CN113758048B - Air source heat pump low temperature protection system - Google Patents
Air source heat pump low temperature protection system Download PDFInfo
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- CN113758048B CN113758048B CN202110923719.2A CN202110923719A CN113758048B CN 113758048 B CN113758048 B CN 113758048B CN 202110923719 A CN202110923719 A CN 202110923719A CN 113758048 B CN113758048 B CN 113758048B
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- 239000003507 refrigerant Substances 0.000 claims abstract description 91
- 238000000034 method Methods 0.000 claims abstract description 19
- 238000004781 supercooling Methods 0.000 claims abstract description 9
- 238000005485 electric heating Methods 0.000 claims description 46
- 239000007788 liquid Substances 0.000 claims description 29
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 claims description 27
- 229910052802 copper Inorganic materials 0.000 claims description 27
- 239000010949 copper Substances 0.000 claims description 27
- 238000010438 heat treatment Methods 0.000 claims description 21
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 21
- 230000008569 process Effects 0.000 claims description 12
- 238000005057 refrigeration Methods 0.000 claims description 12
- 230000002265 prevention Effects 0.000 claims description 11
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 claims description 8
- 230000006835 compression Effects 0.000 claims description 7
- 238000007906 compression Methods 0.000 claims description 7
- 238000001704 evaporation Methods 0.000 claims description 5
- 239000002784 hot electron Substances 0.000 claims description 5
- 230000007246 mechanism Effects 0.000 claims description 5
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 claims description 4
- 229910052782 aluminium Inorganic materials 0.000 claims description 4
- 229910052742 iron Inorganic materials 0.000 claims description 4
- 238000013021 overheating Methods 0.000 claims description 4
- 229920006395 saturated elastomer Polymers 0.000 claims description 3
- 230000006641 stabilisation Effects 0.000 claims description 3
- 238000011105 stabilization Methods 0.000 claims description 3
- 239000000463 material Substances 0.000 claims description 2
- 230000006872 improvement Effects 0.000 abstract description 5
- 230000008447 perception Effects 0.000 abstract description 2
- 230000008859 change Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 230000005540 biological transmission Effects 0.000 description 4
- 238000009434 installation Methods 0.000 description 4
- 230000009467 reduction Effects 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 239000004020 conductor Substances 0.000 description 3
- 238000010257 thawing Methods 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 230000007613 environmental effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/06—Heat pumps characterised by the source of low potential heat
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention discloses an air energy heat pump low-temperature protection system, which relates to the technical field of air energy heat pumps, and belongs to an energy-saving heat exchange device. According to the invention, the compressor is prevented from being impacted, the selected refrigerant also has a larger supercooling degree, so that the refrigerant can absorb more heat from the air after throttling, the performance of the air heat source pump can be effectively improved, the air return method can be applied to the improvement and the improvement of the existing product, the air source heat pump system is changed little, the system is convenient to operate, the indoor air outlet temperature which is an important index for influencing the indoor comfort is also improved, the indoor environment condition in a severe cold area in winter is obviously improved, and the user perception comfort is obviously improved.
Description
Technical Field
The invention relates to the technical field of air-source heat pumps, belongs to an energy-saving heat exchange device, and particularly relates to a low-temperature protection system of an air-source heat pump.
Background
The air source heat pump is a device for converting low-level heat energy in air into high-level heat energy by consuming a certain high-level energy source and utilizing a thermodynamic cycle process, and belongs to an energy-saving heat exchange device.
The technical problem to be solved by the patent is that the existing defrosting technology is generally to defrost by the heat of the medium used by the four-way reversing valve, and the electric heating rod is additionally arranged beside the condenser, but the defrosting method has large energy consumption and poor effect, and especially can not normally defrost in winter below-5 ℃, even can not normally operate an air-source heat pump water heater or a heating air conditioner in severe cases, and the patent can automatically start or close the heating fin and the heating belt to defrost according to the working condition of the condenser by design, so that the defrosting device is convenient to use, obvious in energy-saving effect, and the heat of the heating fin and the heating belt can be transferred to the compressor through the cold medium in the copper pipe and then is used by the compressor to do work, thereby the secondary heat utilization is realized, the heat efficiency is obviously improved, and the energy is saved.
