CN112815570B - Gas heat pump multi-split air conditioning system and efficient defrosting control method thereof - Google Patents
Gas heat pump multi-split air conditioning system and efficient defrosting control method thereof Download PDFInfo
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- CN112815570B CN112815570B CN202110060870.8A CN202110060870A CN112815570B CN 112815570 B CN112815570 B CN 112815570B CN 202110060870 A CN202110060870 A CN 202110060870A CN 112815570 B CN112815570 B CN 112815570B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B27/00—Machines, plants or systems, using particular sources of energy
- F25B27/02—Machines, plants or systems, using particular sources of energy using waste heat, e.g. from internal-combustion engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2347/00—Details for preventing or removing deposits or corrosion
- F25B2347/02—Details of defrosting cycles
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- 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
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A30/00—Adapting or protecting infrastructure or their operation
- Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
- Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine
Abstract
The invention discloses a gas heat pump multi-split air conditioning system, which relates to a heat pump system, and at least comprises a power unit, a heat pump circulation unit and a waste heat recovery unit, wherein a high-temperature and high-pressure gaseous refrigerant formed by compressing a low-temperature and low-pressure gaseous refrigerant in the system by a compressor is condensed by a condenser, a condensed high-pressure liquid refrigerant is throttled and depressurized by a throttling device, the throttled low-temperature and low-pressure gas-liquid two-phase refrigerant is evaporated into a low-temperature and low-pressure gaseous refrigerant by an evaporator, and then the low-temperature and low-pressure gaseous refrigerant returns to the compressor and is continuously compressed into a high-temperature and high-pressure gaseous refrigerant to be discharged to the condenser, so that complete heat pump system circulation is formed. The system and the method have the characteristics of high defrosting speed, small heating quantity attenuation in the defrosting period and high comfort.
Description
Technical Field
The invention relates to the technical field of heat pump systems, in particular to a gas heat pump multi-split air conditioning system and an efficient defrosting control method thereof.
Background
A Gas Engine Driven Heat Pump (GHP) system is an air conditioning system that uses Gas (including natural Gas, liquefied petroleum Gas, methane, etc.) as high-grade driving energy, and uses a Gas Engine to do work to directly drive an open-type compressor to work, thereby completing a vapor compression refrigeration cycle to achieve the purpose of refrigeration or heating. Compared with an Electric Heat Pump (EHP) which uses electric power as high-grade driving energy, the gas heat pump has no difference on the heat pump theory, a high-efficiency gas engine is used for replacing a motor of the electric heat pump, and a large amount of engine cylinder sleeve heat and exhaust smoke waste heat can be recovered to construct a distributed energy system for gradient utilization of energy due to the change of a driving source, so that the primary energy utilization rate is obviously improved.
The EHP can appear frequently frosting problem in the low temperature operation heating process in winter, the existence of frost layer after frosting can increase the heat transfer thermal resistance between refrigerant and air, and the heat transfer amount of wind can attenuate by a wide margin simultaneously, causes the heat transfer effect extremely poor. Meanwhile, the EHP system usually adopts a reverse circulation defrosting mode to defrost, and at this time, the system is switched to a cooling mode due to the reversing of the system four-way valve, which greatly affects the comfort of the heating room. If a plurality of external units of the EHP multi-split air conditioner are connected in parallel, the comfort of a heating room can be slightly improved by adopting a mode of alternately defrosting (namely, a defrosting external unit is switched into a refrigerating mode, and a non-defrosting external unit still operates in a heating mode), but the problems of insufficient heating capacity, low air outlet temperature, long defrosting time, incomplete defrosting and the like of the system still exist. For a GHP multi-split air conditioning system, although waste heat of an engine can be recovered to be used for system defrosting in an auxiliary mode, the problems that defrosting time is long, heating quantity is attenuated to influence comfort experience of users and the like still exist.
Disclosure of Invention
Aiming at the defects in the prior art, the invention provides a gas heat pump multi-split air conditioning system and a high-efficiency defrosting control method thereof.
In order to achieve the purpose, the technical scheme of the invention is as follows:
a gas heat pump multi-split air conditioning system at least comprises a power unit, a heat pump circulating unit and a waste heat recovery unit,
the heat pump circulating unit comprises a compressor, an oil separator, a four-way valve, an outdoor heat exchanger, an indoor heat exchanger, a throttling device and a gas-liquid separator, wherein an air outlet of the compressor is communicated with an inlet of the oil separator, a first outlet of the oil separator is connected into the four-way valve, a left port of the outdoor heat exchanger is connected into the four-way valve, a right port of the outdoor heat exchanger is communicated with an upper port of the indoor heat exchanger, a second outlet of the oil separator is connected to an air suction port of the compressor, a lower port of the indoor heat exchanger is connected into the four-way valve, an inlet of the gas-liquid separator is connected into the four-way valve, and an outlet of the gas-liquid separator is connected to the air suction port of the compressor;
the power unit comprises a gas engine for driving the compressor;
the waste heat recovery unit comprises a heat storage device and a refrigerant-water heat exchanger, wherein a right port of the refrigerant-water heat exchanger is connected to a left port of the outdoor heat exchanger and an upper port of the indoor heat exchanger through two independent pipelines respectively; the left port of the refrigerant-water heat exchanger is connected to the inlet of the gas-liquid separator through two independent pipelines, and one pipeline is provided with the heat storage device.
