. The electromagnetic valves are arranged on the two branches for controlling the flow direction of the refrigerant in the outdoor heat exchanger unit, so that the reliable switching of the paths is ensured, and the situation of incomplete switching is avoided.
As a preferable scheme of the present invention, the indoor heat exchanger unit includes an indoor heat exchanger, one end of the indoor heat exchanger is connected to the compression unit through a pipeline, and the other end of the indoor heat exchanger is connected to an indoor expansion valve and an indoor check valve, which are connected in parallel, through a pipeline. In winter, after the heat of the refrigerant is released and condensed in the indoor heat exchanger, the refrigerant flows through the indoor check valve and enters the outdoor heat exchanger unit to absorb heat. In summer, the temperature of the refrigerant is reduced after heat release and condensation are finished, the refrigerant is blocked by an indoor one-way valve, the refrigerant enters an indoor expansion valve for throttling and pressure reduction, the temperature is reduced while the pressure is reduced, a low-temperature low-pressure refrigerant is obtained, and the low-temperature low-pressure refrigerant enters an indoor heat exchanger for absorbing heat.
As a preferred scheme of the utility model, the compression unit comprises a four-way valve, a compressor is connected between two compressor interfaces of the four-way valve through a pipeline, a third interface of the four-way valve is connected with the indoor heat exchanger unit through a pipeline, and the outdoor heat exchanger units are connected between the other end of the indoor heat exchanger unit and a fourth interface of the four-way valve in parallel.
As a preferred scheme of the present invention, the compression unit is a two-stage compression unit, a high-pressure end of the compression unit is connected to the indoor heat exchanger unit through a pipeline, the other end of the indoor heat exchanger unit is sequentially connected to the refrigerant gas-liquid separation unit through a pipeline, a gas phase interface of the refrigerant gas-liquid separation unit is connected to a middle end of the compression unit through a pipeline, and the plurality of outdoor heat exchanger units are connected in parallel between a liquid phase interface of the refrigerant gas-liquid separation unit and a low-pressure end of the compression unit.
The refrigerant gas-liquid separation unit can directly send the gaseous refrigerant or the gas-liquid mixed refrigerant to the middle end of the compression unit without discharging the gaseous refrigerant or the gas-liquid mixed refrigerant into the outdoor heat exchanger unit to absorb heat, so that the gaseous refrigerant is effectively utilized. The low-pressure end of the compression unit sucks low-pressure low-temperature refrigerant steam generated in the outdoor heat exchanger unit under the non-defrosting condition, and the low-pressure low-temperature refrigerant steam is mixed with the refrigerant separated from the refrigerant gas-liquid separation unit and enters the high-pressure end of the compression unit for compression. Therefore, the heating capacity is increased, the circulating refrigeration coefficient is improved, and the power consumption of the compressor is saved.
As a preferred scheme of the present invention, the compression unit includes a two-stage compressor, the two-stage compressor includes a low-pressure stage compression cylinder, an intermediate chamber, and a high-pressure stage compression cylinder, the outdoor heat exchanger unit is connected to the low-pressure stage compression cylinder through a pipeline, a gas phase interface of the refrigerant gas-liquid separation unit is connected to the intermediate chamber through a pipeline, and the indoor heat exchanger is connected to the high-pressure stage compression cylinder through a pipeline.
The low-pressure stage compression cylinder sucks low-pressure low-temperature refrigerant steam generated in the outdoor heat exchanger unit under the non-defrosting condition, the low-pressure low-temperature refrigerant steam is mixed with the refrigerant separated from the refrigerant gas-liquid separation unit, the mixture enters the high-pressure stage compression cylinder for compression, and the refrigerant is changed into high-temperature high-pressure gas. And the refrigerant passing through the outdoor heat exchanger unit under the non-defrosting working condition absorbs heat and then enters the low-pressure stage cylinder of the two-stage compressor again, and is mixed with the separated gaseous refrigerant and then is further compressed.
As a preferred embodiment of the present invention, the compression unit includes a low-pressure stage compressor and a high-pressure stage compressor connected by a pipeline, the outdoor heat exchanger unit is connected to the low-pressure stage compressor by a pipeline, a gas phase interface of the refrigerant gas-liquid separation unit is connected to a suction port of the high-pressure stage compressor by a pipeline, and the indoor heat exchanger is connected to a discharge port of the high-pressure stage compressor by a pipeline.
The low-pressure stage compressor sucks low-pressure low-temperature refrigerant steam generated in the outdoor heat exchanger unit under the non-defrosting working condition, the low-pressure low-temperature refrigerant steam is mixed with the refrigerant separated from the refrigerant gas-liquid separation unit, the mixed refrigerant enters the high-pressure stage compressor to be compressed, and the refrigerant is changed into high-temperature high-pressure gas. And the refrigerant passing through the outdoor heat exchanger unit under the non-defrosting working condition enters the low-pressure stage compressor again after absorbing heat.
As a preferable scheme of the utility model, the outdoor heat exchanger unit comprises an outdoor heat exchanger, one end of the outdoor heat exchanger, which is far away from the electromagnetic valve, is respectively connected with an outdoor expansion valve and a one-way valve through pipelines, and the outdoor expansion valve and the one-way valve are both connected with the refrigerant gas-liquid separation unit through pipelines. The liquid refrigerant passing through the refrigerant gas-liquid separation unit is blocked by the one-way valve and enters the outdoor expansion valve for throttling and pressure reduction, the refrigerant is in a low-temperature and low-pressure state after throttling and pressure reduction, and the low-temperature and low-pressure refrigerant enters the outdoor heat exchanger under the non-defrosting condition for absorbing heat. And the refrigerant compressed by the compression unit enters the outdoor heat exchanger under the defrosting condition and then enters the indoor expansion valve through the one-way valve to be decompressed.
