CN117940706A - Air source heat pump system - Google Patents

Air source heat pump system Download PDF

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Publication number
CN117940706A
CN117940706A CN202280061663.7A CN202280061663A CN117940706A CN 117940706 A CN117940706 A CN 117940706A CN 202280061663 A CN202280061663 A CN 202280061663A CN 117940706 A CN117940706 A CN 117940706A
Authority
CN
China
Prior art keywords
water
port
way valve
heat exchanger
compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202280061663.7A
Other languages
Chinese (zh)
Inventor
李东哲
潘翠连
管清杭
陈卫星
宋振兴
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Qingdao Hisense Hitachi Air Conditioning System Co Ltd
Original Assignee
Qingdao Hisense Hitachi Air Conditioning System Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Qingdao Hisense Hitachi Air Conditioning System Co Ltd filed Critical Qingdao Hisense Hitachi Air Conditioning System Co Ltd
Priority claimed from PCT/CN2022/136619 external-priority patent/WO2023103968A1/en
Publication of CN117940706A publication Critical patent/CN117940706A/en
Pending legal-status Critical Current

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Classifications

    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating arrangements
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • 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)
  • Air Conditioning Control Device (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Abstract

The utility model provides an air source heat pump system, air source heat pump system include compressor, water side heat exchanger, air side heat exchanger, cross valve, check valve, electronic expansion valve, off-premises station automatically controlled board. The compressor includes a discharge port and a return port. The air side heat exchanger is connected with the water side heat exchanger. Four ports of the four-way valve are respectively connected with an exhaust port of the compressor, a return port of the compressor, the water side heat exchanger and the air side heat exchanger. The one-way valve is connected between the exhaust port of the compressor and the four-way valve, and the compressor is connected to the four-way valve in one way. The electronic expansion valve is connected between the air side heat exchanger and the water side heat exchanger. The outdoor unit electric control board is connected with the compressor and the electronic expansion valve and is configured to: when a shutdown signal is received, the electronic expansion valve is closed and the compressor is controlled to remain on. When it is determined that the shutdown condition is satisfied, the compressor is shut down.

Description

Air source heat pump system
The present application claims priority from chinese patent application number 202123050748.7, 2021, 12, 7, 202210642290.4, 2022, 6, 8, and the entire contents of which are incorporated herein by reference.
Technical Field
The disclosure relates to the technical field of household appliances, in particular to an air source heat pump system.
Background
The air source heat pump comprises an air source heat pump unit and indoor terminal equipment, and the air source heat pump unit comprises an outdoor unit and a water side heat exchanger connected with the outdoor unit. The refrigerant side of the water side heat exchanger receives cold and heat produced by the outdoor unit and transmits the cold and heat to the water outlet side, and the water outlet side of the water side heat exchanger supplies circulating cold and hot water to indoor terminal equipment through a waterway circulating pipeline. The indoor terminal equipment comprises a fan coil (called a fan disc for short), a floor heating coil (called a floor heating coil for short), a radiator, a living water tank and the like.
Disclosure of Invention
The utility model provides an air source heat pump system, air source heat pump system includes compressor, water side heat exchanger, air side heat exchanger, cross valve, check valve, electronic expansion valve, off-premises station automatically controlled board. The compressor includes a discharge port and a return port. The air side heat exchanger is connected with the water side heat exchanger. Four ports of the four-way valve are respectively connected with an exhaust port of the compressor, a return port of the compressor, the water side heat exchanger and the air side heat exchanger. The one-way valve is connected between the exhaust port of the compressor and the four-way valve, and the compressor is in one-way conduction with the four-way valve. The electronic expansion valve is connected between the air side heat exchanger and the water side heat exchanger. The outdoor unit electric control board is connected with the compressor and the electronic expansion valve and is configured to: when a shutdown signal is received, the electronic expansion valve is closed and the compressor is controlled to remain on. When it is determined that a shutdown condition is satisfied, the compressor is shut down.
Drawings
In order to more clearly illustrate the technical solutions of the present disclosure, the drawings that need to be used in some embodiments of the present disclosure will be briefly described below, and it is apparent that the drawings in the following description are only drawings of some embodiments of the present disclosure, and other drawings may be obtained according to these drawings to those of ordinary skill in the art. Furthermore, the drawings in the following description may be regarded as schematic diagrams, not limiting the actual size of the products, the actual flow of the methods, the actual timing of the signals, etc. according to the embodiments of the present disclosure.
FIG. 1 is a block diagram of an air source heat pump system according to some embodiments;
FIG. 2 is a block diagram of a relay reversing device of an air source heat pump system showing a straight-through flow direction, according to some embodiments;
FIG. 3 is a block diagram of a relay reversing device of an air source heat pump system showing bypass flow according to some embodiments;
FIG. 4 is a block diagram of an outdoor unit and a water side heat exchanger of an air source heat pump system according to some embodiments;
FIG. 5 is a schematic diagram of a refrigerant cycle during a cooling operation of an air source heat pump system according to some embodiments;
FIG. 6 is a schematic diagram of a refrigerant cycle during heating operation of an air source heat pump system according to some embodiments;
FIG. 7 is a control schematic timing diagram of an air source heat pump system according to some embodiments;
FIG. 8 is a control schematic timing diagram of another air source heat pump system according to some embodiments;
FIG. 9 is a block diagram of an auxiliary reservoir pipe section in an air source heat pump system according to some embodiments;
FIG. 10 is a control schematic flow diagram of an air source heat pump system according to some embodiments;
FIG. 11 is a flow chart of a method of determining the internal volume of an auxiliary reservoir pipe section in an air source heat pump system according to some embodiments;
FIG. 12 is a flow chart of a method of determining the internal volume of another auxiliary reservoir pipe section in an air source heat pump system according to some embodiments;
fig. 13 is a block diagram of an air source heat pump system according to some embodiments.
In the drawings:
101-an outdoor unit; 11-a compressor; 110-exhaust port; 111-a return air port; 12-a four-way valve; 13-an outdoor unit electric control board; 14-an air side heat exchanger; 15-a one-way valve; 16-an auxiliary liquid storage pipe section; 17-an electronic expansion valve; 18-a fan; 19-high pressure switch; 20-a low pressure switch;
102-a water side heat exchanger; 1021-a first refrigerant port; 1022-a second refrigerant port; OUT-heat pump water supply mouth; IN-heat pump return water port;
205-indoor end equipment; 2051-a domestic hot water tank; 2050-space heating/cooling device; 2052-wind disc; 2053-floor heating;
201-a relay reversing device; a' -a second water inlet; b' -a fourth water outlet; c' -second water return port; d' -a third water outlet; 210-a first straight-through branch; 220-a first bypass branch; 221-a first bypass branch; 222-a second bypass branch; 230-a second through leg; 240-a second bypass branch; 241-a third bypass branch; 242-a fourth bypass branch; 2011-a first electric three-way valve; 2012-a second electric three-way valve; 2013-a third electric three-way valve; 2014-a fourth electric three-way valve; 2015-first booster pump; 2016-second booster pump; 203-a fifth electric three-way valve; 204-a sixth electric three-way valve; p1-a first port; p2-second port; p3-third port;
202-a buffer water tank; a-a first water inlet; b-a first water outlet; c-a first water return port; d-a second water outlet.
Detailed Description
The following description of the embodiments of the present disclosure will be made clearly and fully with reference to the accompanying drawings, in which it is evident that the embodiments described are only some, but not all, of the embodiments of the present disclosure. All other embodiments obtained by one of ordinary skill in the art based on the embodiments provided by the present disclosure are within the scope of the present disclosure.
Throughout the specification and claims, unless the context requires otherwise, the word "comprise" and its other forms such as the third person referring to the singular form "comprise" and the present word "comprising" are to be construed as open, inclusive meaning, i.e. as "comprising, but not limited to. In the description of the specification, the terms "one embodiment", "some embodiments (some embodiments)", "exemplary embodiment (exemplary embodiments)", "example (example)", "specific example (some examples)", etc. are intended to indicate that a particular feature, structure, material, or characteristic associated with the embodiment or example is included in at least one embodiment or example of the present disclosure. The schematic representations of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics may be combined in any suitable manner in any one or more embodiments or examples.
The terms "first" and "second" are used below for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the embodiments of the present disclosure, unless otherwise indicated, the meaning of "a plurality" is two or more.
In describing some embodiments, expressions of "coupled" and "connected" and their derivatives may be used. The term "coupled" is to be interpreted broadly, as referring to, for example, a fixed connection, a removable connection, or a combination thereof; can be directly connected or indirectly connected through an intermediate medium. For example, the term "connected" may be used in describing some embodiments to indicate that two or more elements are in direct physical or electrical contact with each other. As another example, the term "coupled" may be used in describing some embodiments to indicate that two or more elements are in direct physical or electrical contact. However, the term "coupled" or "communicatively coupled (communicatively coupled)" may also mean that two or more elements are not in direct contact with each other, but yet still cooperate or interact with each other. The embodiments disclosed herein are not necessarily limited to the disclosure herein.