There are some disadvantages that the air source heat pump has problems of excessively high exhaust temperature, excessively large pressure ratio, reduced heating performance and the like of the compressor along with the reduction of the ambient temperature, the set cop is rapidly reduced along with the reduction of the outdoor ambient temperature, the pressure ratio of the compressor is increased, the exhaust temperature is continuously increased, the compressor is seriously damaged or burned out after long-time operation, and the energy consumption is relatively high, so that a low-temperature protection system of the air source heat pump is needed in the prior art to solve the problems.
Disclosure of Invention
The invention aims at: in order to solve the problems that the air source heat pump is a device for converting low-level heat energy in air into high-level heat energy by consuming a certain high-level energy and utilizing a thermodynamic cycle process, the air source heat pump can have the problems of overhigh exhaust temperature, overlarge pressure ratio, reduced heating performance and the like of a compressor along with the reduction of the environmental temperature, the cop of a unit rapidly drops along with the reduction of the outdoor environmental temperature, the pressure ratio of the compressor can be increased more and more, the exhaust temperature is increased continuously, and the compressor can be seriously damaged or burnt out during long-time operation.
In order to achieve the above purpose, the present invention adopts the following technical scheme:
The utility model provides an air energy heat pump low temperature protection system, includes central controller, central controller's input and indoor heat exchanger water pump control module's output electric connection, indoor heat exchanger water pump control module's input and refrigerant flow control module's output electric connection, refrigerant flow control module's input and refrigerant selection module's output electric connection, refrigerant selection module's input and start preheating time calculation module's output electric connection, start preheating time calculation module's input and compressor power calculation module's output electric connection, central controller's input still with cold wind prevent control module's output electric connection, cold wind prevent control module's input and electric heater circle control module's output electric connection, electric heater circle control module's input and return air circulation control module's output electric connection.
As a further description of the above technical solution:
The compressor power calculation module is used for calculating the power of the compressor when the system is stable in operation in the vapor compression refrigeration cycle, and the starting preheating time calculation module is used for starting preheating time of the air source heat pump system from the starting of the compressor to the stabilization of system parameters in the air source heat pump system;
in the vapor compression refrigeration cycle, the power P of the compressor when the system operation is stable is represented by specific enthalpy and specific volume:
Wherein q is the rated gas transmission capacity of the compressor, the unit is m 3/s, gamma is the gas transmission coefficient of the compressor, h1 and h2 are the specific enthalpy of suction and exhaust of the compressor respectively, the unit is KJ/kg, v 1 is the specific volume of suction of the compressor, the unit is m 3/kg, and n is the isentropic efficiency of the compressor;
In the starting stage, the air source heat pump control system is in a continuous change process of the suction pressure, the discharge pressure, the suction temperature and the like of the compressor, so that the power consumption of the air source heat pump control system can be calculated in an integral calculation mode;
the mass flow rate of the heat pump system is as follows:
the heat pump coefficient heating amount is as follows:
the heat pump coefficient refrigeration cop is:
Wherein ρ1 is the refrigerant vapor at the compressor suction port, in kg.m-3, V is the compressor displacement, in m 3 h-1, n is the compressor volumetric efficiency, h 3 is the enthalpy at the condenser outlet, in kj.kg-1;
the selected refrigerant can improve the superheat degree of the low-ring-temperature refrigerant working medium at the outlet of the evaporator, prevent the compressor from liquid impact, and has larger supercooling degree, so that the refrigerant can absorb more heat from the air after throttling, and further the performance of the air heat source pump can be effectively improved.
As a further description of the above technical solution:
The refrigerant selecting module is used for the air source heat pump to be in a gas-liquid two-phase state in the starting stage, part of the refrigerant which enters the compressor is still in a liquid state after being compressed, the system needs to evaporate the part of the liquid refrigerant during preheating, and the refrigeration coefficient, the pressure ratio and the exhaust temperature of the compressor are used as selection bases.
As a further description of the above technical solution:
The refrigerant flow control module is used for controlling an electronic expansion valve, an outdoor mechanism hot electron expansion valve and an outdoor side supercooling electronic expansion valve in the indoor heat exchanger to be opened to the maximum degree in the starting stage of the air source heat pump, and is used for delaying the starting time of the indoor heat exchanger water pump to avoid continuous heating of the refrigerant, and when the saturated temperature corresponding to the exhaust pressure of the compressor is higher than the water temperature of the indoor heat exchanger by 0.5-1.5 ℃, the air source heat pump is started again to avoid the refrigerant in the indoor heat exchanger from evaporating and overheating so as to reduce the refrigerant flow.