As a preferred scheme of the utility model, the refrigerant gas-liquid separation unit comprises an indoor expansion valve and a flash steam separator which are connected through a pipeline, the other end of the indoor expansion valve is connected with the indoor heat exchanger through a pipeline, a gas phase interface of the flash steam separator is connected with the compression unit through a pipeline, a liquid phase interface of the flash steam separator is respectively connected with a plurality of outdoor expansion valves through pipelines, and a plurality of one-way valves are connected to the pipeline between the indoor heat exchanger and the indoor expansion valve through pipelines. The refrigerant after being decompressed by the indoor expansion valve enters the flash vapor separator, and the gaseous refrigerant in the flash vapor separator enters the middle end of the compression unit after being separated. The liquid refrigerant check valve in the flash vapor separator enters an outdoor expansion valve for throttling and pressure reduction, the refrigerant is in a low-temperature and low-pressure state after throttling and pressure reduction, and the low-temperature and low-pressure refrigerant enters the outdoor heat exchanger under the non-defrosting working condition.
As a preferred embodiment of the present invention, the refrigerant gas-liquid separation unit includes an intercooler, one end of the intercooler is connected to the indoor heat exchanger through a pipeline, a liquid phase port of the intercooler is connected to the outdoor expansion valve through a pipeline, the liquid phase port of the intercooler is further connected to a normally open solenoid valve through a pipeline, an outer side of the intercooler is connected to the indoor expansion valve through a pipeline, the other end of the indoor expansion valve is connected to the check valve through a pipeline, the other end of the normally open solenoid valve is connected to one end of the indoor expansion valve connected to the check valve through a pipeline, and a gas phase port of the intercooler is connected to the compression unit through a pipeline.
The refrigerant is released heat and condensed in the indoor heat exchanger, enters the intercooler and then is divided into two paths. One path of the refrigerant passes through a normally open electromagnetic valve, is subjected to pressure reduction by an indoor expansion valve, enters the outer side of a coil pipe of the intercooler for heat absorption, and enters the middle end of the compression unit after heat absorption. The refrigerant inside the other coil pipe is cooled in the intermediate cooler and blocked by the one-way valve, and then enters the outdoor expansion valve to be throttled and decompressed, the refrigerant is in a low-temperature and low-pressure state after being throttled and decompressed, and the low-temperature and low-pressure refrigerant enters the outdoor heat exchanger under the non-defrosting condition to absorb heat.
The utility model has the beneficial effects that:
the utility model connects multiple groups of outdoor heat exchanger units in parallel, thereby defrosting one or more outdoor heat exchangers in the normal heat supply state. When defrosting is carried out on one outdoor heat exchanger, the electromagnetic valve is remotely switched, so that the outdoor heat exchanger and the indoor heat exchanger can be used as condensers, and the other outdoor heat exchangers can be used as evaporators. At the moment, when the outdoor heat exchanger is defrosted, normal indoor heat supply is not affected. The electromagnetic valves are arranged on the two branches for controlling the flow direction of the refrigerant in the outdoor heat exchanger unit, so that the reliable switching of the passages is ensured, and the condition that the switching is not in place is avoided.
Drawings
FIG. 1 is a schematic view showing the construction of the present invention in normal heating in winter in example 1;
FIG. 2 is a schematic view showing the construction of the present invention in case of defrosting heat supply in winter in embodiment 1;
FIG. 3 is a schematic view showing the construction of the present invention in normal heating in winter in example 2;
FIG. 4 is a schematic view showing the construction of the present invention in case of defrosting heat supply in winter in embodiment 2;
FIG. 5 is a schematic view showing the construction of the present invention in normal heating in the winter season in embodiment 3;
FIG. 6 is a schematic view showing the construction of the present invention in case of defrosting heat supply in winter in embodiment 3;
FIG. 7 is a schematic view showing the construction of the present invention in normal heating in winter in embodiment 4;
FIG. 8 is a schematic view showing the construction of the present invention in case of defrosting heating in winter in embodiment 4;
FIG. 9 is a schematic view showing the construction of the present invention in normal heating in the winter season in embodiment 5;
FIG. 10 is a schematic view showing the construction of the present invention in case of defrosting heating in winter in embodiment 5;
FIG. 11 is a graph of energy consumption for a conventional defrost technique with a heating power of 150 kW;
fig. 12 is a graph of energy consumption for the defrosting technique of the present invention with a heating power of 150 kW.
In the figure, 1-compression unit; 2-an indoor heat exchanger unit; 3-a refrigerant gas-liquid separation unit; 4-an outdoor heat exchanger unit; 5-an electromagnetic valve; 11-a two-stage compressor; 12-a low pressure stage compressor; 13-a high pressure stage compressor; 14-a four-way valve; 15-a compressor; 21-indoor heat exchanger; 22-indoor expansion valve; 23-an indoor one-way valve; 32-flash vapor separator; 33-an intercooler; 34-normally open electromagnetic valve; 41-outdoor heat exchanger; 42-outdoor expansion valve; 43-a one-way valve; 141-compressor interface; 142-a third interface of the four-way valve; 143-fourth interface of four-way valve.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the utility model and are not to be construed as limiting the utility model.
