CN113758048A - Air energy heat pump low-temperature protection system - Google Patents
Air energy heat pump low-temperature protection system Download PDFInfo
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- CN113758048A CN113758048A CN202110923719.2A CN202110923719A CN113758048A CN 113758048 A CN113758048 A CN 113758048A CN 202110923719 A CN202110923719 A CN 202110923719A CN 113758048 A CN113758048 A CN 113758048A
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- 239000003507 refrigerant Substances 0.000 claims abstract description 95
- 239000007788 liquid Substances 0.000 claims abstract description 28
- 238000004781 supercooling Methods 0.000 claims abstract description 7
- 238000005485 electric heating Methods 0.000 claims description 58
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 claims description 24
- 229910052802 copper Inorganic materials 0.000 claims description 24
- 239000010949 copper Substances 0.000 claims description 24
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 24
- 238000010438 heat treatment Methods 0.000 claims description 22
- 230000002265 prevention Effects 0.000 claims description 12
- 238000005057 refrigeration Methods 0.000 claims description 12
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 claims description 8
- 230000006835 compression Effects 0.000 claims description 8
- 238000007906 compression Methods 0.000 claims description 8
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 claims description 4
- 229910052782 aluminium Inorganic materials 0.000 claims description 4
- 239000004020 conductor Substances 0.000 claims description 4
- 238000001704 evaporation Methods 0.000 claims description 4
- 229910052742 iron Inorganic materials 0.000 claims description 4
- 239000000463 material Substances 0.000 claims description 4
- 238000013021 overheating Methods 0.000 claims description 4
- 238000005266 casting Methods 0.000 claims description 3
- 238000000465 moulding Methods 0.000 claims description 3
- 230000008020 evaporation Effects 0.000 claims 1
- 238000000034 method Methods 0.000 abstract description 11
- 230000008859 change Effects 0.000 abstract description 3
- 230000008447 perception Effects 0.000 abstract description 3
- 230000006872 improvement Effects 0.000 abstract description 2
- 230000008569 process Effects 0.000 description 6
- 238000010257 thawing Methods 0.000 description 5
- 230000005540 biological transmission Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 4
- 230000009467 reduction Effects 0.000 description 4
- 238000009434 installation Methods 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 238000009491 slugging Methods 0.000 description 1
- 230000003245 working effect Effects 0.000 description 1
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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 a low-temperature protection system of an air energy heat pump, relates to the technical field of air energy heat pumps, and belongs to an energy-saving heat exchange device. According to the invention, liquid impact of the compressor is prevented, the selected refrigerant 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 heat source pump can be applied to improvement and promotion of the existing product by improving the air return method, the air heat source pump system is small in change and convenient to operate, meanwhile, the indoor air outlet temperature which is an important index influencing the indoor comfort is also improved, the indoor environment condition of 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 energy heat pumps, belongs to an energy-saving heat exchange device, and particularly relates to a low-temperature protection system of an air energy heat pump.
Background
An air source heat pump is a device which converts low-level heat energy in air into high-level heat energy by consuming certain high-level energy and utilizing a thermodynamic cycle process, and belongs to an energy-saving heat exchange device.
For example, the Chinese patent discloses 'an ultralow temperature air energy heat pump unit and a use method thereof' (patent number: CN102374702A), the technical problem solved by the patent is that the prior defrosting technology generally defrosts by the heat of a medium of a four-way reversing valve, and some defrosting technologies are that an electric heating rod is additionally arranged beside a condenser, however, the defrosting method has large energy consumption and poor effect, especially in winter below minus 5 ℃, the defrosting can not be normally carried out, even the air energy heat pump water heater or the heating air conditioner can not normally work in serious conditions, and the patent is through designing, can be according to the operating condition automatic start of condenser or close the fin that generates heat and generate heat the area defrosting, convenient to use, energy-conserving effect is obvious, and the heat accessible cold medium in the copper pipe of fin that generates heat and the area that generates heat transmits to the compressor, does work through the compressor again, and secondary heat utilizes, is showing the thermal efficiency that improves, the energy saving.