At least one of "A, B and C" has the same meaning as at least one of "A, B or C" and includes the following combinations of A, B and C: a alone, B alone, C alone, a combination of a and B, a combination of a and C, a combination of B and C, and a combination of A, B and C.
"A and/or B" includes the following three combinations: only a, only B, and combinations of a and B.
As used herein, the term "if" is optionally interpreted to mean "when … …" or "at … …" or "in response to a determination" or "in response to detection" depending on the context. Similarly, the phrase "if determined … …" or "if a [ stated condition or event ] is detected" is optionally interpreted to mean "upon determination … …" or "in response to determination … …" or "upon detection of a [ stated condition or event ]" or "in response to detection of a [ stated condition or event ], depending on the context.
The use of "adapted" or "configured to" herein is meant to be an open and inclusive language that does not exclude devices adapted or configured to perform additional tasks or steps.
In addition, the use of "based on" is intended to be open and inclusive in that a process, step, calculation, or other action "based on" one or more of the stated conditions or values may be based on additional conditions or beyond the stated values in practice.
As used herein, "about," "approximately" or "approximately" includes the stated values as well as average values within an acceptable deviation range of the particular values as determined by one of ordinary skill in the art in view of the measurement in question and the errors associated with the measurement of the particular quantity (i.e., limitations of the measurement system).
As used herein, "parallel", "perpendicular", "equal" includes the stated case as well as the case that approximates the stated case, the range of which is within an acceptable deviation range as determined by one of ordinary skill in the art taking into account the measurement in question and the errors associated with the measurement of the particular quantity (i.e., limitations of the measurement system). For example, "parallel" includes absolute parallel and approximately parallel, where the acceptable deviation range for approximately parallel may be, for example, a deviation within 5 °; "vertical" includes absolute vertical and near vertical, where the acceptable deviation range for near vertical may also be deviations within 5 °, for example. "equal" includes absolute equal and approximately equal, where the difference between the two, which may be equal, for example, is less than or equal to 5% of either of them within an acceptable deviation of approximately equal.
Fig. 1 is a block diagram of an air source heat pump system according to some embodiments. As shown in fig. 1, the air source heat pump system includes an outdoor unit 101, a water side heat exchanger 102, and an indoor terminal device 205, wherein the water side heat exchanger 102 is connected to the outdoor unit 101 and the indoor terminal device 205. Illustratively, the water-side heat exchanger 102 is connected to a refrigerant line of the outdoor unit 101 by piping, and is connected to the indoor-end device 205 by a water circulation line. The present disclosure is not limited to the number of indoor end devices 205, which may be one or more, and fig. 1 shows 3 indoor end devices 205.
In some embodiments, the outdoor unit 101 and the water side heat exchanger 102 may be designed as separate units, or the water side heat exchanger 102 may be integrated into the outdoor unit 101.
Fig. 4 is a block diagram of an outdoor unit and a water side heat exchanger of an air source heat pump system according to some embodiments. As shown in fig. 4, the outdoor unit 101 includes a compressor 11, a four-way valve 12, an air-side heat exchanger 14, and an electronic expansion valve 17. The compressor 11 includes an exhaust port 110 and a return port 111, and the exhaust port 110, the return port 111, the water side heat exchanger 102 and the air side heat exchanger 14 of the compressor 11 are respectively connected with four ports of the four-way valve 12 through communication pipelines. The electronic expansion valve 17 is connected to the air-side heat exchanger 14 and the water-side heat exchanger 102 through communication pipes.
It is understood that the air side heat exchanger 14 refers to the heat exchange between the refrigerant and the air in the air side heat exchanger 14, for example, the air side heat exchanger 14 acts as a condenser, and the refrigerant releases heat into the air; the air-side heat exchanger 14 serves as an evaporator, and the refrigerant absorbs heat from the air. The water side heat exchanger 102 refers to heat exchange between the refrigerant and water in the water side heat exchanger 102, for example, the water side heat exchanger 102 serves as a condenser, and the refrigerant releases heat to the water in the water side heat exchanger 102; the water side heat exchanger 102 acts as an evaporator, and the refrigerant absorbs heat from the water in the water side heat exchanger 102.
The compressor 11, the condenser (e.g., the water side heat exchanger 102 or the air side heat exchanger 14), the electronic expansion valve 17, and the evaporator (e.g., the air side heat exchanger 14 or the water side heat exchanger 102) perform refrigerant circulation of the air source heat pump system. The refrigerant cycle includes a series of processes involving compression, condensation, expansion and evaporation, and supplies the refrigerant to the side cycle to be conditioned.
The compressor 11 compresses the gas-phase refrigerant in a low-temperature and low-pressure state, discharges the compressed gas-phase refrigerant of high temperature and high pressure, and flows into the condenser. The condenser condenses the high-temperature high-pressure gas-phase refrigerant into a high-pressure liquid-phase refrigerant, and heat is released to the surrounding environment along with the condensation process. The electronic expansion valve 17 expands the liquid-phase refrigerant in a high-pressure state into a gas-liquid two-phase refrigerant in a low-pressure state. The evaporator absorbs heat from the surrounding environment and evaporates the gas-liquid two-phase refrigerant in a low-pressure state to form a low-temperature low-pressure gas-phase refrigerant, and the low-temperature low-pressure gas-phase refrigerant returns to the compressor 11.
The water side heat exchanger 102 and the air side heat exchanger 14 function as a condenser or evaporator. When the water side heat exchanger 102 is used as a condenser, the air side heat exchanger 14 is used as an evaporator. When the water side heat exchanger 102 is used as an evaporator, the air side heat exchanger 14 is used as a condenser. When the water side heat exchanger 102 is used as a condenser, the water side heat exchanger 102 supplies hot water to the indoor end device 205 at this time, indoor side heating is achieved, and the air source heat pump system is used as a heater of a heating mode. When the water-side heat exchanger 102 is used as an evaporator, the water-side heat exchanger 102 supplies cold water to the indoor-end device 205, and indoor-side cooling is achieved, and the air-source heat pump system functions as a cooler in a cooling mode.
The water side heat exchanger 102 includes a refrigerant side and a water side. The refrigerant side includes a first refrigerant port 1021 and a second refrigerant port 1022, the first refrigerant port 1021 is connected to one port of the four-way valve 12, and the second refrigerant port 1022 is connected to the electronic expansion valve 17. The water side includes a heat pump water feed OUT that communicates with the water intake side of the indoor end device 205 and a heat pump water return IN that communicates with the water return side of the indoor end device 205 (as shown IN fig. 1).
The refrigerant side of the water side heat exchanger 102 receives the refrigerant flowing OUT through the refrigerant pipeline of the outdoor unit 101, cold and hot water flows OUT from the heat pump water supply port OUT after heat exchange of the water side heat exchanger 102, and the cold and hot water flows into the indoor terminal equipment 205 through the waterway circulation pipeline, so that indoor side refrigeration and heating are realized. The water flowing out from the indoor end equipment 205 flows back to the heat pump water return port IN to realize cold and hot water circulation.
It is understood that the side of the water side heat exchanger 102 connected to the outdoor unit 101 is the refrigerant side, and the side of the water side heat exchanger 102 connected to the indoor terminal device 205 is the water side.
Fig. 2 is a block diagram of a relay reversing device of an air source heat pump system according to some embodiments, in which a through flow direction is shown, and referring to fig. 2, the air source heat pump system further includes a relay reversing device 201 and a buffer tank 202. The relay reversing device 201 comprises a second water inlet A ', a third water outlet D' communicated with the second water inlet A ', a second water return port C', and a fourth water outlet B 'communicated with the second water return port C'. The second water inlet A 'communicates with the heat pump water feed OUT of the water side heat exchanger 102 and the third water outlet D' communicates with the water inlet side of the indoor end device 205. The fourth water outlet B 'is communicated with a heat pump water return port IN of the water side heat exchanger 102, and the second water return port C' is communicated with the water return side of the indoor terminal equipment 205. The buffer water tank 202 includes a main body and a first water inlet a, a first water outlet B, a first water return port C and a second water outlet D communicating with the main body.
As shown in fig. 1 and 2, the relay reversing device 201 further includes a first through branch 210, a first bypass branch 220, a second through branch 230, and a second bypass branch 240. The first bypass branch 210 directly communicates with the second water inlet a 'and the third water outlet D', and the first bypass branch 220 communicates with the second water inlet a 'and the third water outlet D' through the buffer tank 202. The first bypass branch 220 includes a first bypass branch 221 and a second bypass branch 222, the first bypass branch 221 communicates with the second water inlet a 'of the relay reversing device 201 and the first water inlet a of the buffer tank 202, and the second bypass branch 222 communicates with the first water outlet B of the buffer tank 202 and the third water outlet D' of the relay reversing device 201, such that the second water inlet a 'communicates with the third water outlet D' through the first bypass branch 220 and the buffer tank 202.
