CN111678224A - Air source heat pump - Google Patents

Air source heat pump Download PDF

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Publication number
CN111678224A
CN111678224A CN202010559270.1A CN202010559270A CN111678224A CN 111678224 A CN111678224 A CN 111678224A CN 202010559270 A CN202010559270 A CN 202010559270A CN 111678224 A CN111678224 A CN 111678224A
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China
Prior art keywords
heat exchanger
performance auxiliary
pipeline
outdoor
auxiliary pipeline
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Granted
Application number
CN202010559270.1A
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Chinese (zh)
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CN111678224B (en
Inventor
董辰
张恒
唐亚洲
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Qingdao Hisense Hitachi Air Conditioning System Co Ltd
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Qingdao Hisense Hitachi Air Conditioning System Co Ltd
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Priority to CN202010559270.1A priority Critical patent/CN111678224B/en
Publication of CN111678224A publication Critical patent/CN111678224A/en
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Publication of CN111678224B publication Critical patent/CN111678224B/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F24F5/001—Compression cycle type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing
    • F24F11/42—Defrosting; Preventing freezing of outdoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/50—Control or safety arrangements characterised by user interfaces or communication
    • F24F11/61—Control or safety arrangements characterised by user interfaces or communication using timers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/64—Electronic processing using pre-stored data
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/65—Electronic processing for selecting an operating mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/22—Means for preventing condensation or evacuating condensate
    • F24F13/222—Means for preventing condensation or evacuating condensate for evacuating condensate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30—Arrangement or mounting of heat-exchangers
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F24F2110/12—Temperature of the outside air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/20—Heat-exchange fluid temperature

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Signal Processing (AREA)
  • Fuzzy Systems (AREA)
  • Mathematical Physics (AREA)
  • Thermal Sciences (AREA)
  • Human Computer Interaction (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

The invention discloses an air source heat pump.A heat exchange loop is connected with a performance auxiliary pipeline in series, and the performance auxiliary pipeline is connected with a bypass pipeline in parallel. One end of the performance auxiliary pipeline is connected with the indoor heat exchanger, the other end of the performance auxiliary pipeline is connected with the outdoor heat exchanger, and the performance auxiliary pipeline is arranged at the bottom of the outdoor heat exchanger. The bypass pipeline is provided with a control valve. When heating, the control valve is opened, one part of the heat exchange medium flowing out of the indoor heat exchanger flows through the performance auxiliary pipeline, the other part of the heat exchange medium flows through the bypass pipeline, and the two paths of heat exchange medium flow into the outdoor heat exchanger together after converging. When refrigerating, the control valve is closed, and all the heat exchange medium flowing out of the outdoor heat exchanger flows to the indoor heat exchanger through the performance auxiliary pipeline. The arrangement of the performance auxiliary pipeline and the bypass pipeline can improve the supercooling degree during refrigeration and improve the refrigeration capacity of the air source heat pump; when heating, the frosting and freezing at the bottom of the outdoor heat exchanger can be prevented, meanwhile, the heat waste is reduced, and the heating capacity and the energy efficiency of the air source heat pump are improved.

Description

Air source heat pump
Technical Field
The invention relates to the technical field of air conditioning equipment, in particular to an air source heat pump.
Background
An air source heat pump is an energy-saving device which utilizes high-level energy to enable heat to flow from low-level heat source air to a high-level heat source. An air source heat pump is a form of heat pump, and as the name suggests, a heat pump can convert low-level heat energy (such as heat contained in air, soil and water) which cannot be directly utilized into high-level heat energy which can be utilized, so that the aim of saving part of high-level energy (such as coal, gas, oil, electric energy and the like) is fulfilled.