The gas heat pump multi-split air conditioning system further comprises an engine cylinder sleeve, a first heat recoverer and a flue gas waste heat recoverer, wherein,
the gas engine is connected with the engine cylinder sleeve, cooling liquid flows out through the engine cylinder sleeve and the first heat recoverer, and at the moment, cold water is recovered by the first heat recoverer and the flue gas waste heat recoverer to form hot water which is supplied through a plurality of branches.
The gas heat pump multi-split air conditioning system further comprises a gas waste heat recoverer, wherein the gas waste heat recoverer is used for recovering heat from the gas of the gas engine and discharging waste heat.
The efficient defrosting control method is applied to the gas heat pump multi-split air conditioning system, and comprises a refrigerating operation mode, a first heating mode, a second heating mode, an efficient defrosting operation mode, an external unit parallel heating mode and an external unit parallel efficient defrosting operation mode:
in the refrigeration running mode, the gas engine drives the compressor to work, the compressor compresses the gaseous refrigerant in the first temperature and pressure state sucked from the air suction port of the compressor to form the gaseous refrigerant in the third temperature and pressure state and discharges the gaseous refrigerant from the air discharge port of the compressor, the gaseous refrigerant in the third temperature and pressure state enters the outdoor heat exchanger serving as a condenser through the oil separator to be condensed, the liquid refrigerant in the second temperature and pressure state formed after condensation flows through the electronic expansion valve EXV of the indoor heat exchanger to be throttled, depressurized and cooled, the throttled gas-liquid two-phase refrigerant in the first temperature and pressure state is evaporated through the indoor heat exchanger serving as an evaporator to form the gaseous refrigerant in the first temperature and pressure state, and then the gaseous refrigerant in the first temperature and pressure state returns to the air suction port of the compressor along the gas-liquid separator;
in the first heating mode, the gas engine drives the compressor to work, the compressor compresses the gaseous refrigerant in the first temperature and pressure state sucked from the air suction port of the compressor to form the gaseous refrigerant in the third temperature and pressure state and discharges the gaseous refrigerant from the air discharge port of the compressor, then the gaseous refrigerant in the third temperature and pressure state flows through the oil separator to enter the indoor heat exchanger serving as a condenser for condensation, the condensed liquid refrigerant in the second temperature and pressure state flows through the electronic expansion valve EXV1 of the outdoor heat exchanger for throttling, pressure reducing and temperature reducing, the throttled gas-liquid two-phase refrigerant in the first temperature and pressure state is evaporated by the outdoor heat exchanger serving as an evaporator to form the gaseous refrigerant in the first temperature and pressure state, and then the gaseous refrigerant in the first temperature and pressure state returns to the air suction port of the compressor along the gas-liquid separator; meanwhile, the waste heat recovery unit recovers engine cylinder sleeve heat and flue gas waste heat to heat carrier water to obtain hot water;
in the second heating mode, the gas engine drives the compressor to work, the compressor compresses the gaseous refrigerant in the first temperature and pressure state sucked from the air suction port of the compressor to form the gaseous refrigerant in the third temperature and pressure state and discharges the gaseous refrigerant from the air discharge port of the compressor, then the gaseous refrigerant in the third temperature and pressure state flows through the oil separator to enter the indoor heat exchanger serving as a condenser to be condensed, the electronic expansion valve EXV1 is controlled to be closed, the condensed liquid refrigerant in the second temperature and pressure state does not flow through the outdoor heat exchanger any more but flows through the electronic expansion valve EXV2 to be throttled, depressurized and cooled, the throttled gas-liquid two-phase refrigerant in the first temperature and pressure state is evaporated through the refrigerant-water heat exchanger serving as an evaporator to form the gaseous refrigerant in the first temperature and pressure state, then the gaseous refrigerant in the first temperature and pressure state returns to the air suction port of the compressor along the gas-liquid separator, and meanwhile, the waste heat of the cylinder sleeve of the engine and the smoke are recovered by the waste heat recovery unit to the heat carrier water to obtain hot water;
in the high-efficiency defrosting operation mode, the gas engine drives the compressor to work, the compressor compresses a gaseous refrigerant in a first temperature and pressure state sucked from an air suction port of the compressor to form a gaseous refrigerant in a third temperature and pressure state and discharges the gaseous refrigerant from an air discharge port of the compressor, then the gaseous refrigerant in the third temperature and pressure state is divided into two paths through an oil separator, wherein one path is condensed through an indoor unit heat exchanger serving as a condenser through a four-way reversing valve, the other path is condensed through an outdoor unit heat exchanger also serving as the condenser, two paths of condensed liquid refrigerant in a second temperature and pressure state are combined and flow through an electronic expansion valve EXV2 to carry out throttling, pressure reduction and temperature reduction, the throttled gas-liquid two-phase refrigerant in the first temperature and pressure state firstly carries out primary evaporation and heat absorption through a refrigerant-water heat exchanger serving as an evaporator, and the gas-liquid two-phase refrigerant in the first temperature and pressure state which is not completely evaporated continues to flow through a heat storage device serving as the evaporator to carry out secondary evaporation and heat absorption, then the gaseous refrigerant in the first temperature and pressure state formed after evaporation returns to the suction port of the compressor along the gas-liquid separator; meanwhile, the waste heat recovery unit recovers engine cylinder sleeve heat and flue gas waste heat to heat carrier water to obtain hot water;