As a further description of the above technical solution:
The air return circulation control module is used for modulating thermal circulation of the air source heat pump, gaseous high-temperature and high-pressure refrigerant flowing out of the compressor flows through the four-way valve, enters the evaporator to emit heat and then is condensed into high-temperature and high-pressure liquid, liquid refrigerant is throttled by the capillary tube and then becomes low-temperature and low-pressure refrigerant liquid, and the liquid refrigerant liquid enters the condenser to exchange heat with outdoor side circulating air, absorbs heat and evaporates into low-temperature and low-pressure gas.
As a further description of the above technical solution:
The gaseous refrigerant returns to the air suction end of the compressor through the four-way valve, an electric heating ring is arranged on a copper pipe section of the air return pipe of the compressor connected with the four-way valve of the outdoor unit, the electric heating ring is sleeved on the surface of the copper pipe pipeline and is tightly connected with the copper pipe, so that the heat transfer specific area is increased, and the electric heating ring can be made of heat conductive materials such as a cylinder, aluminum, iron and the like.
As a further description of the above technical solution:
The air return circulation control module is used for the air source heat pump to electrify the electric heating ring to work and heat the pipeline in the operation process, the electric heating ring directly transmits heat to the copper pipe pipeline which is tightly sleeved with the electric heating ring after generating heat, the copper pipe pipeline absorbs the heat and then transmits the heat to the refrigerant in the copper pipe pipeline, so that the temperature of the refrigerant before entering the compressor is improved, and the air return temperature is improved.
As a further description of the above technical solution:
The installation position of the evaporator coil is arranged on an inlet pipe, an outlet pipe or a elbow of the evaporator according to different models and evaporator flow paths.
As a further description of the above technical solution:
The electric heating ring control module is used for controlling the running state of the electric heating ring mainly according to the coil temperature Tp of the indoor evaporator, and in the heating stage, when the indoor coil temperature Tp is less than or equal to T1 ℃, the electric heating ring works, and when the indoor coil temperature Tp is more than or equal to T2 ℃, the electric heating ring stops working, wherein the temperature range percentages of T1 and T2 are as follows: t1 is more than or equal to 9 ℃ and less than or equal to 60 ℃, T2 is more than or equal to 9 ℃ and less than or equal to 63 ℃, T1 is less than or equal to T2, wherein the electric heating ring takes a tubular electric heating element as a heating body, the element is bent and molded, and the element is poured and molded in a mold.
As a further description of the above technical solution:
The cold air prevention control module is used for controlling and adjusting the rotation speed of the indoor fan according to the temperature of the middle part of the evaporator of the indoor unit of the air source heat pump, if the rotation speed of the indoor fan is lower than a certain given value, the rotation speed of the indoor fan is reduced, and if the rotation speed of the indoor fan is higher than a certain given value, the set rotation speed is restored.
In summary, due to the adoption of the technical scheme, the beneficial effects of the invention are as follows:
In the invention, the air source heat pump control system is in a continuous change process of the suction pressure, the discharge pressure, the suction temperature and the like of the compressor in the starting stage, so the power consumption of the air source heat pump control system can be calculated in an integral calculation mode, and based on the power consumption, a proper refrigerant is selected, the selected refrigerant can improve the superheat degree of a low-temperature refrigerant working medium at the outlet of the evaporator, the compressor is prevented from being impacted by liquid, and the selected refrigerant also has a larger supercooling degree, so that the refrigerant can absorb more heat from the air after throttling, further the performance of the air source heat pump can be effectively improved, the energy-saving effect of the compressor is achieved, the air source heat pump system can be applied to improvement and lifting of the existing product by improving an air return method, the air source heat pump system is small in change and convenient to use, meanwhile, the indoor air outlet temperature which is an important index for influencing indoor comfort is also improved, the indoor environment condition in a severe winter area is obviously improved, and the user perceives that the comfort is obviously increased.
Drawings
Fig. 1 is a block diagram of a low-temperature protection system of an air-source heat pump according to the present invention.
Legend description:
101. A central controller; 102. the indoor heat exchanger water pump control module; 103. a refrigerant flow control module; 104. a refrigerant selection module; 105. starting a preheating time calculation module; 106. a compressor power calculation module; 107. the air return circulation control module; 108. an electric heating coil control module; 109. and a cold air prevention control module.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
The application mainly protects the compressor in the air source heat pump, so that the working performance of the compressor is improved, and the energy-saving effect of the compressor is further realized.