When the air source heat pump is applied, when the temperature and the humidity of the environment reach certain conditions, the air side of the outdoor heat exchanger can be frosted. However, the wind field on the surface of the outdoor heat exchanger is not uniformly distributed, and the wind speed is gradually reduced from top to bottom in the vertical direction. Under the frosting working condition, the lower heat exchanger has low air speed and poor heat exchange effect, so that the lower heat exchanger frosts firstly and the frosting amount is large. Meanwhile, the refrigerant flow required by the lower heat exchanger is small, and the matched flow dividing capillary tube is long, so that the refrigerant flow distributed during defrosting is small, and the defrosting speed is slow. In addition, the defrosting water at the upper part of the outdoor heat exchanger is easy to accumulate at the lower part of the heat exchanger, and the defrosting water quickly frosts or even freezes after the next heating period begins, so that the problems of heat exchange capacity reduction of the heat exchanger, liquid impact of a compressor and the like are caused. In the prior art, an electric heating element is generally added to achieve the anti-freezing effect of the bottom of the heat exchanger.
In addition, in a multi-split system with long on-line piping, if the refrigerant at the outlet of the outdoor heat exchanger does not have enough supercooling degree, certain evaporation is generated due to pressure drop loss of a pipeline, so that the refrigerant is in a two-phase state in front of the indoor throttling element, the reliability of the throttling element is influenced on one hand, and the dryness of the refrigerant at the inlet of the indoor heat exchanger is increased on the other hand, so that the refrigerating performance of the system is reduced.
Disclosure of Invention
In some embodiments of the present application, there is provided an air source heat pump comprising: the heat exchange loop comprises a compressor, an indoor heat exchanger, an outdoor heat exchanger and a throttling element; the air-source heat pump further comprises: the performance auxiliary pipeline is connected in series on the heat exchange loop, one end of the performance auxiliary pipeline is connected with the indoor heat exchanger, the other end of the performance auxiliary pipeline is connected with the outdoor heat exchanger, and the performance auxiliary pipeline is arranged at the bottom of the outdoor heat exchanger; the bypass pipeline is connected with the performance auxiliary pipeline in parallel, and a control valve is arranged on the bypass pipeline; when heating, the control valve is opened, part of the heat exchange medium flowing out of the indoor heat exchanger flows through the performance auxiliary pipeline, the other part of the heat exchange medium flows through the bypass pipeline, and the heat exchange medium flowing out of the performance auxiliary pipeline and the bypass pipeline are converged and then flow to the outdoor heat exchanger together; and during refrigeration, the control valve is closed, and all the heat exchange medium flowing out of the outdoor heat exchanger flows to the indoor heat exchanger through the performance auxiliary pipeline.
When the heat exchanger is used for heating, the evaporation temperature of the refrigerant in the performance auxiliary pipeline is controlled, and when the evaporation temperature of the refrigerant in the performance auxiliary pipeline is higher than the wet bulb temperature of the outdoor environment, the bottom of the heat exchanger can be prevented from frosting, and the effect of preventing frosting is achieved.
Meanwhile, the bypass pipeline is arranged, so that only a part of the refrigerant flows into the performance auxiliary pipeline to be condensed and released so as to prevent the bottom of the heat exchanger from frosting and freezing, and the other part of the refrigerant directly flows to the outdoor heat exchanger from the bypass pipeline, so that the heat of the refrigerant which is dissipated to the external environment through the performance auxiliary pipeline is reduced, and the purpose of reducing heat waste is achieved.
During refrigeration, the medium-temperature high-pressure liquid refrigerant is converged by the main heat exchange pipeline (the number of pipelines is more) and flows into the performance auxiliary pipeline (the number of pipelines is less), so that the flow rate of the refrigerant is increased due to the reduction of the flow path, the heat exchange efficiency is increased, the refrigerant is further cooled by the performance auxiliary pipeline, the supercooling degree is improved, and the refrigeration capacity is improved.
In some embodiments of the present application, the performance auxiliary line has a plurality of performance auxiliary lines connected in parallel, and a plurality of performance auxiliary lines are disposed at the bottom of the windward side of the outdoor heat exchanger.
In some embodiments of the present application, the performance auxiliary pipeline has a plurality of performance auxiliary pipelines connected in series, and a plurality of performance auxiliary pipelines are disposed at the bottom of the windward side of the outdoor heat exchanger.