under the parallel heating mode of the outdoor units, the two gas heat pump air-conditioning systems are used in parallel, the two air-conditioning systems respectively use respective gas engines to drive the compressors to work, the compressors of the two air-conditioning systems compress the gaseous refrigerant in the first temperature-pressure state sucked from the air suction ports of the compressors to form the gaseous refrigerant in the third temperature-pressure state and discharge the gaseous refrigerant from the air exhaust ports of the compressors, then the gaseous refrigerant in the third temperature-pressure state of the two air-conditioning systems flows through respective oil separators and then is converged along air pipes of the respective air-conditioning systems to enter the indoor heat exchangers serving as condensers together for condensation, the condensed liquid refrigerant in the second temperature-pressure state flows through electronic expansion valves EXV1 of the two outdoor unit heat exchangers for throttling, pressure reduction and temperature reduction, the throttled gas-liquid two-phase refrigerant in the first temperature-pressure state is evaporated through the outdoor unit heat exchangers serving as evaporators to form the gaseous refrigerant in the first temperature-pressure state, then the gaseous refrigerant in the first temperature and pressure state returns to the corresponding air suction port of the compressor along the respective gas-liquid separator;
in the outdoor unit parallel connection high-efficiency defrosting operation mode, two gas heat pump air-conditioning systems are used in parallel and are respectively in a high-efficiency defrosting operation mode and a first heating mode, for the air-conditioning system in the high-efficiency defrosting mode, a compressor compresses a gaseous refrigerant in a first temperature and pressure state sucked from an air suction port of the compressor to form a gaseous refrigerant in a third temperature and pressure state and discharges the gaseous refrigerant from an air exhaust port of the compressor, and then the gaseous refrigerant in the third temperature and pressure state flows through an oil separator to be divided into two paths, wherein one path of the gaseous refrigerant passes through a four-way reversing valve and then is converged with a refrigerant of the other air-conditioning system, and then the gaseous refrigerant is condensed by an indoor unit heat exchanger serving as a condenser, and the other path of the gaseous refrigerant flows through an outdoor unit heat exchanger also serving as a condenser to be condensed; for the air-conditioning system in the first heating mode, the compressor compresses the gaseous refrigerant in the first temperature and pressure state sucked from the air suction port of the compressor to form the gaseous refrigerant in the third temperature and pressure state, and the gaseous refrigerant is discharged from the air discharge port of the compressor, and the gaseous refrigerant in the third temperature and pressure state flows out of the oil separator and then is converged with the gaseous refrigerant in the third temperature and pressure state of the other air-conditioning system to enter the heat exchanger of the indoor unit for condensation; the liquid refrigerant in the second temperature and pressure state after being condensed by the indoor machine heat exchanger is divided into two paths, one path flows to an outdoor machine heat exchanger of the air conditioning system in the first heating mode, the other path flows to a refrigerant-water heat exchanger of the air conditioning system in the high-efficiency defrosting mode, wherein,
in the outdoor unit heat exchanger of the air conditioning system in the first heating mode, throttling, cooling and depressurizing are carried out through an electronic expansion valve EXV1, the throttled gas-liquid two-phase refrigerant in the first temperature and pressure state is evaporated and absorbs heat through the outdoor unit heat exchanger serving as an evaporator, and then the evaporated gas-liquid refrigerant forming the first temperature and pressure state returns to the air suction port of the compressor along the gas-liquid separator;
in the refrigerant-water heat exchanger of the air conditioning system in the efficient defrosting mode, the refrigerant is firstly converged with a liquid refrigerant in a second temperature and pressure state condensed by an outdoor unit heat exchanger, throttling, cooling and pressure reduction are firstly carried out by an electronic expansion valve EXV2, the throttled gas-liquid two-phase refrigerant in a first temperature and pressure state is firstly subjected to primary evaporation and heat absorption by the refrigerant-water heat exchanger serving as an evaporator, the gas-liquid two-phase refrigerant in the first temperature and pressure state which is not completely evaporated continuously flows through a heat storage device serving as the evaporator to be subjected to secondary evaporation and heat absorption, and then the evaporated gas refrigerant in the first temperature and pressure state returns to an air suction port of a compressor along a gas-liquid separator.
Compared with the prior art, the invention has the beneficial effects that: the invention provides a novel GHP air conditioning system and a control method thereof, aiming at the problems of insufficient heating capacity, low air outlet temperature, long defrosting time and possible incomplete defrosting during defrosting of an EHP multi-split air conditioning system, and the problems of long defrosting time and low heating capacity of a common GHP multi-split air conditioning system which influence the comfortable experience of users.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present application, and it is obvious for those skilled in the art that other drawings can be obtained according to these drawings without creative efforts.
FIG. 1 is a diagram of a gas heat pump system with a heat storage device according to an embodiment of the present invention;
FIG. 2 is a diagram of a cooling operation mode of a gas heat pump system with a heat storage device according to an embodiment of the present invention;
FIG. 3 is a diagram of a normal heating operation mode of the gas heat pump system with the heat storage device according to the embodiment of the invention;
FIG. 4 is a heating operation mode diagram of a gas heat pump system with a heat storage device in a cold region according to an embodiment of the invention;
FIG. 5 is a schematic diagram of an efficient defrosting operation mode of the gas heat pump system with the heat storage device in the embodiment of the invention;
FIG. 6 is a diagram illustrating a common heating operation mode in which two gas heat pump outdoor units with heat storage devices are connected in parallel according to an embodiment of the present invention;
fig. 7 is a diagram of an efficient defrosting mode of two gas heat pump outdoor units connected in parallel with an outdoor unit 01 according to an embodiment of the present invention;
fig. 8 is a diagram of an efficient defrosting mode of two gas heat pump outdoor units connected in parallel with an outdoor unit 02 according to an embodiment of the present invention;
FIG. 9 is a flow chart of an efficient defrosting operation mode of a single gas heat pump external unit system with a heat storage device according to an embodiment of the invention;
fig. 10 is a flow chart of an alternate efficient defrosting operation mode of a parallel system of two gas heat pump external units with a heat storage device according to an embodiment of the invention.