Example 1:
as shown in fig. 1 and 2, the air source heat pump unit for avoiding cold and heat offset during defrosting of the present embodiment includes a compression unit 1, the compression unit 1 is connected to an indoor heat exchanger unit 2 through a pipeline, a plurality of outdoor heat exchanger units 4 are connected in parallel between the other end of the indoor heat exchanger unit 2 and the compression unit 1, a solenoid valve 5 is connected to a pipeline of the outdoor heat exchanger unit 4, and a solenoid valve 5 is connected between a pipeline between the compression unit 1 and the indoor heat exchanger unit 2 and a pipeline of the outdoor heat exchanger unit 4.
The present invention connects multiple sets of outdoor heat exchanger units 4 in parallel so that one or more of the outdoor heat exchangers 41 can be defrosted in a normal heat supply state. When defrosting a certain outdoor heat exchanger 41, the electromagnetic valve 5 is remotely switched so that the outdoor heat exchanger 41 and the indoor heat exchanger 21 function as condensers and the remaining outdoor heat exchangers 41 function as evaporators. In this case, the normal indoor heating is not affected when defrosting the outdoor heat exchanger 41. The electromagnetic valves 5 are arranged on two branches for controlling the flow direction of the refrigerant in the outdoor heat exchanger unit 4, so that the reliable switching of the passages is ensured, and the situation of incomplete switching is avoided.
The indoor heat exchanger unit 2 comprises an indoor heat exchanger 21, one end of the indoor heat exchanger is connected with the compression unit 1 through a pipeline, and the other end of the indoor heat exchanger 21 is connected with an indoor expansion valve 22 and an indoor one-way valve 23 which are connected in parallel through pipelines. In winter, after the refrigerant releases heat and condenses in the indoor heat exchanger 21, the refrigerant flows through the indoor check valve 22 and enters the outdoor heat exchanger unit 4 to absorb heat. In summer, the temperature of the refrigerant is reduced after heat release and condensation are finished, the refrigerant is blocked by the indoor check valve 23, enters the indoor expansion valve 22 for throttling and pressure reduction, the temperature is reduced while the pressure is reduced, low-temperature and low-pressure refrigerant is obtained, and the low-temperature and low-pressure refrigerant enters the indoor heat exchanger 21 for absorbing heat.
The compression unit 1 comprises a four-way valve 14, a compressor 15 is connected between two compressor interfaces 141 of the four-way valve 14 through a pipeline, a third interface 142 of the four-way valve is connected with the indoor heat exchanger unit 2 through a pipeline, and the outdoor heat exchanger units 4 are connected between the other end of the indoor heat exchanger unit 2 and a fourth interface 143 of the four-way valve in parallel.
As shown in fig. 1, during normal heating operation in winter, the four-way valve 14 is controlled and the solenoid valve 5 is switched. The compressor 15 sucks in low-pressure low-temperature refrigerant vapor generated in the plurality of outdoor heat exchangers 41; after adiabatic compression, the refrigerant becomes a high-temperature and high-pressure gas, and enters the indoor heat exchanger 21. The refrigerant cools and releases heat in the indoor heat exchanger 21, and at this time, the indoor heat exchanger 21 is a condenser and releases heat indoors. After the heat is released and condensed in the indoor heat exchanger 21, the refrigerant flows through the indoor check valve 23, is blocked by the check valves 43, and enters the outdoor expansion valves 42 respectively for throttling and pressure reduction. The refrigerant after throttling and pressure reduction is in a low-temperature and low-pressure state, and the low-temperature and low-pressure refrigerant enters a plurality of outdoor heat exchangers 41 to absorb heat. In this case, the outdoor heat exchanger 41 is an evaporator, and the refrigerant absorbs heat and then enters the compressor 15 again, thereby continuously circulating. When the heat exchange modules are added for increasing the heat exchange quantity, the working principle is similar.
As shown in fig. 2, taking the defrosting condition of one of the outdoor heat exchangers 41 as an example, the multiple-evaporator alternative defrosting air source heat pump unit controls the four-way valve 5 to switch one set of the electromagnetic valves 5 when the heat supply condition is normal in winter. The compressor 15 sucks in the low-pressure and low-temperature refrigerant vapor generated in the outdoor heat exchanger 41 in the non-defrosting mode. After adiabatic compression, the refrigerant is changed into high-temperature and high-pressure gas, and the high-temperature and high-pressure gas respectively enters the indoor heat exchanger 21 and the outdoor heat exchanger 41 under the defrosting condition. The refrigerant cools and releases heat in the indoor heat exchanger 21 and the outdoor heat exchanger 41 under the defrosting condition, and at this time, the indoor heat exchanger 21 and the outdoor heat exchanger 41 under the defrosting condition are condensers, and releases heat indoors. The refrigerant is condensed by heat release in the indoor heat exchanger 21 and the outdoor heat exchanger 41 in the defrosting mode, and then flows through the indoor check valve 23 and the check valve 43 in the defrosting mode, respectively. And the air is blocked by the one-way valve 43 under the non-defrosting working condition and respectively enters the outdoor expansion valve 42 under the non-defrosting working condition for throttling and pressure reduction. The refrigerant is in a low-temperature and low-pressure state after throttling and pressure reduction, and the low-temperature and low-pressure refrigerant enters the outdoor heat exchanger 41 under the non-defrosting condition to absorb heat. The outdoor heat exchanger 41 in the non-defrosting condition is an evaporator. The refrigerant absorbs heat and then enters the compressor 15 again, and the circulation is continued. The working principle is similar when heat exchange modules are added in order to increase the amount of heat exchange.