In some embodiments of the present application, the number of performance auxiliary lines is a non-zero even number.
In this embodiment, the number of the performance auxiliary pipelines is 4.
In some embodiments of the present application, the throttling element comprises an indoor throttling element and an outdoor throttling element; the indoor throttling element is arranged between the indoor heat exchanger and the performance auxiliary pipeline, and the indoor throttling element is connected with the bypass pipeline in series; the outdoor throttling element is arranged between the outdoor heat exchanger and the performance auxiliary pipeline, and the outdoor throttling element is connected with the bypass pipeline in series.
In some embodiments of the present application, a flow divider is disposed between the outdoor heat exchanger and the outdoor throttling element, and a flow dividing capillary tube is disposed between the outdoor heat exchanger and the compressor.
In some embodiments of the present application, a temperature sensor is disposed at an end of the performance auxiliary line near the outdoor throttling element.
In some embodiments of the present application, the control valve is a check valve/solenoid valve/electronic expansion valve.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings needed to be used in the description of the embodiments are briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without creative efforts.
Fig. 1 is a schematic view illustrating an operation principle of an air source heat pump when heating according to an embodiment;
FIG. 2 is a schematic diagram illustrating the operation principle of the air source heat pump in refrigeration according to the embodiment;
FIG. 3 is a schematic diagram of a performance aid line arrangement according to an embodiment;
FIG. 4 is a schematic diagram of a performance auxiliary line arrangement according to another embodiment;
fig. 5 is a control flowchart in heating of the air source heat pump according to the embodiment.
Reference numerals:
01-compressor, 02-four-way reversing valve, 03-shunt capillary tube, 04-main heat exchange pipeline of outdoor heat exchanger, 05-shunt, 06-outdoor throttling element, 07-performance auxiliary pipeline, 08-liquid side stop valve, 09-indoor throttling element, 10-indoor heat exchanger, 11-gas side stop valve, 12-gas-liquid separator, 13-control valve, 14-bypass pipeline and 15-temperature sensor.
Detailed Description
The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are only a part of the embodiments of the present application, 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 application.
In the description of the present application, it is to be understood that the terms "front", "back", "top", "bottom", "inner", "outer", and the like, indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are only for convenience in describing the present application and simplifying the description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present application.
In the description of the present application, it is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meaning of the above terms in the present application can be understood in a specific case by those of ordinary skill in the art.
[ operating principle of air Source Heat Pump ]
The heat exchange loop of the air source heat pump mainly comprises a compressor 01, a gas-liquid separator 12, an indoor heat exchanger 10, an outdoor heat exchanger, a throttling element and the like, wherein the throttling element comprises an indoor throttling element 09 and an outdoor throttling element 06.
When the air source heat pump is in a heating mode, referring to fig. 1, the compressor 01 is started, high-temperature and high-pressure refrigerant vapor is discharged from a discharge port of the compressor 01, passes through the gas-liquid separator 12, enters the indoor heat exchanger 10 through the four-way reversing valve 02 to perform heat exchange, releases heat, turns into medium-temperature and high-pressure refrigerant liquid, is subjected to pressure reduction by the indoor throttling element 09 to turn into a low-temperature and low-pressure gas-liquid two-phase mixture, enters the main heat exchange pipeline 04 of the outdoor heat exchanger to be evaporated and absorbed to turn into low-temperature and low-pressure refrigerant vapor, then enters the gas-liquid separator 12 through the four-way reversing valve 02, and flows back to.
When the air source heat pump is in the cooling mode, referring to fig. 2, the flow direction of the refrigerant cycle is just opposite to that in the heating mode, and the description is omitted.
[ Performance auxiliary line, bypass line ]
A performance auxiliary pipeline 07 is connected in series on the heat exchange loop, one end of the performance auxiliary pipeline 07 is connected with the indoor heat exchanger 10, the other end of the performance auxiliary pipeline is connected with the outdoor heat exchanger, and the performance auxiliary pipeline is arranged at the bottom of the outdoor heat exchanger.