Referring to fig. 1, the present invention provides a technical solution:
example 1
The utility model provides an air energy heat pump low temperature protection system, including central controller 101, central controller 101's input and indoor heat exchanger water pump control module 102's output electric connection, indoor heat exchanger water pump control module 102's input and refrigerant flow control module 103's output electric connection, refrigerant flow control module 103's input and refrigerant selection module 104's output electric connection, refrigerant selection module 104's input and start preheating time calculation module 105's output electric connection, start preheating time calculation module 105's input and compressor power calculation module 106's output electric connection, central controller 101's input still is connected with cold wind prevention control module 109's output electric connection, cold wind prevention control module 109's input and electric heater circle control module 108's output electric connection, electric heater circle control module 108's input and return air circulation control module 107's output.
Specifically, as shown in fig. 1, in the vapor compression refrigeration cycle, the compressor power calculation module 106 is configured to calculate the power of the compressor when the system is running stably, and the time from when the compressor is started to when the system parameters are stable in the air source heat pump system is the start preheating time of the air source heat pump system;
in the vapor compression refrigeration cycle, the power P of the compressor when the system operation is stable is represented by specific enthalpy and specific volume:
Wherein q is the rated gas transmission capacity of the compressor, the unit is m 3/s, gamma is the gas transmission coefficient of the compressor, h1 and h2 are the specific enthalpy of suction and exhaust of the compressor respectively, the unit is KJ/kg, v 1 is the specific volume of suction of the compressor, the unit is m 3/kg, and n is the isentropic efficiency of the compressor;
In the starting stage, the air source heat pump control system is in a continuous change process of the suction pressure, the discharge pressure, the suction temperature and the like of the compressor, so that the power consumption of the air source heat pump control system can be calculated in an integral calculation mode;
the mass flow rate of the heat pump system is as follows:
the heat pump coefficient heating amount is as follows:
the heat pump coefficient refrigeration cop is:
Wherein ρ1 is the refrigerant vapor at the compressor suction port, in kg.m-3, V is the compressor displacement, in m 3 h-1, n is the compressor volumetric efficiency, h 3 is the enthalpy at the condenser outlet, in kj.kg-1;
the selected refrigerant can improve the superheat degree of the low-ring-temperature refrigerant working medium at the outlet of the evaporator, prevent the compressor from liquid impact, and has larger supercooling degree, so that the refrigerant can absorb more heat from the air after throttling, and further the performance of the air heat source pump can be effectively improved.
Specifically, as shown in fig. 1, the refrigerant selecting module 104 is configured to, in the start-up phase of the air source heat pump, make the refrigerant in a gas-liquid two-phase state entering the compressor, make part of the refrigerant still in a liquid state after compression, and evaporate the part of the liquid refrigerant during preheating, where the refrigeration coefficient, the pressure ratio and the compressor discharge temperature of the refrigerant are used as selection criteria.
Specifically, as shown in fig. 1, the refrigerant flow control module 103 is configured to control the electronic expansion valve, the outdoor mechanism hot electron expansion valve and the outdoor side supercooling electronic expansion valve in the indoor heat exchanger to be opened to the maximum degree in the starting stage of the air source heat pump, and the indoor heat exchanger water pump control module 102 is configured to delay the indoor heat exchanger water pump opening time, so as to avoid continuous heating of the refrigerant, and to restart the air source heat pump when the saturation temperature corresponding to the exhaust pressure of the compressor is higher than the indoor heat exchanger water temperature by 0.5-1.5 ℃, so as to avoid the refrigerant in the indoor heat exchanger from evaporating and overheating to reduce the refrigerant flow.
Example two
The utility model provides an air energy heat pump low temperature protection system, including central controller 101, central controller 101's input and indoor heat exchanger water pump control module 102's output electric connection, indoor heat exchanger water pump control module 102's input and refrigerant flow control module 103's output electric connection, refrigerant flow control module 103's input and refrigerant selection module 104's output electric connection, refrigerant selection module 104's input and start preheating time calculation module 105's output electric connection, start preheating time calculation module 105's input and compressor power calculation module 106's output electric connection, central controller 101's input still is connected with cold wind prevention control module 109's output electric connection, cold wind prevention control module 109's input and electric heater circle control module 108's output electric connection, electric heater circle control module 108's input and return air circulation control module 107's output.