Example 2:
as shown in fig. 3 and 4, the quasi-two-stage compression multi-evaporator alternating defrosting air source heat pump unit with the flash vapor separator. The compression unit 1 comprises a two-stage compressor 11, the two-stage compressor 11 comprises a low-pressure stage compression cylinder, a middle cavity and a high-pressure stage compression cylinder, the outdoor heat exchanger unit 4 is connected with the low-pressure stage compression cylinder through a pipeline, a gas phase interface of the refrigerant gas-liquid separation unit is connected with the middle cavity through a pipeline, and the indoor heat exchanger 21 is connected with the high-pressure stage compression cylinder through a pipeline.
The refrigerant gas-liquid separation unit 3 comprises an indoor expansion valve 22 and a flash steam separator 32 which are connected through pipelines, the other end of the indoor expansion valve 22 is connected with the indoor heat exchanger 21 through a pipeline, a gas phase interface of the flash steam separator 32 is connected with the compression unit 1 through a pipeline, a liquid phase interface of the flash steam separator 32 is respectively connected with a plurality of outdoor expansion valves 42 through pipelines, and a plurality of one-way valves 43 are connected on the pipeline between the indoor heat exchanger 21 and the indoor expansion valve 22 through pipelines.
Normal heat supply working condition in winter:
as shown in fig. 3, the solenoid valve 5 is switched during winter heating. The low-pressure stage compression cylinder sucks all low-pressure low-temperature refrigerant vapor generated in the outdoor heat exchanger 41, mixes with the refrigerant separated from the flash vapor separator, and enters the high-pressure stage compression cylinder for compression. The refrigerant turns into a high-temperature and high-pressure gas, and enters the indoor heat exchanger 21. The refrigerant cools and releases heat in the indoor heat exchanger 21, and at this time, the indoor heat exchanger 21 is a condenser and releases heat indoors. After the heat of the refrigerant is released and condensed in the indoor heat exchanger 21, the refrigerant is decompressed through the indoor expansion valve 22, the decompressed preparation enters the flash vapor separator, and the gaseous refrigerant in the flash vapor separator enters the middle cavity of the two-stage compressor 11 after being separated. The liquid refrigerant in the flash vapor separator is blocked by all the one-way valves 43 and enters each outdoor expansion valve 42 respectively for throttling and pressure reduction. The refrigerant after throttling and pressure reduction is in a low-temperature and low-pressure state, the low-temperature and low-pressure refrigerant enters each outdoor heat exchanger 41 to absorb heat, and all the outdoor heat exchangers 41 are evaporators at the moment. The refrigerant absorbs heat and then enters the low-pressure stage cylinder of the two-stage compressor 11 again, and is mixed with the separated gaseous refrigerant and then is further compressed, and the cycle is continued. When the heat exchange modules are added for increasing the heat exchange quantity, the working principle is similar.
Defrosting and heat supplying working conditions in winter:
as shown in fig. 4, the first outdoor heat exchanger 41 from the left is the outdoor heat exchanger 41 in the defrosting mode, and the remaining outdoor heat exchangers 41 are the outdoor heat exchangers 41 in the non-defrosting mode. When heat is supplied in winter and the outdoor heat exchanger 41 is defrosted under the defrosting condition, the electromagnetic valve 5 is switched. The low-pressure stage compression cylinder sucks low-pressure low-temperature refrigerant steam generated in the outdoor heat exchanger 41 under the non-defrosting condition, mixes with the refrigerant separated from the flash vapor separator, and enters the high-pressure stage compression cylinder for compression. The refrigerant is changed into high-temperature and high-pressure gas, and the high-temperature and high-pressure gas respectively enters the indoor heat exchanger 21 and the defrosting condition heat exchanger. The refrigerant is cooled and released in the indoor heat exchanger 21 and the defrosting condition outdoor heat exchanger 41, and at this time, the indoor heat exchanger 21 and the defrosting condition outdoor heat exchanger 41 are condensers. The refrigerant in the indoor heat exchanger 21 is mixed with the refrigerant from the outdoor heat exchanger 41 under the defrosting condition after heat release and condensation, the pressure is reduced through the indoor expansion valve 22, and the preparation after pressure reduction enters the flash vapor separator. The gaseous refrigerant in the flash vapor separator enters the middle cavity of the two-stage compressor 11 after being separated. The liquid refrigerant in the flash vapor separator is blocked by the one-way valve 43 and respectively enters the outdoor expansion valve 42 under the non-defrosting working condition for throttling and pressure reduction, and the refrigerant is in a low-temperature and low-pressure state after throttling and pressure reduction. The low-temperature and low-pressure refrigerant enters the outdoor heat exchanger 41 in the non-defrosting condition to absorb heat. At this time, the outdoor heat exchanger 41 under the non-defrosting condition is an evaporator, and the refrigerant absorbs heat and then enters the low-pressure stage cylinder of the two-stage compressor 11 again, and is further compressed after being mixed with the separated gaseous refrigerant, and the cycle is continued. Other modules work in a similar manner in defrosting operation.