A bypass pipeline 14 is further arranged on the heat exchange loop and connected with the performance auxiliary pipeline 07 in parallel, and a control valve 13 is arranged on the bypass pipeline 14.
Referring to fig. 1, in heating, the control valve 13 is opened, a part of the heat exchange medium (refrigerant) flowing out of the indoor heat exchanger 10 flows through the performance auxiliary line 07, another part flows through the bypass line 14, and the refrigerants flowing out of the performance auxiliary line 07 and the bypass line 14 are merged and then flow to the main heat exchange line 04 of the outdoor heat exchanger.
Specifically, the four-way reversing valve 02 is ON, the air source heat pump performs a heating cycle, and the flow directions of the refrigerants are as follows in sequence: a) a high-temperature and high-pressure gaseous refrigerant discharged from the compressor 01 enters the indoor heat exchanger 10 through the four-way reversing valve 02 and the gas-side stop valve 11 and is condensed into a medium-temperature and high-pressure liquid refrigerant; b) the liquid refrigerant flows out of the indoor throttling element 09, passes through the liquid side stop valve 08 and is divided in front of the performance auxiliary pipeline 07; c) a part of the refrigerant enters the performance auxiliary pipeline 07 to emit heat for further condensation, the high temperature at the bottom of the outdoor heat exchanger is kept, and a part of the refrigerant passes through a bypass pipeline 14; d) the two paths of refrigerants are converged in front of the outdoor throttling element 06 and enter a main heat exchange pipeline 04 of the outdoor heat exchanger to be evaporated into a low-pressure gaseous refrigerant; e) the low-pressure gaseous refrigerant flows into the gas-liquid separator 12 through the four-way reversing valve 02 and is sucked into the suction end of the compressor 01, and the whole heating cycle is completed.
The bypass pipeline 14 is arranged so that only a part of the refrigerant flows into the performance auxiliary pipeline 07 for condensation and heat release to prevent frosting and frost-proof at the bottom of the outdoor heat exchanger, and the other part of the refrigerant directly flows to the outdoor heat exchanger from the bypass pipeline 14, so that the heat of the refrigerant emitted to the external environment through the performance auxiliary pipeline 07 is reduced, and the purpose of reducing heat waste is achieved.
Referring to fig. 2, during cooling, the control valve 13 is closed, and all of the refrigerant flowing out of the outdoor heat exchanger flows to the indoor heat exchanger 10 through the performance auxiliary line 07.
Specifically, the four-way selector valve 02 is OFF, the air source heat pump performs a refrigeration cycle, and the refrigerant flows in the following order: a) high-temperature and high-pressure gaseous refrigerant discharged by the compressor 01 enters a main heat exchange pipeline 04 of the outdoor heat exchanger through a four-way reversing valve 02; b) the refrigerant discharges heat in the main pipe line 04 of the outdoor heat exchanger, is cooled and condensed into a liquid refrigerant with medium temperature and high pressure; c) liquid refrigerants of all pipelines are converged and flow out of the outdoor throttling element 06, and due to the blocking of the bypass control valve 13, the refrigerants cannot pass through the bypass pipeline 14 and all enter the performance auxiliary pipeline 07; d) the refrigerant further releases heat and condenses in the performance auxiliary pipeline 07 and then enters the indoor unit; e) the liquid refrigerant with medium temperature and high pressure enters the indoor heat exchanger 10 to be evaporated into a low-temperature and low-pressure gaseous refrigerant; f) the low-temperature and low-pressure gaseous refrigerant flows into the gas-liquid separator 12 through the gas-side stop valve 11 and the four-way reversing valve 02 and is sucked into the suction end of the compressor 01, and the whole refrigeration cycle is completed.
During refrigeration, the medium-temperature high-pressure liquid refrigerant is converged by the main heat exchange pipeline 04 (the number of pipelines is large) of the outdoor heat exchanger and flows into the performance auxiliary pipeline 07 (the number of pipelines is small), the flow path is reduced, so that the flow speed of the refrigerant is increased, the heat exchange efficiency is increased, the refrigerant is further cooled in the performance auxiliary pipeline 07, the supercooling degree is improved, and the refrigeration capacity is improved.