Still have some weak points, along with the reduction of ambient temperature, air source heat pump can appear compressor exhaust temperature too high, the pressure ratio is too big, heating performance descends the scheduling problem, along with the reduction of outdoor ambient temperature, unit cop sharply descends, and the pressure ratio of compressor can be bigger and bigger, leads to exhaust temperature to rise constantly, and long-time operation can seriously damage or burn out the compressor, and leads to the compressor energy consumption great, therefore, need an air energy heat pump low temperature protection system to solve above-mentioned problem in the present stage urgently.
Disclosure of Invention
The invention aims to: the air source heat pump low-temperature protection system is provided for solving 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 certain high-grade energy and utilizing a thermodynamic cycle process, the air source heat pump has the problems of overhigh exhaust temperature, overlarge pressure ratio, reduced heating performance and the like of a compressor along with the reduction of the ambient temperature, the cop of a unit is sharply reduced along with the reduction of the outdoor ambient temperature, the pressure ratio of the compressor is increased, the exhaust temperature is increased continuously, and the compressor can be seriously damaged or burnt down due to long-time operation.
In order to achieve the purpose, the invention adopts the following technical scheme:
an air energy heat pump low-temperature protection system comprises a central controller, wherein the input end of the central controller is electrically connected with the output end of a water pump control module of an indoor heat exchanger, the input end of the indoor heat exchanger water pump control module is electrically connected with the output end of the refrigerant flow control module, the input end of the refrigerant flow control module is electrically connected with the output end of the refrigerant selection module, the input end of the refrigerant selection module is electrically connected with the output end of the starting preheating time calculation module, the input end of the starting preheating time calculation module is electrically connected with the output end of the compressor power calculation module, the input end of the central controller is also electrically connected with the output end of the cold air prevention control module, the input end of the cold air prevention control module is electrically connected with the output end of the electric heating ring control module, the input end of the electric heating ring control module is electrically connected with the output end of the air return circulation control module.
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 runs stably in a vapor compression refrigeration cycle, and the time of the starting preheating time calculation module from the start of the compressor to the stability of system parameters in the air source heat pump system is the starting preheating time of the air source heat pump system;
in the vapor compression refrigeration cycle, the power P of the compressor is expressed by specific enthalpy and specific volume when the system is stably operated:
wherein q is the rated gas transmission capacity of the compressor and the unit is m3S, gamma is the gas transmission coefficient of the compressor, h1，h2Respectively the specific enthalpy of suction and discharge of the compressor, in KJ/kg，v1Is the suction specific volume of the compressor, and has the unit of m3(iii)/kg, n is the isentropic efficiency of the compressor;
in the starting stage of the air source heat pump control system, the suction pressure, the discharge pressure, the suction temperature and the like of the compressor are in a constantly changing process, so that the power consumption of the air source heat pump control system can be calculated in an integral calculation mode;
the mass flow of the heat pump system is as follows:
m＝ρ1.Vn*
the heat pump coefficient heating capacity is as follows:
Q＝m(h2-h3)
the heat pump coefficient refrigeration cop is:
in the formula, ρ1Is the vapor degree of refrigerant at the suction port of the compressor, and has the unit of kg.m-3V is the compressor displacement in m3.h-1，n*For compressor volumetric efficiency, h3Is enthalpy value of outlet of condenser, and has KJ-1；
The selected refrigerant can improve the superheat degree of a low-ring-temperature refrigerant working medium at the outlet of the evaporator, liquid impact of the compressor is prevented, and the selected refrigerant also has a large supercooling degree, so that the refrigerant can absorb more heat from the air after throttling, and the performance of the air heat source pump can be effectively improved.