Example 3:
as shown in figures 5 and 6, the double-stage compression multi-evaporator alternating defrosting air source heat pump unit with the flash vapor separator. The compression unit 1 comprises a low-pressure stage compressor 12 and a high-pressure stage compressor 13 which are connected through pipelines, the outdoor heat exchanger unit 4 is connected with the low-pressure stage compressor 12 through a pipeline, a gas phase interface of the refrigerant gas-liquid separation unit is connected with a suction inlet of the high-pressure stage compressor 13 through a pipeline, and the indoor heat exchanger 21 is connected with a discharge outlet of the high-pressure stage compressor 13 through a pipeline.
The refrigerant gas-liquid separation unit 3 comprises an indoor expansion valve 22 and a flash steam separator 32 which are connected through pipelines, the other end of the indoor expansion valve 22 is connected with the indoor heat exchanger 21 through a pipeline, a gas phase interface of the flash steam separator 32 is connected with the compression unit 1 through a pipeline, a liquid phase interface of the flash steam separator 32 is respectively connected with a plurality of outdoor expansion valves 42 through pipelines, and a plurality of one-way valves 43 are connected on the pipeline between the indoor heat exchanger 21 and the indoor expansion valve 22 through pipelines.
Normal heat supply working condition in winter:
as shown in fig. 5, the solenoid valve 5 is switched during heating in winter. The low-pressure stage compressor 12 sucks in all the low-pressure low-temperature refrigerant vapor generated in the outdoor heat exchanger 41, mixes the low-pressure low-temperature refrigerant vapor with the refrigerant separated from the flash vapor separator, and then enters the high-pressure stage compressor 13 to be compressed. The refrigerant turns into a high-temperature and high-pressure gas, and enters the indoor heat exchanger 21. The refrigerant is cooled and releases heat in the indoor heat exchanger 21, and at this time, the indoor heat exchanger 21 functions as a condenser and releases heat indoors. After the heat of the refrigerant is released and condensed in the indoor heat exchanger 21, the refrigerant is decompressed through the indoor expansion valve 22, and the decompressed preparation enters the flash vapor separator. The gaseous refrigerant in the flash vapor separator is separated and then enters the suction inlet of the high pressure stage compressor 13. The liquid refrigerant in the flash vapor separator is blocked by the check valves 43 and enters the outdoor expansion valves 42 respectively for throttling and pressure reduction. The refrigerant after throttling and pressure reduction is in a low-temperature and low-pressure state, and the low-temperature and low-pressure refrigerant enters each outdoor heat exchanger 41 to absorb heat, and at this time, each outdoor heat exchanger 41 is an evaporator. The refrigerant absorbs heat and then enters the low-pressure stage compressor 12 again, and is mixed with the separated gaseous refrigerant and then is further compressed, and the cycle is continued. The working principle is similar when heat exchange modules are added in order to increase the amount of heat exchange.
Defrosting and heat supplying working conditions in winter:
as shown in fig. 6, the first outdoor heat exchanger 41 from the left is the outdoor heat exchanger 41 in the defrosting mode, and the remaining outdoor heat exchangers 41 are the outdoor heat exchangers 41 in the non-defrosting mode. When heat is supplied in winter and the outdoor heat exchanger 41 is defrosted under the defrosting condition, the electromagnetic valve 5 is switched. The low-pressure stage compressor 12 sucks in low-pressure low-temperature refrigerant vapor generated in the outdoor heat exchanger 41 under the non-defrosting condition, mixes the low-pressure low-temperature refrigerant vapor with the refrigerant separated from the flash vapor separator, and then enters the high-pressure stage compressor 13 to be compressed. The refrigerant is changed into high-temperature and high-pressure gas, and the high-temperature and high-pressure gas respectively enters the indoor heat exchanger 21 and the outdoor heat exchanger 41 under the defrosting condition; the refrigerant is cooled and released in the indoor heat exchanger 21 and the outdoor heat exchanger 41 under the defrosting condition, and at this time, the indoor heat exchanger 21 and the outdoor heat exchanger 41 under the defrosting condition are condensers. The refrigerant in the indoor heat exchanger 21 is mixed with the refrigerant from the module after defrosting after heat release and condensation, the pressure is reduced through the indoor expansion valve 22, and the preparation after pressure reduction enters the flash vapor separator. The gaseous refrigerant in the flash vapor separator is separated and then enters the suction inlet of the high pressure stage compressor 13. The liquid refrigerant in the flash vapor separator is blocked by the one-way valve 43 under the non-defrosting condition, and respectively enters the outdoor expansion valve 42 under the non-defrosting condition for throttling and pressure reduction, the refrigerant is in a low-temperature and low-pressure state after throttling and pressure reduction, the low-temperature and low-pressure refrigerant enters the outdoor heat exchanger 41 under the non-defrosting condition for absorbing heat, the outdoor heat exchanger 41 under the non-defrosting condition is an evaporator, the refrigerant enters the low-pressure stage compressor 12 again after absorbing heat, is mixed with the separated gaseous refrigerant and then is further compressed, and the circulation is continued. Other modules work in a similar manner in defrosting operation.
Example 4:
as shown in fig. 7 and 8, the quasi-two-stage compression multi-evaporator alternative defrosting air source heat pump unit with the intercooler 33. The compression unit 1 comprises a two-stage compressor 11, the two-stage compressor 11 comprises a low-pressure stage compression cylinder, a middle cavity and a high-pressure stage compression cylinder, the outdoor heat exchanger unit 4 is connected with the low-pressure stage compression cylinder through a pipeline, a gas phase interface of the refrigerant gas-liquid separation unit is connected with the middle cavity through a pipeline, and the indoor heat exchanger 21 is connected with the high-pressure stage compression cylinder through a pipeline.