The direction of the refrigerant is the same as the refrigeration working condition during defrosting, and the description is omitted.
The defrosting water produced during defrosting operation flows out through a water receiving disc (not shown), but when the outdoor environment temperature is lower (< 0 ℃), the water freezes without completely flowing out, and the ice layer gradually thickens along with the increase of the defrosting times, so that fins of the outdoor heat exchanger are blocked, the normal heat exchange of the heat exchanger is affected, the system capacity is reduced, and even system faults can occur. The performance auxiliary pipe 07 can prevent the water generated by melting the upper frost layer from freezing at the lower part during defrosting, and further prevent the ice layer from accumulating along with the increase of the defrosting times.
In the application, due to the arrangement of the performance auxiliary pipeline 07 and the bypass pipeline 14, the supercooling degree can be improved during refrigeration, and the refrigeration capacity of the air source heat pump is improved; when heating, the frosting and freezing at the bottom of the outdoor heat exchanger can be prevented, meanwhile, the heat waste is reduced, and the heating capacity and the energy efficiency of the air source heat pump are improved.
The performance auxiliary line 07 in this application has two arrangements.
First, referring to fig. 3, a plurality of performance auxiliary pipelines 07 are provided, a plurality of performance auxiliary pipelines 07 are connected in parallel, and the plurality of performance auxiliary pipelines 07 are provided at the bottom of the windward side R1 row of the outdoor heat exchanger.
Second, referring to fig. 4, a plurality of performance auxiliary pipelines 07 are provided, a plurality of performance auxiliary pipelines 07 are connected in series, and a plurality of performance auxiliary pipelines 07 are provided at the bottom of the windward side R1 row of the outdoor heat exchanger.
When the air source heat pump heats, outdoor air is heated after passing through the performance auxiliary pipeline 07, the temperature of the air is increased, the heat exchange temperature difference between refrigerant and the air in the main heat exchange pipeline 04 in the rear row (namely R2 and R3) of the performance auxiliary pipeline 07 is increased, the refrigerant evaporates and absorbs heat to recover part of heat, and the heat loss of the part of heat is further reduced.
The performance auxiliary pipeline 07 is arranged at the bottom of the windward side, so that heat waste can be reduced to the maximum extent, and the optimal anti-freezing and anti-frosting effects can be realized.
(1) While the outdoor heat exchanger is expected to absorb heat from the air side during heating, the performance auxiliary pipeline 07 releases heat during heating (for frost prevention and freeze prevention), so that heat is wasted. If the performance auxiliary pipeline 07 is placed on the outermost side, air is heated by heat emitted by the performance auxiliary pipeline 07 when passing through the performance auxiliary pipeline 07, and then the heated air is absorbed by a part of heat when passing through a main heat exchange pipeline (namely R2 and R3 rows) on the inner side of the performance auxiliary pipeline 07, which is equivalent to heat recovery, so that the waste of heat is reduced, and the work of the compressor is also reduced;
(2) after the performance auxiliary line 07 is placed at the outermost side to heat the air, the temperature of the air is increased and the relative humidity is lowered, so that the main heat exchange line (i.e., rows R2 and R3) at the inner side of the performance auxiliary line 07 cannot frost, and if the performance auxiliary line is placed at row R2 or row R3, the outer heat exchange line cannot be guaranteed to frost. The number of the performance auxiliary pipelines 07 needs to comprehensively consider pressure loss of the refrigerant generated in the performance auxiliary pipelines 07 during refrigeration and heat dissipation loss during heating. The number of performance auxiliary pipelines 07 in this embodiment is an even number other than zero, and is set to 4 in this embodiment, and fig. 3 and 4 illustrate the example of 4 pipelines.
With continued reference to fig. 1, the throttling elements include an indoor throttling element 09 and an outdoor throttling element 06.