The second through branch 230 directly communicates with the second return port C 'and the fourth outlet B', and the second bypass branch 240 communicates with the second return port C 'and the fourth outlet B' through the buffer tank 202. The second bypass branch 240 includes a third bypass branch 241 and a fourth bypass branch 242, the third bypass branch 241 communicates with the second water return port C 'of the relay reversing device 201 and the first water return port C of the buffer tank 202, and the fourth bypass branch 242 communicates with the second water outlet D of the buffer tank 202 and the fourth water outlet B' of the relay reversing device 201, such that the second water return port C 'communicates with the fourth water outlet B' through the second bypass branch 240 and the buffer tank 202.
Fig. 3 is a block diagram of a relay reversing device of an air source heat pump system showing bypass flow according to some embodiments. The water flow passes through the first straight through branch 210 or the first bypass branch 220 when passing from the water side heat exchanger 102 to the indoor end fitting 205.
The first bypass branch 210 is in switching communication with the first bypass branch 220. That is, when the first through bypass 210 communicates with the second water inlet a 'and the third water outlet D', the first bypass 220 does not communicate with the second water inlet a 'and the third water outlet D', and the water flow outputted from the heat pump water supply outlet OUT of the water side heat exchanger 102 sequentially passes through the second water inlet a ', the first through bypass 210 and the third water outlet D', at this time, the water flow does not exchange heat through the buffer water tank 202, and the water flow goes toward the solid arrow as shown in fig. 2.
When the first through branch 210 is not connected to the second water inlet a 'and the third water outlet D', the first bypass branch 220 is connected to the second water inlet a 'and the third water outlet D', and the water flow outputted from the heat pump water supply outlet OUT of the water side heat exchanger 102 sequentially passes through the second water inlet a ', the first bypass branch 221, the buffer water tank 202, the second bypass branch 222 and the third water outlet D', and at this time, the water flow exchanges heat through the buffer water tank 202, and the water flow goes toward the solid arrows as shown in fig. 3. The water flow from the indoor end fitting 205 back to the water side heat exchanger 102 passes through the second straight through branch 230 or the second bypass branch 240.
The second through branch 230 is in switching communication with the second bypass branch 240. That is, when the second through branch 230 communicates with the second return port C 'and the fourth water outlet B', the second bypass branch 240 does not communicate with the second return port C 'and the fourth water outlet B', and the water flow flowing back from the indoor terminal device 205 sequentially passes through the second return port C ', the second through branch 230, and the fourth water outlet B', at this time, the water flow does not exchange heat through the buffer tank 202, and the water flow direction is indicated by a dotted arrow shown in fig. 2.
When the second through branch 230 is not connected to the second water return port C 'and the fourth water outlet B', the second bypass branch 240 is connected to the second water return port C 'and the fourth water outlet B', and at this time, the water flowing back from the indoor end device 205 to the water side heat exchanger 102 sequentially passes through the second water return port C ', the third bypass branch 241, the buffer tank 202, the fourth bypass branch 242 and the fourth water outlet B', and at this time, the water flows through the buffer tank 202 to exchange heat, as indicated by the dotted arrow shown in fig. 3.
To achieve the above-described communication of the different paths as needed, in some embodiments of the present disclosure, as shown in fig. 1 to 3, the relay reversing device 201 includes a first electric three-way valve 2011, a second electric three-way valve 2012, a third electric three-way valve 2013, and a fourth electric three-way valve 2014. The first electric three-way valve 2011 and the fourth electric three-way valve 2014 each comprise three ports, wherein the first port P1 and the third port P3 are arranged opposite to each other, the first port P1 is a water inlet, and the third port P3 is a water outlet; the second port P2 is perpendicular to the first port P1 and the third port P3, and the second port is a P2 water outlet. The second electric three-way valve 2012 and the third electric three-way valve 2013 each include three ports, wherein the first port P1 is opposite to the third port P3, the first port P1 is a water inlet, and the third port P3 is a water outlet; the second port P2 is disposed perpendicular to the first port P1 and the third port P3, and the second port P2 is a water inlet.
The first port P1 of the first electric three-way valve 2011 is communicated with the second water inlet a' of the relay reversing device 201, the second port P2 of the first electric three-way valve 2011 is communicated with the first water inlet a of the buffer water tank 202, and the third port P3 of the first electric three-way valve 2011 is communicated with the first port P1 of the second electric three-way valve 2012. The second port P2 of the second electric three-way valve 2012 communicates with the first water outlet B of the buffer water tank 202 and the third port P3 of the second electric three-way valve 2012 communicates with the third water outlet D'.
The first port P1 of the first electric three-way valve 2011 is controlled to communicate with the third port P3, and the first port P1 of the second electric three-way valve 2012 communicates with the third port P3 to form the first through branch 210. The first port P1 of the first electric three-way valve 2011 is controlled to communicate with the second port P2 to form a first bypass branch 221, and the second port P2 of the second electric three-way valve 2012 is controlled to communicate with the third port P3 to form a second bypass branch 222.
The first port P1 of the fourth electric three-way valve 2014 communicates with the second return port C', the second port P2 of the fourth electric three-way valve 2014 communicates with the first return port C of the buffer tank 202, and the third port P3 of the fourth electric three-way valve 2014 communicates with the first port P1 of the third electric three-way valve 2013. The second port P2 of the third electric three-way valve 2013 communicates with the second water outlet D of the buffer water tank 202, and the third port P3 and the fourth water outlet B' of the third electric three-way valve 2013 communicate.
When the first port P1 of the third electric three-way valve 2013 is controlled to communicate with the third port P3, and the first port P1 of the fourth electric three-way valve 2014 is controlled to communicate with the third port P3, the second through branch 230 is formed. The second port P2 of the third electric three-way valve 2013 is controlled to communicate with the third port P3 to form a fourth bypass branch 242, and the first port P1 of the fourth electric three-way valve 2014 is controlled to communicate with the second port P2 to form a third bypass branch 241.
It should be noted that, in some embodiments of the present disclosure, one of the first through branch 210 and the first bypass branch 220 is selected to be in communication, and one of the second through branch 230 and the second bypass branch 240 is selected to be in communication. IN addition, when the first through branch 210 is controlled to be communicated, the second through branch 230 must also be controlled to be communicated, at this time, when the air source heat pump system is operated, neither the water flowing OUT from the heat pump water supply port OUT of the water side heat exchanger 102 and entering the indoor end device 205 nor the water flowing back from the indoor end device 205 to the heat pump water return port IN of the water side heat exchanger 102 passes through the buffer water tank 202, and the pressure of the buffer water tank 202 is reduced; when the first bypass branch 220 is controlled to be communicated, the second bypass branch 240 is correspondingly controlled to be communicated, and at this time, when the air source heat pump system is operated, water flowing OUT from the heat pump water supply port OUT of the water side heat exchanger 102 and entering the indoor end equipment 205 and water flowing back to the heat pump water return port IN of the water side heat exchanger 102 from the indoor end equipment 205 pass through the buffer water tank 202, so that the cold storage capacity or the heat storage capacity of the buffer water tank 202 can be utilized.
The water side heat exchanger 102 controls the relay reversing device 201 so that the water output from the heat pump water supply port OUT of the water side heat exchanger 102 exchanges heat with or without passing through the buffer water tank 202. Illustratively, the water side heat exchanger 102 has an electrical control board, and the electrical control board of the water side heat exchanger 102 controls the relay reversing device 201 to exchange heat with or without the water output from the heat pump water feed outlet OUT of the water side heat exchanger 102 through the buffer water tank 202.
To enhance the flow capacity of the water in the relay reversing device 201, as shown in fig. 1 to 3, the relay reversing device 201 further includes a first booster pump 2015 and a second booster pump 2016, the first booster pump 2015 is located on a communication pipe between the second water inlet a 'and the first port P1 of the first electric three-way valve 2011, the second booster pump 2016 is located on a communication pipe between the third port P3 and the third water outlet D' of the second electric three-way valve 2012, and the first booster pump 2015 and the second booster pump 2016 are configured to change the pressure on the water flow in the communication pipe to change the speed of the water flow.
In some embodiments of the present disclosure, the air source heat pump system includes a plurality of indoor end devices 205, where the plurality of indoor end devices 205 includes a domestic hot water tank 2051 and two space heating/cooling devices 2050, and the two space heating/cooling devices 2050 are respectively exemplified as a wind disk 2052 and a floor heating 2053.