As a further description of the above technical solution:
the refrigerant selection module is used for enabling the air source heat pump to enter a compressor to be a refrigerant in a gas-liquid two-phase state in a starting stage, part of the refrigerant is still in a liquid state after compression, the part of the liquid refrigerant needs to be evaporated firstly during preheating, and the refrigeration coefficient, the pressure ratio and the exhaust temperature ℃ of the compressor of the refrigerant are used as selection bases.
As a further description of the above technical solution:
the control module of the water pump of the indoor heat exchanger is used for delaying the opening time of the water pump of the indoor heat exchanger to avoid continuously heating the refrigerant, and the control module of the water pump of the indoor heat exchanger is opened again when the saturation temperature corresponding to the exhaust pressure of the compressor is 0.5-1.5 ℃ higher than the water temperature of the indoor heat exchanger, so that the refrigerant in the indoor heat exchanger is prevented from evaporating and overheating to reduce the flow of the refrigerant.
As a further description of the above technical solution:
the air return circulation control module is used for modulating heat 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 is programmed into low-temperature and low-pressure refrigerant liquid, enters the condenser to perform heat exchange with outdoor side circulating air, absorbs heat and evaporates to form 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, the electric heating ring is installed on the copper pipe section of the air return pipe of the outdoor unit four-way valve connected with the compressor, the electric heating ring is sleeved on the surface of the copper pipe and is tightly connected with the copper pipe so as to increase the heat transfer specific area, and the material of the electric heating ring can be selected from heat conductive materials such as cylinders, aluminum, iron and the like.
As a further description of the above technical solution:
the air return circulation control module is used for electrifying the electric heating ring to work and heating the pipeline when the air source heat pump operates, the electric heating ring directly transfers heat to the copper pipeline which is tightly sleeved with the electric heating ring after generating heat, the copper pipeline transfers the heat to a refrigerant in the copper pipeline after absorbing the heat, 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 required to be 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 coil control module is used for controlling the running state of the electric heating coil mainly 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, when the indoor coil temperature Tp is more than or equal to T2 ℃, the electric heating coil stops working, and the temperature range ratio of T1 to T2 is as follows: t1 of more than or equal to 9 ℃ and less than or equal to 60 ℃, T2 of more than or equal to 9 ℃ and less than 63 ℃, and T1 and T2, wherein the electric heating ring takes a tubular electric heating element as a heating element, the element is bent and molded, and the element enters a die for casting and molding.
As a further description of the above technical solution:
the cold air prevention control module 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 air source heat pump indoor unit, if the rotating speed of the indoor fan is lower than a certain given value, the rotating speed of the indoor fan is reduced, and if the rotating speed is increased and is higher than the certain given value, the set rotating speed is recovered.
In summary, due to the adoption of the technical scheme, the invention has the beneficial effects that:
in the invention, the air source heat pump control system is in the starting stage, the air suction pressure, the air discharge pressure, the air suction temperature and the like of the compressor are in the process of changing continuously, therefore, the power consumption of the air source heat pump control system can be calculated by 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-ring-temperature refrigerant working medium at the outlet of an evaporator to prevent the compressor from generating liquid slugging, and the selected refrigerant also has larger supercooling degree, so that the refrigerant can absorb more heat from the air after throttling, the performance of the air source heat pump can be effectively improved, the energy-saving effect of the compressor is achieved, and the air source heat pump control system can be applied to the improvement and promotion of the existing product by improving the air return method, the air source heat pump system has small change and is convenient to operate, and the indoor air outlet temperature which is an important index influencing the indoor comfort is also improved, the indoor environment condition of a severe cold area in winter is obviously improved, and the perception comfort of a user is obviously improved.
Drawings
Fig. 1 is a block diagram of a low-temperature protection system of an air-source heat pump according to the present invention.
Illustration of the drawings:
101. a central controller; 102. a water pump control module of the indoor heat exchanger; 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. a return air circulation control module; 108. an electric heating coil control module; 109. and a cold air prevention control module.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
This application is mainly implemented the protection to the compressor among the air-source heat pump for the working property of compressor obtains promoting, and then realizes the energy-conserving effect of compressor.