The indoor throttling element 09 is arranged between the indoor heat exchanger 10 and the performance auxiliary pipeline 07, and the indoor throttling element 09 is simultaneously connected with the bypass pipeline 14 in series. The outdoor throttling element 06 is arranged between the main heat exchange pipeline 04 of the outdoor heat exchanger and the performance auxiliary pipeline 07, and is simultaneously connected with the bypass pipeline 14 in series.
During heating, the medium-temperature high-pressure liquid refrigerant flowing out of the indoor heat exchanger 10 flows to the liquid side stop valve 08 through the indoor throttling element 09, and two paths of refrigerant flowing out of the performance auxiliary pipeline 07 and the bypass pipeline 14 are converged in front of the outdoor throttling element 06, throttled to a low-pressure two-phase state through the outdoor throttling element 06, and then enter the main heat exchange pipeline 04 of the outdoor heat exchanger.
The refrigerant from the indoor side passes through the performance auxiliary pipeline 07 and then is evaporated through the outdoor throttling element 06, the refrigerant in the performance auxiliary pipeline 07 is in a medium-temperature high-pressure state, heat is further released in the performance auxiliary pipeline 07, the performance auxiliary pipeline 07 is enabled to keep a high temperature (higher than 0 ℃) all the time, and the bottom of the heat exchanger can be guaranteed not to frost when the heat exchanger is used for heating in an environment with the outdoor environment temperature lower than 0 ℃.
During refrigeration, the refrigerant flowing out of the outdoor heat exchanger flows to the performance auxiliary pipeline 07 through the outdoor throttling element 06, and the medium-temperature high-pressure liquid refrigerant flowing out of the performance auxiliary pipeline 07 enters the indoor heat exchanger 10 after being throttled by the indoor throttling element 09.
With continued reference to fig. 1, a flow divider 05 is provided between the main heat exchange pipeline 04 of the outdoor heat exchanger and the outdoor throttling element 06, and a flow dividing capillary tube 03 is provided between the main heat exchange pipeline 04 of the outdoor heat exchanger and the compressor 01.
In some embodiments of the present application, a temperature sensor 15 is disposed at one end of the performance auxiliary pipeline 07 close to the outdoor throttling element 06, so as to monitor the temperature Tx at the outlet of the performance auxiliary pipeline 07 in real time under the heating condition, and control the outlet refrigerant temperature Tx of the performance auxiliary pipeline 07 under the heating condition to be kept within a set temperature range (a, b), so as to ensure that the bottom of the outdoor heat exchanger does not frost or freeze.
In some embodiments of the present application, the control valve 13 is a check valve/solenoid valve/electronic expansion valve, and the control valve 13 shown in fig. 1 and 2 is an electronic expansion valve.
When the control valve 13 adopts the electronic expansion valve, the flow of the refrigerant passing through the bypass pipeline 14 is accurately adjusted according to different working condition environments by controlling the opening degree of the electronic expansion valve, so that the heat dissipation loss of the refrigerant in the performance auxiliary pipeline 07 under the heating working condition can be reduced while the bottom of the outdoor heat exchanger is prevented from frosting, the heat waste is reduced, and the heating capacity of the air source heat pump is improved.
In the following, a control method for heating by the air source heat pump will be described in detail, and referring to fig. 5, the control valve 13 is an electronic expansion valve.