The air source heat pump system further includes a fifth electric three-way valve 203 and a sixth electric three-way valve 204, the fifth electric three-way valve 203 and the sixth electric three-way valve 204 being configured to realize switching of the domestic hot water tank 2051, the air tray 2052, and the floor heating 2053. The fifth electric three-way valve 203 and the sixth electric three-way valve 204 each comprise three ports, wherein the first port P1 is opposite to the third port P3, the first port P1 is a water inlet, and the third port P3 is a water outlet; the second port P2 is disposed perpendicular to the first port P1 and the third port P3, and the second port P2 is a water outlet.
The first port P1 of the fifth electric three-way valve 203 communicates with the third water outlet D', the second port P2 of the fifth electric three-way valve 203 communicates with the first port P1 of the sixth electric three-way valve 204, and the third port P3 of the fifth electric three-way valve 203 communicates with the water intake side of the air disc 2052. The second port P2 of the sixth electric three-way valve 204 is communicated with the water intake side of the floor heating 2053, and the third port P3 of the sixth electric three-way valve 204 is communicated with the water intake side of the domestic hot water tank 2051.
In this way, through the fifth electric three-way valve 203 and the sixth electric three-way valve 204, the switching communication between the relay reversing device 201 and the domestic hot water tank 2051, the wind disc 2052, and the floor heating 2053 is realized, and it should be noted that the switching communication in the present disclosure means that the relay reversing device 201 communicates with only one indoor terminal device 205 at the same time.
When a space heating/refrigerating device 2050 is added, an electric three-way valve is correspondingly added, and adjacent ports of each electric three-way valve are communicated.
It is appreciated that the domestic hot water tank 2051 and the space heating/cooling device 2050 belong to different types of indoor end devices 205. The domestic hot water tank 2051 is only in a heating mode when in operation; while the space heating/cooling device 2050 may be in a heating mode or a cooling mode when in operation.
The space heating/cooling device 2050 is configured to heat or cool an indoor space. When the water-side heat exchanger 102 heats or cools, the space heating/cooling device 2050 is filled with heating water or cooling water, thereby heating or cooling the indoor space.
When the domestic hot water tank 2051 and the space heating/cooling device 2050 are switched, or when the space heating/cooling device 2050 is switched between cooling and heating, it is necessary to control the relay reversing device 201 to control the heat pump water supply port OUT of the water side heat exchanger 102 to exchange heat with or without passing through the buffer water tank 202.
In some embodiments of the present disclosure, the plurality of indoor end devices 205 includes a domestic hot water tank 2051 and at least one space heating/cooling device 2050. Illustratively, the plurality of indoor end devices 205 includes one domestic hot water tank 2051 and one space heating/cooling device 2050, the domestic hot water tank 2051 and one space heating/cooling device 2050 are switched in operation, and the space heating/cooling device 2050 is automatically switched in operation for cooling and heating.
The buffer water tank 202 can be used as cold storage equipment or heat storage equipment, is configured to play roles in energy storage buffer, hydraulic partial pressure and the like in the air source heat pump system, can ensure temperature stability during space heating/refrigerating, and improves user comfort.
When in winter, the buffer tank 202 serves as a heat storage device. When the space heating/cooling device 2050 heats and the domestic hot water tank 2051 heats and switches, the water side heat exchanger 102 collects the water temperature in the indoor terminal device 205 in real time, determines whether the water temperature in the indoor terminal device 205 and the target temperature are within a preset temperature range, and controls the relay reversing device 201 to enable the first through branch 210 or the first through branch 220 to be communicated, so that the water output by the heat pump water supply port OUT of the water side heat exchanger 102 exchanges heat through or not through the buffer water tank 202.
When the water side heat exchanger 102 determines that the water temperature and the target temperature of the domestic hot water tank 2051 are within a preset temperature range (e.g., -5 deg.c to 5 deg.c) when switching from the space heating/cooling device 2050 heating to the domestic hot water tank 2051 heating, the relay reversing device 201 is controlled so that the first bypass branch 220 communicates with the buffer water tank 202, at which time the domestic hot water tank 2051 can use the heat in the buffer water tank 202. When the water side heat exchanger 102 determines that the water temperature and the target temperature of the domestic hot water tank 2051 are not within the preset temperature range, the relay reversing device 201 is controlled to enable the first through branch 210 to be communicated, water output by the heat pump water supply port OUT of the water side heat exchanger 102 does not pass through the buffer water tank 202, heating capacity of the water side heat exchanger 102 is fully utilized, heating effect of the domestic hot water tank 2051 is faster, and pressure of the buffer water tank 202 is reduced.
When the space heating/refrigerating equipment 2050 is switched from the domestic hot water tank 2051 to the space heating/refrigerating equipment 2050 for heating operation, the water side heat exchanger 102 controls the relay reversing device 201 to enable the first bypass branch 220 to be communicated with the buffer water tank 202, and at the moment, water output by the heat pump water supply mouth OUT of the water side heat exchanger 102 passes through the buffer water tank 202, so that the heat in the buffer water tank 202 is utilized to ensure the temperature stability during space heating, and the user comfort is improved.
When in summer, the buffer tank 202 serves as a cold storage device, for example. When the cooling of the space heating/cooling device 2050 is switched to the heating of the domestic hot water tank 2051, the water side heat exchanger 102 controls the relay reversing device 201 to enable the first through branch 210 to be communicated, and water output by the heat pump water supply port OUT of the water side heat exchanger 102 does not pass through the buffer water tank 202, so that the water in the buffer water tank 202 is prevented from being changed from cold water to hot water, the load of the buffer water tank 202 is reduced, and meanwhile, energy waste is avoided.
When the domestic hot water tank 2051 is heated and switched to the space heating/refrigerating equipment 2050 for refrigerating, the water side heat exchanger 102 controls the relay reversing device 201 to enable the first bypass branch 220 to be communicated with the buffer water tank 202, and water output from the heat pump water supply port OUT of the water side heat exchanger 102 passes through the buffer water tank 202, so that cold storage capacity in the buffer water tank 202 is utilized.
Illustratively, the buffer tank 202 serves as a thermal storage device. When the domestic hot water tank 2051 is heated and switched to the space heating/refrigerating equipment 2050 for refrigerating, the water side heat exchanger 102 controls the relay reversing device 201 to enable the first through branch 210 to be communicated, water output by the heat pump water supply port OUT of the water side heat exchanger 102 does not pass through the buffer water tank 202, water in the buffer water tank 202 is prevented from being changed into cold water from hot water, the load of the buffer water tank 202 is reduced, and meanwhile, energy waste is avoided.
When the cooling is switched from the space heating/cooling device 2050 to the heating of the domestic hot water tank 2051, the water side heat exchanger 102 controls the relay reversing device 201 such that the first bypass branch 220 communicates with the buffer water tank 202 when it is determined that the water temperature and the target temperature of the domestic hot water tank 2051 are within a preset temperature range (e.g., -5 ℃ to 5 ℃), and the domestic hot water tank 2051 can use the heat in the buffer water tank 202. When the water side heat exchanger 102 determines that the water temperature and the target temperature of the domestic hot water tank 2051 are not within the preset temperature range, the relay reversing device 201 is controlled to enable the first through branch 210 to be communicated, water output by the heat pump water supply port OUT of the water side heat exchanger 102 does not pass through the buffer water tank 202, heating capacity of the water side heat exchanger 102 is fully utilized, heating effect of the domestic hot water tank 2051 is faster, and pressure of the buffer water tank 202 is reduced.
When the space heating/cooling device 2050 enters an automatic operation mode in a transition season (spring and autumn), the automatic operation mode means that the space heating/cooling device 2050 automatically switches the cooling mode when the outdoor temperature is up to a preset temperature upper limit value, and the space heating/cooling device 2050 automatically switches the heating mode when the outdoor temperature is lower than a preset temperature lower limit value. The outdoor unit 101 thus controls the space heating/cooling device 2050 to perform automatic switching between space cooling and heating based on the detected outdoor temperature. The water side heat exchanger 102 controls the relay reversing device 201 so that the water output from the heat pump water supply port OUT of the water side heat exchanger 102 exchanges heat with or without passing through the buffer water tank 202.
Illustratively, the outdoor unit 101 further includes an outdoor unit electric control board 13, and the outdoor unit electric control board 13 collects outdoor ambient temperature and determines whether the space heating/cooling device 2050 is space cooling or space heating based on the outdoor ambient temperature. When the water side heat exchanger 102 is integrated into the outdoor unit 101, the electric control board in the water side heat exchanger 102 may be integrated into the outdoor unit electric control board 13, and at this time, the outdoor unit electric control board 13 may control the relay reversing device 201, so that the water output from the heat pump water supply port OUT of the water side heat exchanger 102 exchanges heat with or without passing through the buffer water tank 202.
In the automatic operation mode, the operation procedure of switching the cooling mode and the heating mode of the space heating/cooling device 2050 is as follows:
Illustratively, the buffer tank 202 serves as a thermal storage device. When the space heating/cooling device 2050 is switched from the cooling mode to the heating mode, the water side heat exchanger 102 controls the relay reversing device 201 to communicate the first bypass branch 220 with the buffer water tank 202, and the water output from the heat pump water supply port OUT of the water side heat exchanger 102 passes through the buffer water tank 202 to use the heat in the buffer water tank 202.