Referring to fig. 1, the present invention provides a technical solution:
example one
The utility model provides an air-source heat pump low temperature protection system, including central controller 101, the input of central controller 101 and the output electric connection of indoor heat exchanger water pump control module 102, the input of indoor heat exchanger water pump control module 102 and the output electric connection of refrigerant flow control module 103, the input of refrigerant flow control module 103 and the output electric connection of refrigerant selection module 104, the input of refrigerant selection module 104 and the output electric connection of starting preheating time calculation module 105, the input of starting preheating time calculation module 105 and the output electric connection of compressor power calculation module 106, the input of central controller 101 still with the output electric connection of cold wind prevention control module 109, the input of cold wind prevention control module 109 and the output electric connection of electric heating circle control module 108, the input of electric heating circle control module 108 and the output electric connection of air return circulation control module 107.
Specifically, as shown in fig. 1, the compressor power calculation module 106 is used in a vapor compression refrigeration cycle to calculate the power of the compressor when the system operates stably, and the time from the start of the compressor to the time 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 is expressed by specific enthalpy and specific volume when the system is stably operated:
wherein q is the rated gas transmission capacity of the compressor and the unit is m3S, gamma is the gas transmission coefficient of the compressor, h1，h2Respectively, the specific enthalpy of suction and discharge of the compressor, with the unit of KJ/kg, v1Is the suction specific volume of the compressor, and has the unit of m3(iii)/kg, n is the isentropic efficiency of the compressor;
in the starting stage of the air source heat pump control system, the suction pressure, the discharge pressure, the suction temperature and the like of the compressor are in a constantly changing process, so that the power consumption of the air source heat pump control system can be calculated in an integral calculation mode;
the mass flow of the heat pump system is as follows:
m＝ρ1.Vn*
the heat pump coefficient heating capacity is as follows:
Q＝m(h2-h3)
the heat pump coefficient refrigeration cop is:
in the formula, ρ1Is the vapor degree of refrigerant at the suction port of the compressor, and has the unit of kg.m-3V is the compressor displacement in m3.h-1，n*For compressor volumetric efficiency, h3Is enthalpy value of outlet of condenser, and has KJ-1；
The selected refrigerant can improve the superheat degree of a low-ring-temperature refrigerant working medium at the outlet of the evaporator, liquid impact of the compressor is prevented, and the selected refrigerant also has a large supercooling degree, so that the refrigerant can absorb more heat from the air after throttling, and the performance of the air heat source pump can be effectively improved.
Specifically, as shown in fig. 1, the refrigerant selection module 104 is configured to, in a starting stage of the air source heat pump, enable a part of refrigerant entering the compressor to be in a gas-liquid two-phase state, and after the part of refrigerant is compressed, still enable the part of refrigerant to be in a liquid state, and during preheating, the system needs to evaporate the part of liquid refrigerant, and the refrigeration coefficient, the pressure ratio, and the compressor discharge temperature ℃ of the refrigerant are taken as selection bases.
Specifically, as shown in fig. 1, the refrigerant flow control module 103 is used for controlling the electronic expansion valve, the outdoor unit heating electronic expansion valve and the outdoor side supercooling electronic expansion valve in the indoor heat exchanger to be opened to the maximum extent in the starting stage of the air source heat pump, and the indoor heat exchanger water pump control module 102 is used for delaying the opening time of the indoor heat exchanger water pump to avoid continuously heating the refrigerant, and is opened again when the saturation temperature corresponding to the discharge 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 and reducing the refrigerant flow.
Example two
The utility model provides an air-source heat pump low temperature protection system, including central controller 101, the input of central controller 101 and the output electric connection of indoor heat exchanger water pump control module 102, the input of indoor heat exchanger water pump control module 102 and the output electric connection of refrigerant flow control module 103, the input of refrigerant flow control module 103 and the output electric connection of refrigerant selection module 104, the input of refrigerant selection module 104 and the output electric connection of starting preheating time calculation module 105, the input of starting preheating time calculation module 105 and the output electric connection of compressor power calculation module 106, the input of central controller 101 still with the output electric connection of cold wind prevention control module 109, the input of cold wind prevention control module 109 and the output electric connection of electric heating circle control module 108, the input of electric heating circle control module 108 and the output electric connection of air return circulation control module 107.