The refrigerant gas-liquid separation unit 3 comprises an intercooler 33, one end of the intercooler 33 is connected with the indoor heat exchanger 21 through a pipeline, a liquid phase interface of the intercooler 33 is connected with the outdoor expansion valve 42 through a pipeline, the liquid phase interface of the intercooler 33 is further connected with a normally open electromagnetic valve 34 through a pipeline, the outer side of the intercooler 33 is connected with the indoor expansion valve 22 through a pipeline, the other end of the indoor expansion valve 22 is connected with a one-way valve 43 through a pipeline, the other end of the normally open electromagnetic valve 34 is connected with one end of the indoor expansion valve 22, which is connected with the one-way valve 43, and a gas phase interface of the intercooler 33 is connected with the compression unit 1 through a pipeline.
Normal heat supply working condition in winter:
as shown in fig. 7, the solenoid valve 5 is switched during heating in winter. The low-pressure stage cylinder of the two-stage compressor 11 sucks in low-pressure and low-temperature refrigerant vapor generated in each outdoor heat exchanger 41, mixes the refrigerant with the refrigerant from the intercooler 33 after adiabatic compression, and then enters the high-pressure stage cylinder of the two-stage compressor 11 to be compressed, so that the refrigerant is changed into high-temperature and high-pressure gas and enters the indoor heat exchanger 21. The refrigerant cools and releases heat in the indoor heat exchanger 21, and at this time, the indoor heat exchanger 21 is a condenser and releases heat indoors. The refrigerant is condensed by heat release in the indoor heat exchanger 21, and then enters the intercooler 33 and is divided into two paths. One path of the refrigerant passes through the normally open electromagnetic valve 34, is depressurized by the indoor expansion valve 22, enters the outer side of the coil of the intercooler 33 to absorb heat, and the gas-liquid mixed refrigerant after absorbing heat enters the middle cavity of the two-stage compressor 11. The refrigerant in the other coil is cooled in the intercooler 33, and then enters the outdoor expansion valves 42 for throttling and pressure reduction under the action of the check valves 43. The refrigerant after throttling and pressure reduction is in a low-temperature and low-pressure state, and the low-temperature and low-pressure refrigerant enters each outdoor heat exchanger 41 to absorb heat. At this time, each outdoor heat exchanger 41 is an evaporator, and the refrigerant absorbs heat and then enters the low-pressure stage suction port of the two-stage compressor 11 again to be mixed with the intermediate chamber refrigerant and then further compressed, thereby continuously circulating. The operating principle is similar when heat exchange modules are added in order to increase the amount of heat exchange.
Defrosting and heat supplying working conditions in winter:
as shown in fig. 8, the first outdoor heat exchanger 41 from the left is the outdoor heat exchanger 41 in the defrosting mode, and the remaining outdoor heat exchangers 41 are the outdoor heat exchangers 41 in the non-defrosting mode. When heat is supplied in winter and the outdoor heat exchanger 41 is defrosted under the defrosting condition, the electromagnetic valve 5 is switched. The low-pressure stage cylinder of the two-stage compressor 11 sucks in low-pressure low-temperature refrigerant vapor generated in the outdoor heat exchanger 41 under the non-defrosting condition, mixes the refrigerant vapor with the refrigerant from the intercooler 33 after adiabatic compression, and then enters the high-pressure stage cylinder of the two-stage compressor 11 for compression. The refrigerant is changed into high-temperature and high-pressure gas, and the high-temperature and high-pressure gas respectively enters the indoor heat exchanger 21 and the outdoor heat exchanger 41 under the defrosting condition. The refrigerant is cooled and released in the indoor heat exchanger 21 and the outdoor heat exchanger 41 under the defrosting condition, and at this time, the indoor heat exchanger 21 and the outdoor heat exchanger 41 under the defrosting condition are condensers. After the heat of the refrigerant in the outdoor heat exchanger 41 in the defrosting condition is released, the refrigerant is decompressed by the indoor expansion valve 22, and then enters the outer side of the coil of the intercooler 33 to absorb heat, and the gas-liquid mixed refrigerant after absorbing heat enters the middle cavity of the two-stage compressor 11. The refrigerant in the indoor heat exchanger 21 is cooled in the intercooler 33 and then blocked by the non-defrost working condition check valve 43, and then enters the outdoor expansion valve 42 of the non-defrost working condition for throttling and pressure reduction. The refrigerant is in a low-temperature and low-pressure state after throttling and pressure reduction, the low-temperature and low-pressure refrigerant enters the outdoor heat exchanger 41 under the non-defrosting condition to absorb heat, and the outdoor heat exchanger 41 under the non-defrosting condition is an evaporator. The refrigerant absorbs heat and then enters the low-pressure stage of the two-stage compressor 11 again to be mixed with the refrigerant in the middle cavity for further compression, and the circulation is continued. Other modules work in a similar manner in defrosting operation.
Example 5:
as shown in fig. 9 and 10, the two-stage compression multi-evaporator alternative defrosting air source heat pump unit with the intercooler 33. The compression unit 1 comprises a low-pressure stage compressor 12 and a high-pressure stage compressor 13 which are connected through pipelines, the outdoor heat exchanger unit 4 is connected with the low-pressure stage compressor 12 through a pipeline, a gas phase interface of the refrigerant gas-liquid separation unit is connected with a suction inlet of the high-pressure stage compressor 13 through a pipeline, and the indoor heat exchanger 21 is connected with a discharge outlet of the high-pressure stage compressor 13 through a pipeline.