When the space heating/cooling device 2050 is switched from the heating mode to the cooling mode, the water side heat exchanger 102 controls the relay reversing device 201 to communicate the first through branch 210, the water output from the heat pump water supply port OUT of the water side heat exchanger 102 does not pass through the buffer water tank 202, the cooling capacity of the water side heat exchanger 102 is fully utilized, and the pressure of the buffer water tank 202 is reduced.
Illustratively, the buffer tank 202 serves as a cold storage device. When the space heating/cooling device 2050 is switched from the heating mode to the cooling mode, the water side heat exchanger 102 controls the relay reversing device 201 such that the first bypass branch 220 communicates with the buffer tank 202, and the water output from the heat pump water supply port OUT of the water side heat exchanger 102 passes through the buffer tank 202.
When the space heating/cooling device 2050 is switched from the cooling mode to the heating mode, the water side heat exchanger 102 controls the relay reversing device 201 to communicate the first through branch 210, and the water output from the heat pump water supply port OUT of the water side heat exchanger 102 does not pass through the buffer water tank 202.
In the automatic operation mode of the space heating/cooling device 2050, when the outdoor unit 101 determines that the space heating/cooling device 2050 needs to heat, the operation process of the space heating/cooling device 2050 and the domestic hot water tank 2051 in the heating/switching operation at this time refers to the operation process of the space heating/cooling device 2050 and the domestic hot water tank 2051 in the heating/switching operation in winter, which will not be described herein.
In the automatic operation mode of the space heating/cooling device 2050, when the outdoor unit 101 determines that the space heating/cooling device 2050 needs to perform cooling, the working process of the space heating/cooling device 2050 and the domestic hot water tank 2051 in the heating and switching operation at this time refers to the working process of the space heating/cooling device 2050 in summer and the working process of the domestic hot water tank 2051 in the heating and switching operation at this time, which will not be described herein.
As shown in fig. 1, the air source heat pump system further includes an auxiliary heat source 103, and the auxiliary heat source 103 is communicated with the buffer water tank 202 through a communication pipe. In some embodiments, the auxiliary heat source 103 may be a gas wall-mounted stove, solar water heater, gas water heater, or the like, with the auxiliary heat source 103 configured to provide heat to the buffer water tank 202. When the auxiliary heat source 103 is a solar water heater, the water in the buffer water tank 202 can be heated by satisfying the solar heatable temperature condition, so that the energy is effectively utilized.
In some embodiments of the present disclosure, the relay reversing device 201 may be controlled by an electric control board of the water side heat exchanger 102, and may also be controlled by an independent control circuit in the relay reversing device 201, and when the outdoor unit 101 fails, the auxiliary heat source 103 in communication with the buffer tank 202 may be used to provide heat energy to the indoor end device 205. It should be noted that, when the buffer tank 202 is only used as a heat storage device, the auxiliary heat source 103 can only work, and the start and stop of the auxiliary heat source 103 can be controlled by the electric control board of the water side heat exchanger 102.
Illustratively, when the space heating/cooling device 2050 heats and the domestic hot water tank 2051 heats and switches, the target temperature for heating in the buffer water tank 202 varies according to the indoor end device 205, and the auxiliary heat source 103 and the water side heat exchanger 102 may together supply heat to the water in the buffer water tank 202.
The buffer water tank 202 is a heat storage device, when the domestic hot water tank 2051 heats and switches to space heating/refrigerating equipment 2050 for refrigerating, the water side heat exchanger 102 controls the relay reversing device 201 to enable the first through branch 210 to be communicated, water output by the heat pump water supply mouth OUT of the water side heat exchanger 102 does not pass through the buffer water tank 202, heat provided by the auxiliary heat source 103 is effectively utilized, and refrigerating water is prevented from flowing into the buffer water tank 202, so that the load of the buffer water tank 202 is reduced.
The buffer water tank 202 is a heat storage device, and when the cooling is switched from the space heating/cooling device 2050 to the domestic hot water tank 2051 for heating, the water side heat exchanger 102 controls the relay reversing device 201 so that the first bypass branch 220 is communicated with the buffer water tank 202, and the water output from the heat pump water supply port OUT of the water side heat exchanger 102 passes through the buffer water tank 202 to utilize the heat provided by the auxiliary heat source 103.
For the air source heat pump system with the auxiliary heat source 103, when the outdoor unit 101 or the water side heat exchanger 102 fails, the cooling mode of the air source heat pump system cannot be performed normally, but at this time, the heating mode of the air source heat pump system can enter the emergency operation mode, i.e. the auxiliary heat source 103 can be used to heat the water in the buffer water tank 202, so as to further meet the heating requirement of the space heating/cooling device 2050.
When the living hot water tank 2051 and two or more space heating/cooling apparatuses 2050 are switched to operate, the operation process at the time of switching is similar as above.
In other embodiments of the present disclosure, the plurality of indoor end devices 205 includes at least two space heating/cooling devices 2050. Illustratively, the plurality of indoor end devices 205 includes two space heating/cooling devices 2050, respectively a floor heating 2053 and a wind disk 2052, the floor heating 2053 and the wind disk 2052 switching operation.
For example, when in winter or transitional seasons, and the buffer tank 202 serves as a heat storage device. The operation of the air pan 2052 heating and floor heating 2053 heating switching operations is as follows: the water side heat exchanger 102 controls the relay reversing device 201 to enable the first bypass branch 220 to be communicated with the buffer water tank 202, water output by the heat pump water supply port OUT of the water side heat exchanger 102 passes through the buffer water tank 202, and heat in the buffer water tank 202 is utilized to ensure stable temperature during space heating, so that user comfort is improved.
When the buffer water tank is used as the cold storage device in summer or in a transition season, the working process of the switching operation of cooling by the air disc 2052 and cooling by the ground heating 2053 is as follows: the water side heat exchanger 102 controls the relay reversing device 201 to enable the first bypass branch 220 to be communicated with the buffer water tank 202, water output by the heat pump water supply port OUT of the water side heat exchanger 102 passes through the buffer water tank 202, and the cold accumulation capacity in the buffer water tank 202 is utilized to enable the water temperature in the system to be in a lower state for a long time, so that user comfort is improved.
When there are a plurality of space heating/cooling devices 2050, the operation at the time of switching is similar as above.
In the present disclosure, by setting the relay reversing device 201 and the buffer water tank 202, different requirements of the indoor terminal device 205 can be met, and meanwhile, the pressure of the buffer water tank 202 can be effectively reduced, energy loss is reduced, and user experience is effectively improved.
Fig. 5 is a schematic diagram of a refrigerant cycle during a refrigeration operation of the air source heat pump system according to some embodiments, and the solid arrows in fig. 5 indicate the flow direction of the refrigerant during the refrigeration cycle of the air source heat pump system. As shown in fig. 5, the compressor 11 compresses a gas-phase refrigerant in a low-temperature and low-pressure state, discharges the compressed gas-phase refrigerant in a high-temperature and high-pressure state through the gas outlet 110, and the gas-phase refrigerant in a high-temperature and high-pressure state flows into the air-side heat exchanger 14 as a condenser through the four-way valve 12, the air-side heat exchanger 14 condenses the compressed gas-phase refrigerant in a high-pressure state into a liquid-phase refrigerant in a high-pressure state, and heat generated in the condensation process is released to the surrounding environment.
The liquid-phase refrigerant in a high-pressure state flowing out of the air-side heat exchanger 14 enters the electronic expansion valve 17, expands into a gas-liquid two-phase refrigerant in a low-pressure state through the electronic expansion valve 17, and then enters the water-side heat exchanger 102 serving as an evaporator. The water-side heat exchanger 102 evaporates the low-pressure gas-liquid two-phase refrigerant expanded in the electronic expansion valve 17, and the low-pressure gas-liquid two-phase refrigerant absorbs heat in water flowing through the water-side heat exchanger 102 and evaporates into a low-temperature low-pressure gas-phase refrigerant, and the low-temperature low-pressure gas-phase refrigerant finally returns to the compressor 11 through the return air port 111.
Fig. 6 is a schematic diagram of a refrigerant circulation during a heating operation of the air source heat pump system according to some embodiments, as indicated by a dashed arrow in fig. 6, the refrigerant flow direction during the heating cycle of the air source heat pump system is that the compressor 11 compresses a gas-phase refrigerant in a low-temperature low-pressure state and discharges the compressed gas-phase refrigerant in a high-temperature high-pressure state through the gas outlet 110, the gas-phase refrigerant in a high-temperature high-pressure state flows into the water side heat exchanger 102 as a condenser through the four-way valve 12, the water side heat exchanger 102 condenses the compressed gas-phase refrigerant in a high-pressure state into a liquid-phase refrigerant, and heat generated in the condensation process is released into water flowing in the water side heat exchanger 102.