Wherein: 1. a compressor; 2. an oil separator; 3. an outdoor heat exchanger; 4. an indoor unit heat exchanger; 5. a gas-liquid separator; 6. a gas engine; 7. a heat storage device; 8. a refrigerant-water heat exchanger; 9. an engine cylinder liner; 10. a first heat recovery unit; 11. a flue gas waste heat recoverer.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present application, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.
Example (b):
it should be noted that the terms "first," "second," and the like in the description and claims of the present invention and in the drawings described above are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used is interchangeable under appropriate circumstances such that the embodiments of the invention described herein are capable of operation in sequences other than those illustrated or described herein. Furthermore, the terms "comprises," "comprising," and any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed, but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.
It will be understood that the terms "central," "longitudinal," "transverse," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in an orientation or positional relationship indicated in the drawings for convenience and simplicity of description only and do not indicate or imply that the device or element so referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus should not be considered as limiting the invention.
In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise. Furthermore, unless expressly stated or limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, as they may be fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In the present invention, unless otherwise expressly stated or limited, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through an intermediate. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.
Referring to fig. 1 to 10, fig. 1 is a diagram of a gas heat pump system with a heat storage device according to an embodiment of the present invention; FIG. 2 is a diagram of a cooling operation mode of a gas heat pump system with a heat storage device according to an embodiment of the present invention; FIG. 3 is a diagram of a normal heating operation mode of the gas heat pump system with the heat storage device according to the embodiment of the invention; FIG. 4 is a heating operation mode diagram of a gas heat pump system with a heat storage device in a cold region according to an embodiment of the invention; FIG. 5 is a schematic diagram of an efficient defrosting operation mode of the gas heat pump system with the heat storage device in the embodiment of the invention; FIG. 6 is a diagram illustrating a common heating operation mode in which two gas heat pump outdoor units with heat storage devices are connected in parallel according to an embodiment of the present invention; fig. 7 is a diagram of an efficient defrosting mode of two gas heat pump outdoor units connected in parallel with an outdoor unit 01 according to an embodiment of the present invention; fig. 8 is a diagram of an efficient defrosting mode of two gas heat pump outdoor units connected in parallel with an outdoor unit 02 according to an embodiment of the present invention; FIG. 9 is a flow chart of an efficient defrosting operation mode of a single gas heat pump external unit system with a heat storage device according to an embodiment of the invention; fig. 10 is a flow chart of an alternate efficient defrosting operation mode of a parallel system of two gas heat pump external units with a heat storage device according to an embodiment of the invention.
Referring to fig. 1, a gas heat pump multi-split air conditioning system includes a power unit, a heat pump cycle unit, a waste heat recovery unit, and in some embodiments, a controller unit, where after a gas (including natural gas, liquefied petroleum gas, coal gas, or biogas, etc.) is fed into a gas engine 6 (internal combustion engine) to be combusted, a part of the released heat energy is converted into mechanical energy to drive a compressor 1 of the heat pump system, and the rest of the heat energy is displayed in the form of waste heat (including flue gas waste heat, cylinder cooling water, and heat taken away by engine oil), and the waste heat can be recovered by adding a related waste heat recovery system. Wherein the power unit is a gas engine 6 providing a power source; the controller unit consists of various sensors and a controller body; the heat pump circulating unit comprises a compressor 1, a condenser, an evaporator, a throttling device and the like; the waste heat recovery system unit comprises a heat storage device 7, an engine cylinder sleeve 9, a flue gas waste heat recoverer 11 and the like.
The heat pump circulation unit comprises a compressor 1, an oil separator 2, a four-way valve, an outdoor heat exchanger 3, an indoor heat exchanger 4, a throttling device and a gas-liquid separator 5, wherein an exhaust port of the compressor 1 is communicated with an inlet of the oil separator 2, a first outlet of the oil separator 2 is connected into the four-way valve, a left port of the outdoor heat exchanger 3 is connected into the four-way valve, a right port of the outdoor heat exchanger 3 is communicated with an upper port of the indoor heat exchanger 4, a second outlet of the oil separator 2 is connected to an air suction port of the compressor 1, a lower port of the indoor heat exchanger 4 is connected into the four-way valve, an inlet of the gas-liquid separator 5 is connected into the four-way valve, and an outlet of the gas-liquid separator 5 is connected to the air suction port of the compressor 1; the power unit comprises a gas engine 6 for driving the compressor 1; the waste heat recovery unit comprises a heat storage device 7 and a refrigerant-water heat exchanger 8, wherein the right port of the refrigerant-water heat exchanger 8 is connected to the left port of the outdoor heat exchanger 3 and the upper port of the indoor heat exchanger 4 through two independent pipelines respectively; the left port of the refrigerant-water heat exchanger 8 is connected to the inlet of the gas-liquid separator 5 through two independent pipelines, and one of the pipelines is provided with the heat storage device 7.