The refrigerant gas-liquid separation unit 3 comprises an intercooler 33, one end of the intercooler 33 is connected with the indoor heat exchanger 21 through a pipeline, a liquid phase interface of the intercooler 33 is connected with the outdoor expansion valve 42 through a pipeline, the liquid phase interface of the intercooler 33 is further connected with a normally open electromagnetic valve 34 through a pipeline, the outer side of the intercooler 33 is connected with the indoor expansion valve 22 through a pipeline, the other end of the indoor expansion valve 22 is connected with a one-way valve 43 through a pipeline, the other end of the normally open electromagnetic valve 34 is connected with one end of the indoor expansion valve 22, which is connected with the one-way valve 43, and a gas phase interface of the intercooler 33 is connected with the compression unit 1 through a pipeline.
Normal heat supply working condition in winter:
as shown in fig. 9, during normal heating in winter, the normally open solenoid valve 34 is opened, and the solenoid valve 5 is switched. The low-pressure stage compressor 12 sucks in low-pressure and low-temperature refrigerant vapor generated in each outdoor heat exchanger 41, adiabatically compresses the refrigerant vapor, mixes the refrigerant vapor with the refrigerant from the intercooler 33, and then, enters the high-pressure stage compressor 13 to compress the refrigerant, thereby turning the refrigerant into high-temperature and high-pressure gas, and then, enters the indoor heat exchanger 21. The refrigerant cools and releases heat in the indoor heat exchanger 21, and at this time, the indoor heat exchanger 21 is a condenser and releases heat indoors. The refrigerant is condensed by heat release in the indoor heat exchanger 21, and then enters the intercooler 33 and is divided into two paths. One of the paths passes through a normally open electromagnetic valve 34, is depressurized by an indoor expansion valve 22, enters the outer side of a coil of an intercooler 33 to absorb heat, and a gas-liquid mixed refrigerant after heat absorption enters a suction inlet of the high-pressure stage compressor 13. After being cooled by the intercooler 33, the refrigerant inside the other coil enters each outdoor expansion valve 42 for throttling and pressure reduction under the action of each one-way valve 43, and the refrigerant is in a low-temperature and low-pressure state after throttling and pressure reduction. The low-temperature and low-pressure refrigerant enters each outdoor heat exchanger 41 to absorb heat, at the moment, each outdoor heat exchanger 41 is an evaporator, the refrigerant absorbs heat and then enters the suction port of the low-pressure stage compressor 12 again to be mixed with the refrigerant outside the coil pipe of the intercooler 33, and then is further compressed, and the circulation is continued. The working principle is similar when heat exchange modules are added in order to increase the amount of heat exchange.
Defrosting and heating working conditions in winter:
as shown in fig. 10, the first outdoor heat exchanger 41 from the left is the outdoor heat exchanger 41 in the defrosting mode, and the remaining outdoor heat exchangers 41 are the outdoor heat exchangers 41 in the non-defrosting mode. When heat is supplied in winter and the outdoor heat exchanger 41 is defrosted under the defrosting condition, the electromagnetic valve 5 is switched. The low-pressure stage compressor 12 sucks in low-pressure and low-temperature refrigerant vapor generated in the outdoor heat exchanger 41 under the non-defrosting condition, mixes the refrigerant with the refrigerant from the intercooler 33 after adiabatic compression, and then enters the high-pressure stage compressor 13 for compression, so that the refrigerant is changed into high-temperature and high-pressure gas and enters the indoor heat exchanger 21 and the outdoor heat exchanger 41 under the defrosting condition respectively. The refrigerant is cooled and released in the indoor heat exchanger 21 and the outdoor heat exchanger 41 under the defrosting condition, and at this time, the indoor heat exchanger 21 and the outdoor heat exchanger 41 under the defrosting condition are condensers. After the heat of the refrigerant in the outdoor heat exchanger 41 in the defrosting condition is released, the refrigerant is decompressed by the indoor expansion valve 22, and then enters the outer side of the coil of the intercooler 33 to absorb heat, and the gas-liquid mixed refrigerant after absorbing heat enters the suction port of the high-pressure stage compressor 13. The refrigerant in the indoor heat exchanger 21 enters the inner side of the coil of the intercooler 33 after heat release and condensation, and the refrigerant inside the coil is cooled in the intercooler 33 and then blocked by the one-way valve 43 under the non-defrosting condition, and respectively enters the expansion valve under the non-defrosting condition for throttling and pressure reduction. The refrigerant is in a low-temperature and low-pressure state after throttling and pressure reduction, the low-temperature and low-pressure refrigerant enters the outdoor heat exchanger 41 under the non-defrosting condition to absorb heat, and the outdoor heat exchanger 41 under the non-defrosting condition is an evaporator. The refrigerant which absorbs heat and enters the low-pressure stage compressor 12 again is mixed with the refrigerant in the intermediate chamber and then is further compressed, and the circulation is continued. Other modules work in a similar manner in defrosting operation.
The present invention is not limited to the above-mentioned alternative embodiments, and any other various products can be obtained by anyone in the light of the present invention, but any changes in the shape or structure thereof, all of which fall within the scope of the present invention, fall within the protection scope of the present invention.