The liquid-phase refrigerant in a high-pressure state from the water-side heat exchanger 102 enters the electronic expansion valve 17, expands into a gas-liquid two-phase refrigerant in a low-pressure state through the electronic expansion valve 17, and then enters the air-side heat exchanger 14 as an evaporator. The air-side heat exchanger 14 evaporates the low-pressure gas-liquid two-phase refrigerant expanded in the electronic expansion valve 17, and the low-pressure gas-liquid two-phase refrigerant absorbs heat in the surrounding environment and evaporates into a low-temperature low-pressure gas-phase refrigerant, and the gas-phase refrigerant in the low-temperature low-pressure state finally returns to the compressor 11 through the gas return port 111.
After the product is stopped, the refrigerant flows from the high-pressure side to the low-pressure side due to the pressure difference problem at the two ends of the compressor, and when the product is started again, the refrigerant at the low-pressure side enters the compressor 11 for compression, and the gas-phase refrigerant discharged after being compressed by the compressor 11 is in a high-pressure high-temperature overheat state. Because the gas-phase refrigerant is discharged at a high flow rate and a high temperature, part of compressor oil is discharged together with the gas-phase refrigerant due to the fact that oil vapor and oil drop particles are formed under the action of the high temperature. And the higher the temperature of the gas-phase refrigerant, the faster the flow rate, and the more compressor oil is discharged. Therefore, a large amount of refrigerant at the low pressure side is recompressed and discharged, so that a large amount of compressor oil taken away by the compressor can cause the problem of oil shortage of the compressor.
In the related art, an oil separator is installed between the outlet 110 of the compressor 11 and the four-way valve 12, a high-temperature and high-pressure gas-phase refrigerant discharged from the compressor 11 and a part of compressor oil enter the oil separator, the oil separator separates the gas-phase refrigerant from the part of compressor oil, the high-temperature and high-pressure gas-phase refrigerant enters the condenser to be condensed, and a part of compressor oil returns to the compressor 11 through the oil separator. However, adding an oil separator increases cost and is therefore not generally used.
To solve the above-mentioned problems, in some embodiments of the present disclosure, as shown in fig. 4, the air source heat pump system further includes a check valve 15, and the check valve 15 is disposed between the discharge port 110 of the compressor 11 and the four-way valve 12, and is in one-way conduction from the compressor 11 to the four-way valve 12.
Fig. 7 is a control principle timing diagram of an air source heat pump system according to some embodiments, fig. 8 is a control principle timing diagram of another air source heat pump system according to some embodiments, and fig. 13 is a block diagram of an air source heat pump system according to some embodiments. As shown in fig. 4, the air source heat pump system further includes a blower 18, a high pressure switch 19, and a low pressure switch 20. The blower 18 is disposed at one side of the air-side heat exchanger 14. The high-pressure switch 19 is provided between the discharge port 110 of the compressor 11 and the check valve 15, and is configured to be turned off when the pressure in the air source heat pump system is higher than a preset pressure upper limit value. The low pressure switch 20 is provided between the return air port 111 of the compressor 11 and the four-way valve 12, and is configured to be turned off when the pressure in the air source heat pump system is lower than a preset pressure lower limit value.
As shown in fig. 8 and 13, the outdoor unit electric control board 13 is connected to the electronic expansion valve 17, the compressor 11, and the blower 18, and is configured to: when a stop signal is received, the electronic expansion valve 17 is closed, and the compressor 11 and the fan 18 are controlled to be kept on; when it is determined that the shutdown condition is satisfied, the compressor 11 and the blower 18 are turned off.
It will be appreciated that when the air source heat pump system does not include the blower 18, as shown in fig. 7 and 13, the outdoor unit electric control board 13 is connected to the electronic expansion valve 17 and the compressor 11, and configured to: when a stop signal is received, the electronic expansion valve 17 is closed, and the compressor 11 is controlled to be kept on; when it is determined that the shutdown condition is satisfied, the compressor 11 is turned off.
The shutdown condition includes any one of the following conditions: the suction pressure of the compressor 11 reaches the suction pressure lower limit value, the discharge pressure of the compressor 11 reaches the discharge pressure upper limit value, the discharge temperature of the compressor 11 reaches the discharge temperature upper limit value, the high-pressure switch 19 is turned off, the low-pressure switch 20 is turned off, and the duration in which the compressor 11 remains on reaches the time upper limit value.
When the suction pressure of the compressor 11 reaches the suction pressure lower limit value or the discharge pressure of the compressor 11 reaches the discharge pressure upper limit value, the outdoor unit electric control board 13 controls the compressor 11 to be closed, so that the suction pressure and the discharge pressure can be protected, and the operation pressure safety of the system is ensured.
When the duration of the compressor 11 kept on reaches the upper limit value of time, the outdoor unit electric control board 13 controls the compressor 11 to be turned off, so that the system is prevented from being unable to stop for a long time after receiving the stop signal.
In some embodiments of the present disclosure, the electronic expansion valve 17 is closed after the outdoor unit electric control board 13 receives the shutdown signal and the compressor 11 is controlled to keep running, at this time, the compressor 11 may continue to discharge the refrigerant at the low pressure side to the high pressure side, and because the electronic expansion valve 17 is closed, the refrigerant at the high pressure side cannot flow to the low pressure side through the communication pipeline, after the above process continues for a period of time, when the outdoor unit electric control board 13 determines that the shutdown condition is met, the compressor 11 is closed. Because of the existence of the check valve 15, the refrigerant on the high pressure side cannot flow to the low pressure side through the compressor 11, and at this time, the high pressure side and the low pressure side always maintain a pressure difference state, thereby realizing the storage of the refrigerant on the high pressure side. After the compressor 11 is restarted, a large amount of refrigerant cannot enter the compressor 11 in a short time due to the small amount of refrigerant at the low pressure side, so that a large amount of compressor oil of the compressor 11 cannot be consumed, and the problem of oil shortage of the compressor 11 is avoided. With the circulation of the refrigerant, the refrigerant at the high pressure side flows back to the low pressure side through the electronic expansion valve 17 which is opened again, and then enters the compressor 11, so as to form dynamic balance of the refrigerant.
In some embodiments of the present disclosure, the outdoor unit electronic control board 13 is further configured to control the compressor 11 to be operated at a set frequency after receiving the shutdown signal. The set frequency at least satisfies that the pressure difference between the discharge port 110 and the return port 111 of the compressor 11 is not less than the pressure difference threshold.
In some embodiments of the present disclosure, the set frequency is in the range of 30Hz to 60Hz, and the high pressure side and the low pressure side of the compressor 11 maintain a suitable pressure differential while within the set frequency range.
In some embodiments of the present disclosure, the rotation speed of the outdoor unit electric control board 13 for controlling the fan 18 to be turned on should be maintained at a relatively high rotation speed to improve heat exchange efficiency.
In some embodiments of the present disclosure, the air source heat pump system includes two modes of operation, a normal mode and a silent mode, respectively, where normal mode refers to maintaining a relatively high rotational speed during normal operation of the blower 18 as compared to the silent mode. The silent mode herein refers to the fan 18 being maintained at a relatively low rotational speed during normal operation as compared to the normal mode. The rotating speed of the fan 18 in the mute mode is smaller than that of the fan 18 in the normal mode, and noise generated by the fan 18 is reduced by reducing the rotating speed of the fan 18, so that low-noise operation is realized. The fan 18 has corresponding gear positions in the normal mode and the mute mode, and each gear position is independently set.
In the mute mode, the gear of the blower 18 includes a first gear and a second gear, and the wind speed of the first gear is greater than the wind speed of the second gear. In the normal mode, the gear of the blower 18 includes a third gear and a fourth gear, and the wind speed of the third gear is greater than the wind speed of the fourth gear. It should be noted that, the mute mode and the normal mode are not limited to the two gear positions, more gear positions may be set to further refine the control range, and the outdoor unit electric control board 13 controls the fan 18 to operate according to different gear positions in different modes.
In some embodiments of the present disclosure, for an air source heat pump system that does not include a silent mode, the outdoor unit electronic control board 13 is controlled according to control logic of a normal mode when controlling the operation of the blower 18.
For air source heat pump systems using a refrigerant such as R32, the refrigerant charge of the system generally requires a minimum room area, and the smaller the refrigerant charge in the system, the easier it is to meet the field installation room area requirement. Therefore, for this type of air source heat pump product, the system is designed without using a reservoir in order to reduce the refrigerant charge in the system. Because the difference between the inner volumes of the water side heat exchanger 102 and the air side heat exchanger 14 is large, the optimal refrigerant amount required by the air source heat pump system during refrigeration and heating is inconsistent, and the refrigerant amount filled in the air source heat pump system during refrigeration and heating cannot be balanced when the liquid storage device is not used.