As an optional implementation manner, in some embodiments, the waste heat recovery unit further includes an engine cylinder sleeve 9, a first heat recoverer 10, and a flue gas waste heat recoverer 11, wherein the gas engine 6 is connected to the engine cylinder sleeve 9, and a coolant flows out through the engine cylinder sleeve 9 and the first heat recoverer 10, at this time, cold water recovers heat through the first heat recoverer 10 and the flue gas waste heat recoverer 11 to form hot water and is supplied through a plurality of branches.
The working principle of the system is as follows: for a heat pump system, a high-temperature high-pressure gaseous refrigerant formed by compressing a low-temperature low-pressure gaseous refrigerant in the system by a compressor 1 is condensed by a condenser, a condensed high-pressure liquid refrigerant is throttled and depressurized by a throttling device, the throttled low-temperature low-pressure gas-liquid two-phase refrigerant is evaporated into a low-temperature low-pressure gaseous refrigerant by an evaporator, and then the low-temperature low-pressure gaseous refrigerant returns to the compressor 1 and is continuously compressed into a high-temperature high-pressure gaseous refrigerant to be discharged to the condenser, so that complete heat pump system circulation is formed. For the waste heat recovery system, a large amount of heat contained in the cooling water heat recoverer and the flue gas heat recoverer of the gas engine 6 can be recycled, the heat can be recovered into a heat pump system or an external water system for targeted utilization according to requirements, in addition, a heat storage device 7 is added into the system for heat storage during heating, and the stored heat is released when defrosting is required. The heat of the waste heat recovery system can be heated to prepare domestic hot water for use in summer, and the heat pump which operates in the heating mode in winter just recycles the waste heat, so that the heating performance of the whole heat pump system is further improved.
As shown in fig. 2, which is a cooling operation mode diagram of a gas heat pump system with a heat storage device, at this time, a gas engine transmits power to an open-type compressor through a belt, the compressor compresses low-temperature and low-pressure gaseous refrigerants sucked from an air suction port thereof to form high-temperature and high-pressure gaseous refrigerants to be discharged from an air discharge port of the compressor, then the refrigerants flow through an oil separator to enter an outdoor heat exchanger serving as a condenser to be condensed, the condensed medium-temperature and high-pressure liquid refrigerants flow through an indoor unit (the indoor unit heat exchangers in all system diagrams in the present invention are only schematically illustrated and refer to a general name of a plurality of indoor unit heat exchangers) to be throttled, depressurized and cooled, the throttled low-temperature and low-pressure gas-liquid two-phase refrigerants are evaporated through an electronic expansion valve EXV serving as an evaporator to form low-temperature and low-pressure gaseous refrigerants, then the low-temperature and low-pressure gaseous refrigerants return to an air suction port of the compressor along a gas-liquid separator to be further compressed into high-temperature and high-pressure gaseous refrigerants to be discharged from an air discharge port of the compressor, thereby forming a complete heat pump system cycle. At the moment, the waste heat recovery system of the system can recover engine cylinder sleeve heat and smoke waste heat to heat carrier water to obtain hot water, then the hot water is provided for users as domestic hot water, if the hot water is not utilized, the hot water can be directly communicated to a radiator for heat dissipation and discharge, at the moment, the radiator can be arranged near an outdoor unit heat exchanger of the gas heat pump system, and the heat is discharged by utilizing large air volume of an outdoor fan.
As shown in fig. 3, a diagram of a common heating operation mode (i.e., a first heating mode) of a gas heat pump system with a heat storage device is shown, at this time, a gas engine transmits power to an open-type compressor through a belt, the compressor compresses low-temperature and low-pressure gaseous refrigerants sucked from an air suction port of the compressor to form high-temperature and high-pressure gaseous refrigerants, the high-temperature and high-pressure gaseous refrigerants are discharged from an air outlet of the compressor, the refrigerants flow through an oil separator and enter an indoor heat exchanger serving as a condenser to be condensed, the condensed medium-temperature and high-pressure liquid refrigerants flow through an outdoor unit electronic expansion valve EXV1 to be throttled, depressurized and cooled, the throttled low-temperature and low-pressure gas-liquid two-phase refrigerants are evaporated by an outdoor unit serving as an evaporator to form low-temperature and low-pressure gaseous refrigerants, the low-temperature and low-pressure gaseous refrigerants return to the air suction port of the compressor along a gas-liquid separator and then continue to be compressed into high-temperature and discharged from the air outlet of the compressor, thereby forming a complete cycle of the heat pump system. At the moment, a waste heat recovery system of the system can recover engine cylinder sleeve heat and smoke waste heat to heat carrier water to obtain hot water, the recovered heat can be utilized to different places by selectively opening and closing SV5, SV6 and SV7 (which can be opened simultaneously or partially), the hot water can be provided for users to be used as domestic hot water by opening an electromagnetic valve SV7, the heat in the hot water can be recovered to a refrigerant through a refrigerant-water heat exchanger to increase the total heat circularly conveyed by a heat pump so as to greatly improve the heating capacity of an indoor unit, the heat in the hot water can be transferred to a heat storage device to be stored by opening an electromagnetic valve SV5, and the heat is released to be used as an evaporator when an outdoor unit needs defrosting.