(1) After the heating operation of the system is started, setting an initial opening degree of an electronic expansion valve (namely, a control valve 13) EVS on a bypass pipeline 14;
(2) periodically detecting the temperature Tx of an outlet refrigerant of the performance auxiliary pipeline 07;
(3) judging whether Tx is more than or equal to b ℃, if so, executing (4); if not, executing (7);
(4) judging whether EVS (n) +. DELTA.EVS < EVSmax, wherein EVS (n) represents the current opening degree of the expansion valve, DELTA.EVS represents the unit variation of the opening degree of the expansion valve, and EVSmax represents the maximum value of the opening degree of the expansion valve;
if yes, executing (5); if not, executing (6);
(5) controlling the opening degree of the expansion valve to: EVS (n +1) = EVS (n) +. EVS, and then (2) is re-executed after the next cycle;
(6) controlling the opening degree of the expansion valve to: EVS (n +1) = EVSmax, and then (2) is re-executed after the next cycle;
(7) judging whether Tx is less than or equal to a ℃, if so, executing (8); if not, re-executing the step (2) after the next period;
(8) judging whether EVS (n) -delta EVS is larger than EVSmin or not, wherein EVSmin represents the minimum value of the opening of the expansion valve, and specifically can be in a closed state, namely the opening is zero;
if yes, executing (9); if not, executing (10);
(9) controlling the opening degree of the expansion valve to: EVS (n +1) = EVS (n) - Δ EVS, and then (2) is re-executed after the next cycle;
(10) controlling the opening degree of the expansion valve to: EVS (n +1) = EVSmin, and then (2) is re-executed after the next cycle.
In the foregoing description of embodiments, the particular features, structures, materials, or characteristics may be combined in any suitable manner in any one or more embodiments or examples.
The above description is only for the specific embodiments of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that can be easily conceived by those skilled in the art within the technical scope of the present invention are included in the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the claims.

Claims (9)

1. An air-source heat pump comprising:
the heat exchange loop comprises a compressor, an indoor heat exchanger, an outdoor heat exchanger and a throttling element;
characterized in that, the air source heat pump still includes:
the performance auxiliary pipeline is connected in series on the heat exchange loop, one end of the performance auxiliary pipeline is connected with the indoor heat exchanger, the other end of the performance auxiliary pipeline is connected with the outdoor heat exchanger, and the performance auxiliary pipeline is arranged at the bottom of the outdoor heat exchanger;
the bypass pipeline is connected with the performance auxiliary pipeline in parallel, and a control valve is arranged on the bypass pipeline;
when heating, the control valve is opened, part of the heat exchange medium flowing out of the indoor heat exchanger flows through the performance auxiliary pipeline, the other part of the heat exchange medium flows through the bypass pipeline, and the heat exchange medium flowing out of the performance auxiliary pipeline and the bypass pipeline are converged and then flow to the outdoor heat exchanger together;
and during refrigeration, the control valve is closed, and all the heat exchange medium flowing out of the outdoor heat exchanger flows to the indoor heat exchanger through the performance auxiliary pipeline.
2. The air-source heat pump of claim 1,
the performance auxiliary pipelines are connected in parallel and are arranged at the bottom of the windward side of the outdoor heat exchanger.
3. The air-source heat pump of claim 1,
the performance auxiliary pipelines are connected in series and are arranged at the bottom of the windward side of the outdoor heat exchanger.
4. Air source heat pump according to claim 2 or 3,
the number of performance auxiliary pipelines is a non-zero even number.
5. The air source heat pump according to claim 4,
the number of the performance auxiliary pipelines is 4.
6. The air-source heat pump of claim 1,
the throttling element comprises an indoor throttling element and an outdoor throttling element;
the indoor throttling element is arranged between the indoor heat exchanger and the performance auxiliary pipeline, and the indoor throttling element is connected with the bypass pipeline in series;
the outdoor throttling element is arranged between the outdoor heat exchanger and the performance auxiliary pipeline, and the outdoor throttling element is connected with the bypass pipeline in series.
7. The air-source heat pump of claim 6,
a shunt is arranged between the outdoor heat exchanger and the outdoor throttling element, and a shunt capillary tube is arranged between the outdoor heat exchanger and the compressor.
8. The air-source heat pump of claim 1,
and a temperature sensor is arranged at one end of the performance auxiliary pipeline close to the outdoor throttling element.
9. The air-source heat pump of claim 1,
the control valve is a one-way valve/a solenoid valve/an electronic expansion valve.
CN202010559270.1A 2020-06-18 2020-06-18 Air source heat pump Active CN111678224B (en)

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CN115307348A (en) * 2022-08-04 2022-11-08 国网陕西省电力有限公司电力科学研究院 Reverse-cycle defrosting air source heat pump system and control method thereof

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