In the related art, the air source heat pump system adopts the water side heat exchanger 102 and the air side heat exchanger 14 with the same internal volume, but the selection requirement on the water side heat exchanger 102 and the air side heat exchanger 14 is higher, and when the water side heat exchanger 102 and the air side heat exchanger 14 with the same internal volume cannot be selected, the problem that the refrigerant amount filled in the air source heat pump system cannot be kept balanced during refrigeration and heating cannot be avoided.
Fig. 9 is a structural diagram of an auxiliary liquid storage pipe section in an embodiment of an air source heat pump system, and in some embodiments of the present disclosure, as shown in fig. 4 and 9, the air source heat pump system further includes an auxiliary liquid storage pipe section 16, wherein the auxiliary liquid storage pipe section 16 is a cylinder, is disposed along a vertical direction and is located between the water side heat exchanger 102 and the air side heat exchanger 14, and is configured to assist the water side heat exchanger 102 to store a refrigerant. The auxiliary reservoir pipe section 16 includes a top port 161 and a bottom port 162, the top port 161 is connected to the air side heat exchanger 14 through a communication line, and the bottom port 162 is connected to the water side heat exchanger 102 through a communication line.
As shown in fig. 6 and 9, when the air source heat pump system is in heating operation, referring to arrows shown by broken lines in fig. 9, the liquid-phase refrigerant in a high-pressure state flowing out of the water side heat exchanger 102 enters the auxiliary liquid pipe section 16 from the bottom port 162 and flows out from the top port 161. The auxiliary liquid storage pipe section 16 needs to be fully filled before the high-pressure gas-liquid two-phase refrigerant flowing out of the water side heat exchanger 102 enters the electronic expansion valve 17, at this time, the auxiliary liquid storage pipe section 16 is configured to share the amount of liquid refrigerant which should be stored in the water side heat exchanger 102 as a condenser, at this time, more refrigerant circulates to the water side heat exchanger 102, and thus the heating operation mode can be operated better.
As shown in fig. 5 and 9, when the air source heat pump system is operated in the cooling mode, referring to the arrows shown by the solid lines in fig. 9, the low-pressure gas-liquid two-phase refrigerant flowing out of the electronic expansion valve 17 enters the auxiliary liquid storage pipe section 16 from the top port 161 and flows out of the bottom port 162, the amount of refrigerant stored in the auxiliary liquid storage pipe section 16 is reduced by the up-in-down-out mode, so that more refrigerant can be circulated to the air side heat exchanger 14 as a condenser, and the cooling mode can be operated better.
In the cooling and heating operation of the air source heat pump system, the volume of the air side heat exchanger 14 is far greater than the volume of the water side heat exchanger 102, the density of the high-pressure refrigerant is high, the high-pressure liquid-phase refrigerant is generated in the air side heat exchanger 14 as a condenser during cooling, the amount of the stored refrigerant is small in the auxiliary liquid storage pipe section 16 at this time, the high-pressure liquid-phase refrigerant is generated in the water side heat exchanger 102 as a condenser during heating, and the amount of the stored refrigerant is large in the auxiliary liquid storage pipe section 16 at this time. Therefore, the refrigerant quantity of the air source heat pump system during refrigeration and heating can be balanced by adding the auxiliary liquid storage pipe section 16.
In some embodiments of the present disclosure, the air side heat exchanger 14 may be, but is not limited to, a fin and tube heat exchanger and the water side heat exchanger 102 may be, but is not limited to, a plate heat exchanger.
Fig. 10 is a control principle flow chart of an embodiment of an air source heat pump system, as shown in fig. 4 and 10, in some embodiments of the present disclosure, the outdoor unit electric control board 13 is further configured to control to close the electronic expansion valve 17 and control the compressor 11 to be kept on when a shutdown signal is received and it is determined that the air source heat pump system is not malfunctioning, and to close the compressor 11 and the blower 18 when it is determined that the shutdown condition is satisfied.
In some embodiments of the present disclosure, the auxiliary reservoir pipe section 16 is disposed between the electronic expansion valve 17 and the water side heat exchanger 102. When the outdoor unit electric control board 13 executes the shutdown control logic (i.e. the electronic expansion valve 17 is closed, and the compressor 11 is kept on), the check valve 15 can prevent the refrigerant from leaking from the high pressure side to the low pressure side when the air source heat pump system heats or cools, and the auxiliary liquid storage pipe section 16 can assist the water side heat exchanger 102 to store more refrigerant at the high pressure side when the air source heat pump system heats. For systems that do not use a reservoir, the most appropriate auxiliary reservoir tube segment 16 size and refrigerant addition is calculated in the on-line scheme. On the premise that the pressure drop of the auxiliary liquid storage pipe section 16 is allowed, the auxiliary liquid storage pipe section 16 is shorter, the corresponding pipe diameter is thicker, the longer the auxiliary liquid storage pipe section 16 is, the corresponding pipe diameter is thinner, and the refrigerant quantity stored in the auxiliary liquid storage pipe section 16 is ensured to be within an allowed range without affecting the reliability. Meanwhile, the on-line tubing without filling can be increased in the mode, and site installation is facilitated.
In some embodiments of the present disclosure, as shown in fig. 10, the control method of the air source heat pump system includes S11 to S14.
S11, when the outdoor unit electric control board 13 receives a stop signal, the outdoor unit electric control board 13 determines whether an air source heat pump system fails; when the air source heat pump system fails, executing S12; otherwise, S14 is performed.
S12, the outdoor unit electric control board 13 controls the electronic expansion valve 17 to be closed, and the compressor 11 and the fan 18 are kept on.
S13, the outdoor unit electric control board 13 determines whether a shutdown condition is met; when the shutdown condition is satisfied, S14 is performed; otherwise, S12 is performed.
S14, the outdoor unit electric control board 13 controls the compressor 11, the fan 18 and the electronic expansion valve 17 to be closed.
Fig. 11 is a flowchart of a method for determining the internal volume of the auxiliary liquid storage pipe section in an embodiment of an air source heat pump system, as shown in fig. 11, in some embodiments of the present disclosure, the method for determining the internal volume of the auxiliary liquid storage pipe section 16 includes: s110 to S180.
S110, determining a theoretical cycle.
And S120, selecting the types of the compressor 11, the air side heat exchanger 14, the electronic expansion valve 17 and the water side heat exchanger 102.
S130, judging whether the standard refrigeration capacity and the standard heating capacity energy efficiency of the air source heat pump system reach the standard after test and test; when the standard refrigerating and standard heating capacity energy efficiency of the air source heat pump system reaches the standard, executing S140; otherwise, the theoretical cycle is corrected, and S120 is performed.
S140, obtaining total refrigerant quantity m c and m h of all components and communication pipelines in the refrigeration operation and the heating operation under ideal conditions.
The total refrigerant quantity of all parts and communication pipelines in the refrigeration operation and the heating operation in the ideal state is m c and m h respectively; ideally, the volume of the air-side heat exchanger 14 as a condenser in the cooling operation is larger than the volume of the water-side heat exchanger 102 as a condenser in the heating operation, and therefore, the total refrigerant amount m c flowing to all the components and the communication lines in the air-source heat pump system in the cooling operation is larger than the total refrigerant amount m h flowing to all the components and the communication lines in the air-source heat pump system in the heating operation.
The method for obtaining the total refrigerant quantity m c and m h of all the components and the communication pipeline in the refrigeration operation and the heating operation under the ideal state is various, and can comprise the following steps: s141, determining the refrigerant quantity by adopting simulation calculation; or S142, determining the refrigerant quantity in a test mode.
The method for determining the refrigerant quantity by adopting simulation calculation comprises the following steps: and calculating the total refrigerant quantity m c of all the components and the communication pipelines in the standard refrigeration operation and the total refrigerant quantity m h of all the components and the communication pipelines in the standard heating operation.
As shown in fig. 12, the method for calculating and determining the refrigerant amount by using the bottoming test includes: the test was performed using a prototype without a reservoir, testing standard refrigeration and heating conditions, and adjusting the refrigerant quantity to an optimal COP (Coefficient of Performance, energy efficiency coefficient) to achieve the required capacity, to obtain m c、m h, respectively.
S150, the densities rho c and rho h of the refrigerants in the auxiliary liquid storage pipe section 16 during the refrigeration operation and the heating operation in the ideal state are obtained.
The densities of the refrigerants in the auxiliary liquid storage pipe section 16 during the refrigeration operation and the heating operation in the ideal state are ρ c and ρ h respectively; in an ideal state, the amount of the refrigerant stored in the auxiliary liquid storage pipe section 16 is small during the refrigeration operation, the refrigerant in the liquid part of the refrigerant in the gas-liquid two-phase state is not easy to store in the auxiliary liquid storage pipe section 16, a large amount of the refrigerant is stored in the auxiliary liquid storage pipe section 16 during the heating operation, and the refrigerant in the gaseous part of the refrigerant in the gas-liquid two-phase state is not easy to store in the auxiliary liquid storage pipe section 16, so that the density ρ c of the refrigerant in the auxiliary liquid storage pipe section 16 during the refrigeration operation is smaller than the density ρ h of the refrigerant in the auxiliary liquid storage pipe section 16 during the heating operation.