Claims (8)
1. An air source heat pump unit for avoiding cold and heat offset during defrosting is characterized by comprising a compression unit (1), wherein the compression unit (1) is connected with an indoor heat exchanger unit (2) through a pipeline, a plurality of outdoor heat exchanger units (4) are connected between the other end of the indoor heat exchanger unit (2) and the compression unit (1) in parallel, the pipeline of each outdoor heat exchanger unit (4) is connected with an electromagnetic valve (5), and the electromagnetic valve (5) is connected between the pipeline between the compression unit (1) and the indoor heat exchanger unit (2) and the pipeline of each outdoor heat exchanger unit (4); the compression unit (1) comprises a four-way valve (14), a compressor (15) is connected between two compressor interfaces (141) of the four-way valve (14) through a pipeline, a third interface (142) of the four-way valve is connected with the indoor heat exchanger unit (2) through a pipeline, and a plurality of outdoor heat exchanger units (4) are connected between the other end of the indoor heat exchanger unit (2) and a fourth interface (143) of the four-way valve in parallel.
2. The air source heat pump unit for avoiding cold and heat offset during defrosting according to claim 1, wherein the indoor heat exchanger unit (2) comprises an indoor heat exchanger (21), one end of the indoor heat exchanger (21) is connected with the compression unit (1) through a pipeline, and the other end of the indoor heat exchanger (21) is connected with an indoor expansion valve (22) and an indoor one-way valve (23) which are connected in parallel through pipelines.
3. The air source heat pump unit for avoiding cold and heat offset during defrosting according to claim 1, wherein the high pressure end of the compression unit (1) is connected with the indoor heat exchanger unit (2) through a pipeline, the other end of the indoor heat exchanger unit (2) is connected with the refrigerant gas-liquid separation unit (3) through a pipeline, the gas phase interface of the refrigerant gas-liquid separation unit (3) is connected with the middle end of the compression unit (1) through a pipeline, and the outdoor heat exchanger units (4) are connected in parallel between the liquid phase interface of the refrigerant gas-liquid separation unit (3) and the low pressure end of the compression unit (1).
4. The air source heat pump unit for avoiding cold and heat offset during defrosting according to claim 3, wherein the compression unit (1) comprises a two-stage compressor (11), the two-stage compressor (11) comprises a low-pressure stage compression cylinder, an intermediate cavity and a high-pressure stage compression cylinder, the outdoor heat exchanger unit (4) is connected with the low-pressure stage compression cylinder through a pipeline, a gas phase interface of the refrigerant gas-liquid separation unit is connected with the intermediate cavity through a pipeline, and the indoor heat exchanger unit (2) is connected with the high-pressure stage compression cylinder through a pipeline.
5. The air source heat pump unit for avoiding cold and heat offset during defrosting according to claim 3, wherein the compression unit (1) comprises a low-pressure stage compressor (12) and a high-pressure stage compressor (13) which are connected through a pipeline, the outdoor heat exchanger unit (4) is connected with the low-pressure stage compressor (12) through a pipeline, the gas phase interface of the refrigerant gas-liquid separation unit is connected with the suction inlet of the high-pressure stage compressor (13) through a pipeline, and the indoor heat exchanger unit is connected with the discharge outlet of the high-pressure stage compressor (13) through a pipeline.
6. The air source heat pump unit for avoiding cold and heat offset during defrosting according to claim 3, wherein the outdoor heat exchanger unit (4) comprises an outdoor heat exchanger (41), one end of the outdoor heat exchanger (41) far away from the electromagnetic valve (5) is respectively connected with an outdoor expansion valve (42) and a one-way valve (43) through pipelines, and the outdoor expansion valve (42) and the one-way valve (43) are both connected with the refrigerant gas-liquid separation unit (3) through pipelines.
7. The air source heat pump unit for avoiding cold and heat offset during defrosting according to claim 6, wherein the refrigerant gas-liquid separation unit (3) comprises an indoor expansion valve (22) and a flash steam separator (32) which are connected through a pipeline, the other end of the indoor expansion valve (22) is connected with the indoor heat exchanger unit (2) through a pipeline, a gas phase interface of the flash steam separator (32) is connected with the two-stage compression unit (1) through a pipeline, a liquid phase interface of the flash steam separator (32) is respectively connected with a plurality of outdoor expansion valves (42) through pipelines, and a plurality of one-way valves (43) are connected on the pipeline between the indoor heat exchanger unit (2) and the indoor expansion valve (22) through pipelines.
8. The air source heat pump unit for avoiding the cold-heat offset during the defrosting according to claim 6, the refrigerant gas-liquid separation unit (3) comprises an intercooler (33), one end of the intercooler (33) is connected with the indoor heat exchanger unit (2) through a pipeline, a liquid phase interface of the intercooler (33) is connected with the outdoor expansion valve (42) through a pipeline, the liquid phase interface of the intercooler (33) is further connected with a normally open electromagnetic valve (34) through a pipeline, the outer side of the intercooler (33) is connected with the indoor expansion valve (22) through a pipeline, the other end of the indoor expansion valve (22) is connected with the one-way valve (43) through a pipeline, the other end of the normally open electromagnetic valve (34) is connected with one end of the one-way valve (43) connected with the indoor expansion valve (22) through a pipeline, and a gas phase interface of the intercooler (33) is connected with the two-stage compression unit (1) through a pipeline.
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| CN202122298880.3U CN216744986U (en) | 2021-09-22 | 2021-09-22 | Air source heat pump unit for avoiding cold and heat offset during defrosting |
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| CN202122298880.3U CN216744986U (en) | 2021-09-22 | 2021-09-22 | Air source heat pump unit for avoiding cold and heat offset during defrosting |
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