Specifically, as shown in fig. 1, the air return circulation control module 107 is used for modulating thermal circulation by an air source heat pump, the gaseous high-temperature high-pressure refrigerant flowing out of the compressor flows through the four-way valve, enters the evaporator to emit heat and then is condensed into high-temperature high-pressure liquid, the liquid refrigerant is throttled by the capillary tube and then becomes low-temperature low-pressure refrigerant liquid, and enters the condenser to exchange heat with outdoor side circulating air, and absorbs heat and evaporates into low-temperature low-pressure gas.
Specifically, as shown in fig. 1, the gaseous refrigerant returns to the air suction end of the compressor through the four-way valve, an electric heating ring is installed on the copper pipe section of the air return pipe of the compressor connected with the four-way valve of the outdoor unit, and the electric heating ring is sleeved on the surface of the copper pipe and is tightly connected with the copper pipe, so that the heat transfer specific area is increased, and the electric heating ring can be made of heat conductive materials such as copper, aluminum, iron and the like.
Specifically, as shown in fig. 1, the air return circulation control module 107 is used for the air source heat pump to energize and heat the pipeline in the operation process, after the electric heating coil generates heat, the heat is directly transferred to the copper pipe pipeline which is tightly sleeved with the electric heating coil, after the copper pipe pipeline absorbs the heat, the heat is transferred to the refrigerant in the copper pipe pipeline, so that the temperature of the refrigerant before entering the compressor is increased, and the air return temperature is increased.
Specifically, as shown in fig. 1, the installation position of the evaporator coil is set on the evaporator inlet pipe, outlet pipe or elbow according to different models and evaporator flow paths.
Specifically, as shown in fig. 1, the operation state of the electric heating coil control module 108 for the electric heating coil is mainly controlled according to the indoor evaporator coil temperature Tp, in the heating stage, when the indoor coil temperature Tp is less than or equal to T1 ℃, the electric heating coil works, and when the indoor coil temperature Tp is less than or equal to T2 ℃, the electric heating coil stops working, wherein the temperature range percentages of T1 and T2 are as follows: t1 is more than or equal to 9 ℃ and less than or equal to 60 ℃, T2 is more than or equal to 9 ℃ and less than or equal to 63 ℃, T1 is less than or equal to T2, wherein the electric heating ring takes a tubular electric heating element as a heating body, the element is bent and molded, and the element is poured and molded in a mold.
Specifically, as shown in fig. 1, the cold air prevention control module 109 is configured to control and adjust the rotation speed of the indoor fan according to the temperature of the middle part of the evaporator of the indoor unit of the air source heat pump, if the rotation speed is lower than a certain given value, the rotation speed of the indoor fan is reduced, and if the rotation speed is higher than a certain given value, the rotation speed is restored.
The embodiment specifically comprises the following steps: the air return method can be applied to improvement and promotion of the existing products, the air source heat pump system is small in change and convenient to operate, meanwhile, the indoor air outlet temperature which is an important index for influencing indoor comfort is also improved to some extent, an obvious improvement effect is achieved on indoor environment conditions in severe cold areas in winter, and user perception comfort is obviously improved.