Specifically, as shown in fig. 1, the air return cycle control module 107 is used for air source heat pump modulation heat cycle, gaseous high-temperature and high-pressure refrigerant flowing out of the compressor flows through the four-way valve, enters the evaporator to release heat and then is condensed into high-temperature and high-pressure liquid, the liquid refrigerant is throttled by the capillary tube and then is programmed into low-temperature and low-pressure refrigerant liquid, enters the condenser to exchange heat with the outdoor circulating air, and absorbs heat and evaporates to form low-temperature and low-pressure gas.
Specifically, as shown in fig. 1, the gaseous refrigerant returns to the suction end of the compressor through the four-way valve, the electric heating coil is installed at the copper pipe section of the air return pipe of the outdoor unit four-way valve connected to the compressor, and the electric heating coil is sleeved on the surface of the copper pipe and tightly connected with the copper pipe to increase the heat transfer ratio area, and the material of the electric heating coil can be selected from heat conductive materials such as a cylinder, aluminum, iron and the like.
Specifically, as shown in fig. 1, the air-return circulation control module 107 is used for electrifying the electric heating ring to work and heat the pipeline during the operation of the air source heat pump, the electric heating ring directly transfers heat to the copper pipeline tightly sleeved with the electric heating ring after generating heat, and the copper pipeline absorbs heat and then transfers the heat to the refrigerant in the copper 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 required to be arranged on the inlet pipe, the outlet pipe or the elbow of the evaporator according to different models and evaporator flow paths.
Specifically, as shown in fig. 1, the electric heating coil control module 108 is configured to control the operation state of the electric heating coil mainly according to the indoor evaporator coil temperature Tp, and in the heating phase, when the indoor coil temperature Tp is less than or equal to T1 ℃, the electric heating coil operates, and when the indoor coil temperature Tp is greater than or equal to T2 ℃, the electric heating coil stops operating, where the temperature range ratio of T1 to T2 is: t1 of more than or equal to 9 ℃ and less than or equal to 60 ℃, T2 of more than or equal to 9 ℃ and less than 63 ℃, and T1 and T2, wherein the electric heating ring takes a tubular electric heating element as a heating element, the element is bent and molded, and the element enters a die for casting and molding.
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 portion of the evaporator of the air source heat pump indoor unit, and if the rotation speed of the indoor fan is lower than a predetermined value, the rotation speed of the indoor fan is reduced, and if the rotation speed of the indoor fan is increased and is higher than the predetermined value, the set rotation speed is restored.
The embodiment specifically includes: the air return method is improved, the air source heat pump system is small in change and convenient to operate, the indoor air outlet temperature which is an important index influencing indoor comfort is also improved, the indoor environment condition of a severe cold area in winter is obviously improved, and the user perception comfort is obviously improved.