As shown in fig. 4, the diagram shows a heating operation mode (i.e., the second heating mode) in a cold area of the gas heat pump system with the heat storage device, where the application scenario is a place with a low outdoor temperature (e.g., the system enters the cold area heating mode when the outdoor ambient temperature is set to be lower than-15 ℃). The gas engine transmits power to the open-type compressor through a belt, the compressor compresses low-temperature and low-pressure gaseous refrigerants sucked from an air suction port of the compressor to form high-temperature and high-pressure gaseous refrigerants to be discharged from an air exhaust port of the compressor, then the refrigerants flow through the oil separator to enter an indoor heat exchanger serving as a condenser to be condensed, the electronic expansion valve EXV1 is controlled to be closed at the moment, the condensed medium-temperature and high-pressure liquid refrigerants do not flow through an outdoor heat exchanger any more, the condensed medium-temperature and high-pressure liquid refrigerants flow through the electronic expansion valve EXV2 to be throttled, depressurized and cooled, the throttled low-temperature and low-pressure gas-liquid two-phase refrigerants are evaporated through a refrigerant-water heat exchanger serving as an evaporator to form low-temperature and low-pressure gaseous refrigerants, then the low-temperature and low-pressure gaseous refrigerants return to the air suction port of the compressor along the gas-liquid separator to be further compressed into high-temperature and high-pressure gaseous refrigerants to be discharged from the air exhaust port of the compressor, and accordingly complete heat pump system circulation is formed. At the moment, the waste heat recovery system of the system can recover engine cylinder sleeve heat and smoke waste heat to heat carrier water to obtain hot water, and then the recovered heat can be utilized to different places by selectively opening and closing SV5, SV6 and SV7 (which can be simultaneously opened or partially opened), and the specific operation is the same as the waste heat recovery and utilization mode shown in fig. 3.
As shown in fig. 5, a high-efficiency defrosting operation mode diagram of the gas heat pump system with the heat storage device is shown. During defrosting, the four-way valve continues to maintain the heating state without switching to the cooling mode, and the whole system operates as follows. The gas engine transmits power to the open-type compressor through a belt, the compressor compresses low-temperature and low-pressure gaseous refrigerants sucked from a suction port of the compressor to form high-temperature and high-pressure gaseous refrigerants, the high-temperature and high-pressure gaseous refrigerants are discharged from a discharge port of the compressor and flow through the oil separator, the refrigerants flow out of the oil separator and then are divided into two paths, one path of the refrigerants are condensed through an indoor unit heat exchanger serving as a condenser along a four-way reversing valve for heating, the other path of the refrigerants flow through an outdoor unit heat exchanger serving as the condenser along an SV3 electromagnetic valve which is controlled to be opened for condensation, and the refrigerants release heat to the outdoor environment through the outdoor unit heat exchanger during the period to enable outdoor unit frost to be layered. The two paths of condensed medium-temperature high-pressure liquid refrigerants are combined and flow through an electronic expansion valve EXV2 to be throttled, depressurized and cooled, the throttled low-temperature low-pressure gas-liquid two-phase refrigerant firstly passes through a refrigerant-water heat exchanger serving as an evaporator to be evaporated and absorbed heat for the first time, the incompletely evaporated low-temperature low-pressure gas-liquid two-phase refrigerant continuously flows through a heat storage device serving as the evaporator along an opened SV8 electromagnetic valve to be evaporated and absorbed heat for the second time, and then the evaporated low-temperature low-pressure gaseous refrigerant returns to a compressor air suction port along a gas-liquid separator and is continuously compressed into a high-temperature high-pressure gaseous refrigerant to be discharged from a compressor exhaust port, so that a complete defrosting operation mode is formed. The waste heat recovery system of the system recovers engine cylinder sleeve heat and smoke waste heat to heat carrier water during defrosting to obtain hot water, the heat storage device releases heat at the moment, SV5 is in a closed state, and SV6 is in an open state because a primary evaporator is used for defrosting by the refrigerant-water heat exchanger, and SV7 is selectively opened according to the requirement of hot water for life of a user. The defrosting method has the remarkable characteristics that the four-way reversing valve is still in a heating state during defrosting, the heating indoor unit continues to ensure the heating state, and the refrigerant-water heat exchanger and the heat storage device are arranged at the moment, so that the heat source at the heat absorption side of the heat pump system is obviously more sufficient compared with the heat source of a common heat pump system, and the sufficient heating quantity of the heating indoor unit can be maintained while high-efficiency defrosting is ensured, so that good user comfort is kept. The control flow of the efficient defrosting operation mode of the single gas heat pump external unit with the heat storage device is specifically shown in fig. 9.
As shown in fig. 6, a diagram of a parallel common heating operation mode of two gas heat pump outdoor units with a heat storage device (i.e., an outdoor unit parallel heating mode) belongs to a multi-outdoor unit parallel mode, the present invention only takes the parallel connection of two gas heat pump outdoor units as an example to schematically illustrate related operation modes such as defrosting, etc., and the idea and method for parallel connection control of three or more gas heat pump outdoor units are similar, and the present invention is not specifically described but should not be construed as limiting the present invention. In the parallel common heating operation mode diagram of the two gas heat pump outdoor units, the respective outdoor units have the same common heating mode as that of a single outdoor unit, and only gas liquid and liquid pipes from gas side stop valves and liquid side stop valves of the two outdoor units are correspondingly converged and connected together to be conveyed to the indoor unit. The parallel connection of the two gas heat pump outdoor units has similar heating operation modes in cold regions, and the respective outdoor unit operation modes are also the same as the heating operation of a single outdoor unit in the cold regions, and the detailed description is omitted here. In fig. 6, the external units 01 and 02 respectively use their respective gas engines to transmit power to their corresponding open-type compressors via belts, the compressors of the two external units compress low-temperature and low-pressure gaseous refrigerants sucked from their respective air inlets to form high-temperature and high-pressure gaseous refrigerants, which are discharged from the compressor air outlets, then the refrigerants of the two external units flow through their respective oil separators and join together along their respective air pipes to enter the indoor heat exchangers of condensers for condensation, the condensed medium-temperature and high-pressure liquid refrigerants flow through the electronic expansion valves EXV1 of the two external units for throttling, depressurizing and cooling, the throttled low-temperature and low-pressure gas-liquid two-phase refrigerants are evaporated by the external units corresponding to the evaporators to form low-temperature and low-pressure gaseous refrigerants, then the low-temperature and low-pressure gaseous refrigerants return to their respective air inlets along their respective gas-liquid separators to be compressed into their corresponding compressor air inlets and then the high-temperature and high-pressure gaseous refrigerants are discharged from their corresponding compressor air outlets, thereby forming a complete heat pump system cycle. At the moment, the waste heat recovery systems of the respective systems can correspondingly recover the heat of the engine cylinder sleeve and the waste heat of the flue gas to heat carrier water to obtain hot water, and then the recovered heat can be utilized to different places by selectively opening and closing SV5, SV6 and SV7 (which can be opened simultaneously or partially). The specific operation is the same as the waste heat recycling mode shown in the common heating mode of a single outdoor unit.