Working principle: when in use, the compressor power calculation module 106 is used for calculating the power of the compressor when the system is running stably in the vapor compression refrigeration cycle, the starting preheating time calculation module 105 is used for starting the preheating time of the air source heat pump system from the starting of the compressor to the stabilization of system parameters in the air source heat pump system, the refrigerant selection module 104 is used for controlling the electronic expansion valve, the outdoor mechanism hot electron expansion valve and the outdoor side supercooling electronic expansion valve in the indoor heat exchanger to be opened to the maximum degree in the starting stage of the air source heat pump, the refrigerant which enters the compressor and is in a gas-liquid two-phase state is still in a liquid state after being compressed, the system needs to evaporate the part of liquid refrigerant when in preheating, the refrigeration coefficient, the pressure ratio and the exhaust temperature of the compressor of the refrigerant are taken as selection bases, the refrigerant flow control module 103 is used for controlling the electronic expansion valve, the outdoor mechanism hot electron expansion valve and the outdoor side supercooling electronic expansion valve in the indoor heat exchanger to be opened to the maximum degree in the starting stage of the air source heat pump, the indoor heat exchanger water pump control module 102 is used for delaying the starting time of the indoor heat exchanger water pump to avoid continuous heating of the refrigerant, and restarting the indoor heat exchanger when the saturated temperature corresponding to the exhaust pressure of the compressor is higher than the water temperature of the indoor heat exchanger by 0.5-1.5 ℃, so as to avoid the refrigerant in the indoor heat exchanger from evaporating and overheating to reduce the refrigerant flow, the air return circulation control module 107 is used for modulating the heat circulation by the air source heat pump, the gaseous high-temperature high-pressure refrigerant flowing out from the compressor flows through the four-way valve to enter the evaporator to release heat and then condense into high-temperature high-pressure liquid, the liquid refrigerant becomes low-temperature low-pressure refrigerant liquid after capillary throttling, enters the condenser to exchange heat with the circulating air at the outdoor side, the endothermic evaporation becomes low-temperature low-pressure gas, the gaseous refrigerant returns to the air suction end of the compressor through the four-way valve, an electric heating ring is arranged on a copper pipe section of an air return pipe of an outdoor unit four-way valve connecting compressor, the electric heating ring is sleeved on the surface of the copper pipe and is tightly connected with a copper pipe, so that the heat transfer specific area is increased, the materials of the electric heating ring can be selected from heat conducting materials such as a cylinder, aluminum and iron, the air return circulation control module 107 is used for the air source heat pump to work and heat pipes in the operation process, the electric heating ring directly transfers heat to the copper pipe tightly sleeved with the electric heating ring after generating heat, the copper pipe absorbs heat and then transfers the heat to a refrigerant in the copper pipe, the temperature of the refrigerant before entering the compressor is increased, the air return temperature is increased, the installation position of an evaporator coil is required to be arranged on an evaporator inlet pipe, an outlet pipe or a bent head according to different models, the installation position of the evaporator coil is mainly controlled according to the temperature Tp of the indoor evaporator coil, the electric heating ring control module 108 is used for controlling the temperature Tp of the indoor evaporator coil, in the heating stage, when the indoor coil temperature Tp is at T1 ℃, when the indoor coil temperature Tp is more than or equal to 2 ℃, the temperature T1 and the temperature range of T2 is less than or equal to the temperature of the indoor coil temperature T2: the temperature T1 is more than or equal to 9 ℃ and less than or equal to 60 ℃, the temperature T2 is more than or equal to 9 ℃ and less than or equal to 63 ℃, and T1 is less than T2, wherein the electric heating ring takes a tubular electric heating element as a heating body, the element is bent and formed, the element enters a die for pouring and forming, the cold air prevention control module 109 is used for controlling and adjusting the rotating speed of an indoor fan according to the middle temperature of an evaporator of an indoor unit of an air source heat pump, if the rotating speed is lower than a certain given value, the rotating speed of the indoor fan is reduced, and if the rotating speed is raised and higher than a certain given value, the set rotating speed is restored.
It is noted that relational terms such as first and second, and the like are used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Moreover, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one … …" does not exclude the presence of other like elements in a process, method, article, or apparatus that comprises the element.
Claims (4)
1. The air energy heat pump low-temperature protection system is characterized by comprising a central controller (101), wherein the input end of the central controller (101) is electrically connected with the output end of an indoor heat exchanger water pump control module (102), the input end of the indoor heat exchanger water pump control module (102) is electrically connected with the output end of a refrigerant flow control module (103), the input end of the refrigerant flow control module (103) is electrically connected with the output end of a refrigerant selection module (104), the input end of the refrigerant selection module (104) is electrically connected with the output end of a start preheating time calculation module (105), the input end of the start preheating time calculation module (105) is electrically connected with the output end of a compressor power calculation module (106), the input end of the central controller (101) is also electrically connected with the output end of a cold air prevention control module (109), the input end of the cold air prevention control module (109) is electrically connected with the output end of an electric heating ring control module (108), and the input end of the electric heating ring control module (108) is electrically connected with the output end of a return air circulation control module (107).