The working principle is as follows: when the system is used, the compressor power calculation module 106 is used for calculating the power of the compressor when the system runs stably in a vapor compression refrigeration cycle, the time from the start of the compressor to the time when system parameters are stable in the air source heat pump system by the start preheating time calculation module 105 is the start preheating time of the air source heat pump system, the refrigerant selection module 104 is used for enabling the air source heat pump to enter the refrigerant of the compressor in a gas-liquid two-phase state in the start stage, part of the refrigerant is still in a liquid state after compression, the system needs to evaporate the part of the liquid refrigerant during preheating, the refrigeration coefficient, the pressure ratio and the compressor exhaust temperature ℃ of the refrigerant are used as selection bases, the refrigerant flow control module 103 is used for controlling the electronic expansion valve in the indoor heat exchanger, the outdoor machine electronic expansion valve and the outdoor side supercooling electronic expansion valve to be opened to the maximum degree in the start stage of the air source heat pump, the indoor heat exchanger water pump control module 102 is used for delaying the opening time of an indoor heat exchanger water pump, avoiding continuously heating a refrigerant, and opening the indoor heat exchanger water pump when the saturation temperature corresponding to the exhaust pressure of a compressor is 0.5-1.5 ℃ higher than the water temperature of the indoor heat exchanger, avoiding the refrigerant in the indoor heat exchanger from evaporating and overheating and reducing the flow of the refrigerant, the air return circulation control module 107 is used for modulating heat circulation of an air source heat pump, gaseous high-temperature and high-pressure refrigerant flowing out of a compressor flows through a four-way valve, enters an evaporator to emit heat and then is condensed into high-temperature and high-pressure liquid, the liquid refrigerant is throttled by a capillary tube and then is programmed into low-temperature and low-pressure refrigerant liquid, enters a condenser to exchange heat with circulating air at the outdoor side, absorbs heat and evaporates into low-temperature and low-pressure gas, the gaseous refrigerant returns to the air suction end of the compressor through the four-way valve of the outdoor unit, and an electric heating ring is installed at the air return pipe section of the four-way valve connected with the compressor, the electric heating ring is sleeved on the surface of the copper pipe and is tightly connected with the copper pipe to increase the heat transfer specific area, the material of the electric heating ring can be selected from heat conductive materials such as a cylinder, aluminum, iron and the like, the air return circulation control module 107 is used for electrifying the electric heating ring to work and heating the pipe in the operation process of the air source heat pump, the electric heating ring directly transfers heat to the copper pipe which is tightly sleeved with the electric heating ring after generating heat, the copper pipe transfers the heat to a refrigerant in the copper pipe after absorbing the heat, the temperature of the refrigerant before entering a compressor is improved, the air return temperature is improved, the installation position of an evaporator coil is required to be arranged on an inlet pipe, an outlet pipe or a bent head of the evaporator according to different types and evaporator flow paths, the electric heating ring control module 108 is used for controlling the operation state of the electric heating ring mainly according to the temperature Tp of the indoor evaporator coil, in the heating stage, when the temperature Tp of the indoor coil is less than or equal to T1 ℃, the electric heating ring works, and when the temperature Tp of the indoor coil is more than or equal to T2 ℃, the electric heating ring stops working, wherein the temperature range ratio of T1 to T2 is as follows: t1 of 9 ℃ and 60 ℃ and T2 of 9 ℃ and 63 ℃ and T1 of 2, wherein the electric heating ring takes a tubular electric heating element as a heating element, the element is bent and formed and enters a die for pouring and forming, 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 air source heat pump indoor unit, if the rotating speed of the indoor fan is lower than a certain given value, the rotating speed of the inner fan is reduced, and if the rotating speed is increased and is higher than a certain given value, the set rotating speed is restored.
The above description is only for the preferred embodiment of the present invention, but the scope of the present invention is not limited thereto, and any person skilled in the art should be able to cover the technical scope of the present invention and the equivalent alternatives or modifications according to the technical solution and the inventive concept of the present invention within the technical scope of the present invention.
Claims (10)
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 starting preheating time calculation module (105), the input end of the starting 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 of cold wind prevents control module (109) and the output electric connection of electric heating circle control module (108), the input of electric heating circle control module (108) and the output electric connection of return air circulation control module (107).
2. The air-source heat pump low-temperature protection system as claimed in claim 1, wherein the compressor power calculation module (106) is used for calculating the power of the compressor when the system operates stably in the vapor compression refrigeration cycle, and the time from the start of the compressor to the time when the system parameters are stable in the air-source heat pump system of the start-up preheating time calculation module (105) is the start-up preheating time of the air-source heat pump system.