As shown in fig. 7, a high-efficiency defrosting operation mode diagram (i.e., an external unit parallel high-efficiency defrosting operation mode) is shown in which two gas heat pump external units are connected in parallel with an external unit 01 and provided with a heat storage device. At this time, the outer unit 01 is in an efficient defrosting mode, and the outer unit 02 is in a normal common heating mode. For the outdoor unit 01, a gas engine transmits power to a corresponding open-type compressor through a belt, the compressor compresses low-temperature and low-pressure gaseous refrigerants sucked from a suction port to form high-temperature and high-pressure gaseous refrigerants, the high-temperature and high-pressure gaseous refrigerants are discharged from a compressor discharge port pipe and flow through an oil separator, the refrigerants flow out of the oil separator and are divided into two paths, one path of the refrigerants joins with the refrigerants at an air pipe of the outdoor unit 02 along a heating four-way reversing valve and is condensed by an indoor unit heat exchanger serving as a condenser on a subsequent air pipe, the other path of the refrigerants flows through an outdoor unit heat exchanger serving as the condenser along an SV3 electromagnetic valve which is controlled to be opened to be condensed, and heat is released to the outdoor environment through the outdoor unit heat exchanger during the period to enable outdoor unit frost to be layered. For the outdoor unit 02, the gas engine transmits power to the corresponding open-type compressor through a belt, the compressor compresses the low-temperature and low-pressure gaseous refrigerant sucked from the air suction port of the compressor to form high-temperature and high-pressure gaseous refrigerant, the high-temperature and high-pressure gaseous refrigerant is discharged from the air discharge port of the compressor and flows out of the oil separator, and the high-temperature and high-pressure gaseous refrigerant flowing to the air pipe from the outdoor unit 01 is converged together in the subsequent air pipe after the refrigerant is discharged from the oil separator and enters the heat exchanger of the indoor unit for condensation. It can be seen that the whole parallel system is used as the indoor heat exchanger of the condenser and the outdoor heat exchanger of the outdoor unit 01. The medium-temperature high-pressure liquid refrigerant condensed by the indoor unit heat exchanger is divided into two paths: (1) one path of refrigerant flows to an outdoor unit heat exchanger of the outdoor unit 02, is throttled, cooled and depressurized through an electronic expansion valve EXV1 of the outdoor unit 02 before flowing to the outdoor unit heat exchanger of the outdoor unit 02, the throttled low-temperature low-pressure gas-liquid two-phase refrigerant is evaporated and absorbed in the outdoor unit heat exchanger of the outdoor unit 02, and then the evaporated low-temperature low-pressure gaseous refrigerant returns to a compressor suction port of the outdoor unit 02 along a gas-liquid separator and is continuously compressed into a high-temperature high-pressure gaseous refrigerant to be discharged from a compressor exhaust port, so that a complete common heating mode of the outdoor unit 02 is formed; (2) and the other path of refrigerant flows to the refrigerant-water heat exchanger of the outer unit 01, wherein before flowing to the refrigerant-water heat exchanger of the outer unit 01, the path of refrigerant is firstly merged with the medium-temperature high-pressure liquid refrigerant condensed by the outdoor unit heat exchanger of the outer unit 01 and then is throttled, cooled and depressurized through an electronic expansion valve EXV2 of the outer unit 01, the throttled low-temperature low-pressure gas-liquid two-phase refrigerant is firstly subjected to primary evaporation and heat absorption through the refrigerant-water heat exchanger taking the outer unit 01 as an evaporator, the incompletely evaporated low-temperature low-pressure gas-liquid two-phase refrigerant continuously flows through a heat storage device of the outer unit 01 as the evaporator along an opened SV8 electromagnetic valve to be subjected to secondary evaporation and heat absorption, and then the evaporated low-temperature low-pressure gaseous refrigerant returns to a compressor suction port of the outer unit 01 along a gas-liquid separator and then is continuously compressed into high-temperature high-pressure gaseous refrigerant and discharged from a compressor exhaust port, so that a complete defrosting operation mode of the outer unit 01 is formed. For the waste heat recovery system, the waste heat recovery systems of the external unit 01 and the external unit 02 have the same corresponding operation mode as that of the respective single external unit.