S160, calculating the internal volume V of the auxiliary liquid storage pipe section: v= (m c-m h)/(ρ h-ρ c).
The diameter and length of the auxiliary reservoir section 16 are selected to be appropriate based on the internal volume V of the auxiliary reservoir section 16, such that the internal volume thereof is equal to V.
S170, the total refrigerant charge m=m c+ρ c V, or m=m h+ρ h V is calculated.
S180, testing other working conditions, and verifying reliability.
In the description of the above embodiments, particular features, structures, materials, or characteristics may be combined in any suitable manner in any one or more embodiments or examples.
It will be understood by those skilled in the art that the scope of the present disclosure is not limited to the specific embodiments described above, and that certain elements of the embodiments may be modified and substituted without departing from the spirit of the application. The scope of the application is limited by the appended claims.

Claims (15)

  1. An air source heat pump system comprising:
    the compressor comprises an exhaust port and an air return port;
    A water side heat exchanger;
    an air side heat exchanger connected with the water side heat exchanger;
    Four ports of the four-way valve are respectively connected with an exhaust port of the compressor, a return port of the compressor, the water side heat exchanger and the air side heat exchanger;
    The one-way valve is connected between the exhaust port of the compressor and the four-way valve, and the compressor is in one-way conduction with the four-way valve;
    the electronic expansion valve is connected between the air side heat exchanger and the water side heat exchanger;
    The outdoor unit electric control board is connected with the compressor and the electronic expansion valve and is configured to:
    when a shutdown signal is received, closing the electronic expansion valve and controlling the compressor to be kept on;
    when it is determined that a shutdown condition is satisfied, the compressor is shut down.
  2. The air source heat pump system of claim 1, wherein the outdoor unit electric control board is further configured to control the compressor to operate at a set frequency that at least satisfies a pressure difference between an exhaust port and a return port of the compressor not less than a pressure difference threshold when a shutdown signal is received.
  3. An air source heat pump system according to claim 2 wherein the set frequency has a value in the range of 30Hz to 60Hz.
  4. The air source heat pump system of claim 1, further comprising a blower disposed on one side of the air side heat exchanger;
    The outdoor unit electric control board is connected with the fan and is further configured to:
    When a shutdown signal is received, controlling the fan to be kept on;
    and when the shutdown condition is determined to be met, the fan is turned off.
  5. The air source heat pump system according to claim 4 wherein,
    The gear of the fan comprises a first gear, a second gear, a third gear and a fourth gear, the wind speed of the third gear is larger than the wind speed of the fourth gear, the wind speed of the fourth gear is larger than the wind speed of the first gear, and the wind speed of the first gear is larger than the wind speed of the second gear;
    the outdoor unit electric control board is further configured to:
    when the current operation mode of the air source heat pump system is a mute mode, controlling the fan to operate according to a first gear or a second gear;
    And when the current operation mode of the air source heat pump system is a common mode, controlling the fan to operate according to a third gear or a fourth gear.
  6. The air source heat pump system according to claim 1 wherein,
    The outdoor unit electric control board is further configured to:
    When a shutdown signal is received and the air source heat pump system is determined to not have a fault, closing the electronic expansion valve and controlling a compressor to be kept on;
    The compressor is shut down when a shutdown condition is determined to be satisfied.
  7. The air source heat pump system according to any one of claims 1-6, further comprising:
    The high-pressure switch is arranged between the exhaust port of the compressor and the one-way valve, is connected with the outdoor unit electric control board and is configured to be disconnected when the pressure in the air source heat pump system is higher than a preset pressure upper limit value;
    The low-pressure switch is arranged between the air return port of the compressor and the four-way valve, is connected with the outdoor unit electric control board and is configured to be disconnected when the pressure in the air source heat pump system is lower than a preset pressure lower limit value;
    the shutdown condition includes any one of the following conditions:
    the suction pressure of the compressor reaches the lower limit value of the suction pressure;
    the discharge pressure of the compressor reaches the upper limit value of the discharge pressure;
    The exhaust temperature of the compressor reaches an upper limit value of the exhaust temperature;
    the high-voltage pressure switch is opened;
    The low-voltage pressure switch is opened;
    the duration for which the compressor remains on reaches a time upper limit.
  8. The air source heat pump system of claim 1, further comprising:
    The auxiliary liquid storage pipe section is arranged in the vertical direction and is provided with a top port and a bottom port, the top port is connected with the electronic expansion valve, and the bottom port is connected with the water side heat exchanger.
  9. The air source heat pump system of claim 8, wherein the internal volume of the auxiliary reservoir pipe section is calculated by the formula:
    V＝(m c-m h)/(ρ h-ρ c)
    Wherein V represents the internal volume of the auxiliary liquid storage pipe section, m c represents the total refrigerant quantity of all components and communication pipelines in the refrigeration operation in the ideal state, ρ c represents the density of the refrigerant in the auxiliary liquid storage pipe section in the refrigeration operation in the ideal state, m h represents the total refrigerant quantity of all components and communication pipelines in the heating operation in the ideal state, ρ h represents the density of the refrigerant in the auxiliary liquid storage pipe section in the heating operation in the ideal state.
  10. The air source heat pump system of claim 1, further comprising:
    The buffer water tank is provided with a first water inlet, a first water outlet, a first water return port and a second water outlet;
    The indoor terminal equipment comprises a domestic hot water tank and at least one space heating/refrigerating equipment or at least two space heating/refrigerating equipment, and the indoor terminal equipment is switched to run;
    The relay reversing device is provided with a second water inlet communicated with a heat pump water supply port of the water side heat exchanger, a fourth water outlet communicated with a heat pump water return port of the water side heat exchanger, and a second water return port and a third water outlet communicated with the plurality of indoor terminal devices; the relay reversing device further includes:
    the first straight-through branch is communicated with the second water inlet and the third water outlet;
    The first bypass branch comprises a first bypass branch and a second bypass branch, the first bypass branch is communicated with the second water inlet and the first water inlet, and the second bypass branch is communicated with the first water outlet and the third water outlet;
    Wherein the first through branch is in switching communication with the first bypass branch;
    the second straight-through branch is communicated with the second water return port and the fourth water outlet;
    The second bypass branch comprises a third bypass branch and a fourth bypass branch, and the third bypass branch is communicated with the second water return port and the first water return port; the fourth bypass branch is communicated with the second water outlet and the fourth water outlet;
    wherein the second through branch is in switched communication with the second bypass branch.
  11. The air source heat pump system of claim 10, wherein the relay reversing device comprises a first electrically powered three-way valve, a second electrically powered three-way valve, a third electrically powered three-way valve, and a fourth electrically powered three-way valve;
    The first port of the first electric three-way valve is communicated with the second water inlet, the second port of the first electric three-way valve is communicated with the first water inlet, the third port of the first electric three-way valve is communicated with the first port of the second electric three-way valve, the second port of the second electric three-way valve is communicated with the first water outlet, the third port of the second electric three-way valve is communicated with the third water outlet, and the first electric three-way valve and the second electric three-way valve form the first straight-through branch and the first bypass branch;
    The first port of the fourth electric three-way valve is communicated with the second water return port, the second port of the fourth electric three-way valve is communicated with the first water return port, the third port of the fourth electric three-way valve is communicated with the first port of the third electric three-way valve, the second port of the third electric three-way valve is communicated with the second water outlet, the third port of the third electric three-way valve is communicated with the fourth water outlet, and the third electric three-way valve and the fourth electric three-way valve form the second straight-through branch and the second bypass branch.
  12. The air source heat pump system of claim 11, further comprising:
    the first booster pump is connected between the second water inlet and the first port of the first electric three-way valve;
    and the second booster pump is connected between the third port and the third water outlet of the second electric three-way valve.
  13. The air source heat pump system of claim 10, further comprising:
    An auxiliary heat source in communication with the buffer tank configured to provide heat to the buffer tank.
  14. The air source heat pump system of claim 13, wherein the auxiliary heat source comprises a gas-fired wall-mounted furnace, a solar water heater, or a gas-fired water heater.
  15. An air source heat pump system according to claim 10 wherein the space heating/cooling device comprises a fan tray or floor heating.
CN202280061663.7A 2022-06-08 2022-12-05 Air source heat pump system Pending CN117940706A (en)

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CN202210642290.4A CN114935223A (en) 2022-06-08 2022-06-08 Air source heat pump system
CN2022106422904 2022-06-08
PCT/CN2022/136619 WO2023103968A1 (en) 2021-12-07 2022-12-05 Air source heat pump system

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