The starting preheating time calculation module (105) is used for starting preheating time of the air source heat pump system from the starting of the compressor to the stabilization of system parameters in the air source heat pump system;
The refrigerant selecting module (104) is used for enabling the air source heat pump to enter the refrigerant in a gas-liquid two-phase state of the compressor in the starting stage, and part of the refrigerant is still in a liquid state after being compressed, and the system needs to evaporate the part of the liquid refrigerant when preheating, wherein the refrigeration coefficient, the pressure ratio and the exhaust temperature of the compressor are used as selection bases;
The refrigerant flow control module (103) is used for controlling an electronic expansion valve, an outdoor mechanism hot electron expansion valve and an outdoor side supercooling electronic expansion valve in the indoor heat exchanger to be opened to the maximum degree in the starting stage of the air source heat pump, the indoor heat exchanger water pump control module (102) is used for delaying the starting time of the indoor heat exchanger water pump to avoid continuous heating of the refrigerant, and the refrigerant is started again when the saturated temperature corresponding to the exhaust pressure of the compressor is higher than the water temperature of the indoor heat exchanger by 0.5-1.5 ℃, so that the refrigerant in the indoor heat exchanger is prevented from evaporating and overheating to reduce the refrigerant flow;
the air return circulation control module (107) is used for modulating thermal circulation of the air source heat pump, gaseous high-temperature and high-pressure refrigerant flowing out of the compressor flows through the four-way valve, enters the evaporator to emit heat and then is condensed into high-temperature and high-pressure liquid, liquid refrigerant is throttled by the capillary tube and then becomes low-temperature and low-pressure refrigerant liquid, and enters the condenser to exchange heat with outdoor side circulating air, and absorbs heat and evaporates into low-temperature and low-pressure gas;
an electric heating ring is arranged on a copper pipe section of an air return pipe of the four-way valve connecting compressor of the outdoor unit;
the air return circulation control module (107) is used for electrifying the electric heating ring to work and heating the pipeline in the operation process of the air source heat pump, the electric heating ring directly transmits heat to the copper pipe pipeline which is tightly sleeved with the electric heating ring after generating heat, the copper pipe pipeline absorbs the heat and then transmits the heat to the refrigerant in the copper pipe pipeline, so that the temperature of the refrigerant before entering the compressor is improved, and the air return temperature is improved;
The electric heating ring control module (108) is used for controlling the running state of the electric heating ring mainly according to the indoor evaporator coil temperature Tp, the electric heating ring works when the indoor coil temperature Tp is less than or equal to T1 ℃ and stops working when the indoor coil temperature Tp is less than or equal to T2 ℃, wherein the temperature range percentages of T1 and T2 are as follows: t1 is more than or equal to 9 ℃ and less than or equal to 60 ℃, T2 is more than or equal to 9 ℃ and less than or equal to 63 ℃, T1 is less than T2, wherein the electric heating ring takes a tubular electric heating element as a heating body, the element is bent and molded, and the element is poured and molded in a mold;
the cold air prevention control module (109) is used for controlling and adjusting the rotating speed of the indoor fan according to the temperature of the middle part of the evaporator of the indoor unit of the air source heat pump, if the rotating speed is lower than a certain given value, the rotating speed of the indoor fan is reduced, and if the rotating speed is higher than a certain given value, the rotating speed is restored.
2. An air-source heat pump cryoprotection system according to claim 1, wherein the compressor power calculation module (106) is configured to calculate the power of the compressor when the system is operating steadily in a vapor compression refrigeration cycle.
3. The air-source heat pump low-temperature protection system according to claim 2, wherein the gaseous refrigerant returns to the air suction end of the compressor through the four-way valve, and the electric heating ring is sleeved on the surface of the copper pipe pipeline and is tightly connected with the copper pipe, so that the heat transfer specific area is increased, and the material of the electric heating ring is copper, aluminum or iron.
4. An air-source heat pump cryoprotection system according to claim 3, wherein the evaporator coil is mounted in a different type of evaporator inlet, outlet or elbow depending on the type of evaporator flow path.