3. The air-source heat pump low-temperature protection system as claimed in claim 2, wherein the refrigerant selection module (104) is used for enabling the air-source heat pump to enter the compressor as a refrigerant in a gas-liquid two-phase state in a starting stage, part of the refrigerant 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 compressor discharge temperature ℃ of the refrigerant are used as selection bases.
4. The air-source heat pump low-temperature protection system as claimed in claim 3, wherein the refrigerant flow control module (103) is configured to control the electronic expansion valve in the indoor heat exchanger, the electronic expansion valve for heating in the outdoor unit, and the electronic expansion valve for supercooling on the outdoor side to be opened to the maximum extent during a start-up phase of the air-source heat pump, and the indoor heat exchanger water pump control module (102) is configured to delay an opening time of an indoor heat exchanger water pump to avoid continuous heating of the refrigerant and to be opened again when a saturation temperature corresponding to a discharge pressure of the compressor is 0.5-1.5 ℃ higher than a water temperature of the indoor heat exchanger to avoid evaporation and overheating of the refrigerant in the indoor heat exchanger to reduce a flow rate of the refrigerant.
5. The air-source heat pump low-temperature protection system as claimed in claim 4, wherein the air-return cycle control module (107) is used for air-source heat pump modulation heat cycle, gaseous high-temperature and high-pressure refrigerant flowing out of a compressor flows through a four-way valve, enters an evaporator to release heat and then is condensed into high-temperature and high-pressure liquid, liquid refrigerant is throttled by a capillary tube and then is programmed into low-temperature and low-pressure refrigerant liquid, enters a condenser to perform heat exchange with outdoor circulating air, absorbs heat and evaporates into low-temperature and low-pressure gas.
6. The air-source heat pump low-temperature protection system according to claim 5, wherein the gaseous refrigerant returns to the suction end of the compressor through the four-way valve, an electric heating coil is installed on a copper pipe section of a return pipe of the outdoor unit four-way valve connected with the compressor, the electric heating coil is sleeved on the surface of the copper pipe and is tightly connected with the copper pipe so as to increase the heat transfer ratio area, and the material of the electric heating coil can be selected from heat-conductive materials such as a cylinder, aluminum, iron and the like.
7. The air-source heat pump low-temperature protection system according to claim 6, wherein the air-return circulation control module (107) is used for enabling the electric heating ring to work when the air-source heat pump is in operation and heating the pipeline, the electric heating ring generates heat and then directly transfers the heat to the copper pipeline which is tightly sleeved with the electric heating ring, the copper pipeline absorbs the heat and then transfers the heat to a refrigerant in the copper pipeline, the temperature of the refrigerant before entering the compressor is increased, and the air-return temperature is increased.
8. An air-source heat pump cryogenic protection system of claim 7 wherein the evaporator coil is mounted in the evaporator inlet pipe, outlet pipe or elbow depending on the model and evaporator flow path.
9. An air-source heat pump low-temperature protection system according to claim 8, wherein the electric heating coil control module (108) is used for controlling the operation state of the electric heating coil mainly according to the indoor evaporator coil temperature Tp, the electric heating coil is operated in the heating stage when the indoor coil temperature Tp is less than or equal to T1 ℃, and the electric heating coil is stopped when the indoor coil temperature Tp is greater than or equal to T2 ℃, wherein the temperature range ratio of T1 and T2 is as follows: t1 of more than or equal to 9 ℃ and less than or equal to 60 ℃, T2 of more than or equal to 9 ℃ and less than 63 ℃, and T1 and T2, wherein the electric heating ring takes a tubular electric heating element as a heating element, the element is bent and molded, and the element enters a die for casting and molding.
10. The air-source heat pump low-temperature protection system according to claim 9, wherein the cold air prevention control module (109) is configured to control and adjust the indoor fan speed according to the temperature of the middle portion of the evaporator of the indoor unit of the air source heat pump, decrease the indoor fan speed if the indoor fan speed is lower than a given value, and restore the set speed if the indoor fan speed is higher than the given value.
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