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Citations (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2570706Y (en) * | 2002-09-13 | 2003-09-03 | 阎首弟 | Overlapping type hyperthermal water source heat pump apparatus |
| CN102230701A (en) * | 2011-06-10 | 2011-11-02 | Tcl空调器(中山)有限公司 | Low-temperature refrigeration device and control method thereof |
| CN102331050A (en) * | 2011-07-23 | 2012-01-25 | 济源市贝迪地能中央空调设备有限公司 | Ultralow-temperature heat source and heat pump type air conditioning system for electric automobile |
| CN104197596A (en) * | 2014-09-18 | 2014-12-10 | 山东宏力热泵能源股份有限公司 | Self-control device for low-temperature liquid impact prevention of refrigeration compressor and self-control method |
| CN105466095A (en) * | 2016-01-25 | 2016-04-06 | 珠海格力电器股份有限公司 | Electric heating control method, device and system for low-temperature refrigeration air conditioning unit |
| CN105674636A (en) * | 2016-03-30 | 2016-06-15 | 天津亭华科技有限公司 | High-low temperature test chamber with function of protecting compressor and refrigeration system |
| CN105928280A (en) * | 2016-05-06 | 2016-09-07 | Tcl空调器(中山)有限公司 | Protection method and device for air conditioner compressor |
| CN107560259A (en) * | 2017-09-01 | 2018-01-09 | 广东美的暖通设备有限公司 | The low-temperature starting control method and device of multiple on-line system, multiple on-line system |
| CN109654781A (en) * | 2018-12-12 | 2019-04-19 | 广东华天成新能源科技股份有限公司 | A kind of control method of high stability heat pump system |
| CN110701840A (en) * | 2019-09-12 | 2020-01-17 | 浙江中广电器股份有限公司 | Compressor starting low-pressure control method, compressor and low-temperature heat pump system |
| CN112178978A (en) * | 2020-10-15 | 2021-01-05 | 广东纽恩泰新能源科技发展有限公司 | Protection control method for overhigh exhaust temperature of variable frequency heat pump |
| CN215062986U (en) * | 2021-03-05 | 2021-12-07 | 郑州天地节能设备有限公司 | Compressor overcurrent protection air source heat pump machine |
| CN218600035U (en) * | 2022-11-08 | 2023-03-10 | 宁波东大空调设备有限公司 | Be suitable for frostproofing air source heat pump system of low temperature and ultra-low temperature environment |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR102319725B1 (en) * | 2016-04-07 | 2021-11-03 | 엘리 쿠프리 애스워드, 에밀리 | Refrigeration system control and protection devices |
-
2021
- 2021-08-12 CN CN202110923719.2A patent/CN113758048B/en active Active
Patent Citations (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2570706Y (en) * | 2002-09-13 | 2003-09-03 | 阎首弟 | Overlapping type hyperthermal water source heat pump apparatus |
| CN102230701A (en) * | 2011-06-10 | 2011-11-02 | Tcl空调器(中山)有限公司 | Low-temperature refrigeration device and control method thereof |
| CN102331050A (en) * | 2011-07-23 | 2012-01-25 | 济源市贝迪地能中央空调设备有限公司 | Ultralow-temperature heat source and heat pump type air conditioning system for electric automobile |
| CN104197596A (en) * | 2014-09-18 | 2014-12-10 | 山东宏力热泵能源股份有限公司 | Self-control device for low-temperature liquid impact prevention of refrigeration compressor and self-control method |
| CN105466095A (en) * | 2016-01-25 | 2016-04-06 | 珠海格力电器股份有限公司 | Electric heating control method, device and system for low-temperature refrigeration air conditioning unit |
| CN105674636A (en) * | 2016-03-30 | 2016-06-15 | 天津亭华科技有限公司 | High-low temperature test chamber with function of protecting compressor and refrigeration system |
| CN105928280A (en) * | 2016-05-06 | 2016-09-07 | Tcl空调器(中山)有限公司 | Protection method and device for air conditioner compressor |
| CN107560259A (en) * | 2017-09-01 | 2018-01-09 | 广东美的暖通设备有限公司 | The low-temperature starting control method and device of multiple on-line system, multiple on-line system |
| CN109654781A (en) * | 2018-12-12 | 2019-04-19 | 广东华天成新能源科技股份有限公司 | A kind of control method of high stability heat pump system |
| CN110701840A (en) * | 2019-09-12 | 2020-01-17 | 浙江中广电器股份有限公司 | Compressor starting low-pressure control method, compressor and low-temperature heat pump system |
| CN112178978A (en) * | 2020-10-15 | 2021-01-05 | 广东纽恩泰新能源科技发展有限公司 | Protection control method for overhigh exhaust temperature of variable frequency heat pump |
| CN215062986U (en) * | 2021-03-05 | 2021-12-07 | 郑州天地节能设备有限公司 | Compressor overcurrent protection air source heat pump machine |
| CN218600035U (en) * | 2022-11-08 | 2023-03-10 | 宁波东大空调设备有限公司 | Be suitable for frostproofing air source heat pump system of low temperature and ultra-low temperature environment |
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|---|---|
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