For the efficient defrosting operation mode with two gas heat pump outdoor units connected in parallel with the outdoor unit 01 and provided with the heat storage device, the system is provided with an indoor unit heat exchanger and an outdoor unit heat exchanger of the outdoor unit 01 as the parts of the condenser, and is provided with a refrigerant-water heat exchanger of the outdoor unit 01, the heat storage device of the outdoor unit 01 and an outdoor unit heat exchanger of the outdoor unit 02 as the parts of the evaporator. Compared with the common heat pump system single-outdoor unit and multi-outdoor unit parallel defrosting mode, the two gas heat pump outdoor units parallel high-efficiency defrosting operation mode has the remarkable characteristics that the source of heat at the evaporation side is increased, the total amount of heat is obviously increased, and the high-efficiency defrosting can be ensured, and meanwhile, the sufficient heating capacity of the heating indoor unit is maintained, so that the good user comfort is kept. When the defrosting of the two gas heat pump outdoor units connected in parallel with the outdoor unit 01 with the heat storage device is completed, the two gas heat pump outdoor units can alternately enter the efficient defrosting mode of the outdoor unit 02, and the specific operation diagram is shown in fig. 8, at this time, the outdoor unit 02 is in the efficient defrosting mode, and the outdoor unit 01 is in the normal common heating mode. The specific operation flow is similar to that described above with reference to fig. 7, and is not described again here. The specific control flow of the parallel-connection rotation efficient defrosting operation mode of the two gas heat pump external units with the heat storage device is shown in fig. 10.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.
The above embodiments are only for illustrating the technical concept and features of the present invention, and the purpose thereof is to enable those skilled in the art to understand the contents of the present invention and implement the present invention accordingly, and not to limit the protection scope of the present invention accordingly. All equivalent changes or modifications made in accordance with the spirit of the present disclosure are intended to be covered by the scope of the present disclosure.
Claims (4)
1. The efficient defrosting control method is characterized by being applied to a gas heat pump multi-split air conditioning system, and comprises a refrigeration operation mode, a first heating mode, a second heating mode, an efficient defrosting operation mode, an external unit parallel heating mode and an external unit parallel efficient defrosting operation mode:
in the refrigeration running mode, the gas engine drives the compressor to work, the compressor compresses the gaseous refrigerant in the first temperature and pressure state sucked from the air suction port of the compressor to form the gaseous refrigerant in the third temperature and pressure state and discharges the gaseous refrigerant from the air discharge port of the compressor, the gaseous refrigerant in the third temperature and pressure state enters the outdoor heat exchanger serving as a condenser through the oil separator to be condensed, the condensed liquid refrigerant in the second temperature and pressure state flows through the electronic expansion valve EXV of the indoor heat exchanger to be throttled, depressurized and cooled, the throttled gas-liquid two-phase refrigerant in the first temperature and pressure state is evaporated through the indoor heat exchanger serving as an evaporator to form the gaseous refrigerant in the first temperature and pressure state, and then the gaseous refrigerant in the first temperature and pressure state returns to the air suction port of the compressor along the gas-liquid separator;
in the first heating mode, the gas engine drives the compressor to work, the compressor compresses the gaseous refrigerant in the first temperature and pressure state sucked from the air suction port of the compressor to form the gaseous refrigerant in the third temperature and pressure state and discharges the gaseous refrigerant from the air discharge port of the compressor, then the gaseous refrigerant in the third temperature and pressure state flows through the oil separator and enters the indoor heat exchanger serving as a condenser to be condensed, the condensed liquid refrigerant in the second temperature and pressure state flows through the electronic expansion valve EXV1 of the outdoor heat exchanger to be throttled, depressurized and cooled, the throttled gas-liquid two-phase refrigerant in the first temperature and pressure state is evaporated by the outdoor heat exchanger serving as an evaporator to form the gaseous refrigerant in the first temperature and pressure state, and then the gaseous refrigerant in the first temperature and pressure state returns to the air suction port of the compressor along the gas-liquid separator; meanwhile, the waste heat recovery unit recovers engine cylinder sleeve heat and flue gas waste heat to heat carrier water to obtain hot water;
in the second heating mode, the gas engine drives the compressor to work, the compressor compresses the gaseous refrigerant in the first temperature and pressure state sucked from the air suction port of the compressor to form the gaseous refrigerant in the third temperature and pressure state and discharges the gaseous refrigerant from the air discharge port of the compressor, then the gaseous refrigerant in the third temperature and pressure state flows through the oil separator to enter the indoor heat exchanger serving as a condenser to be condensed, the electronic expansion valve EXV1 is controlled to be closed, the condensed liquid refrigerant in the second temperature and pressure state does not flow through the outdoor heat exchanger any more but flows through the electronic expansion valve EXV2 to be throttled, depressurized and cooled, the throttled gas-liquid two-phase refrigerant in the first temperature and pressure state is evaporated through the refrigerant-water heat exchanger serving as an evaporator to form the gaseous refrigerant in the first temperature and pressure state, and then the gaseous refrigerant in the first temperature and pressure state returns to the air suction port of the compressor along the gas-liquid separator, meanwhile, the waste heat recovery unit recovers engine cylinder sleeve heat and flue gas waste heat to heat carrier water to obtain hot water;
in the high-efficiency defrosting operation mode, the gas engine drives the compressor to work, the compressor compresses the gaseous refrigerant in the first temperature and pressure state sucked from the air suction port of the compressor to form the gaseous refrigerant in the third temperature and pressure state and discharges the gaseous refrigerant from the air discharge port of the compressor, then the gaseous refrigerant in the third temperature and pressure state is divided into two paths through the oil separator, wherein one path is condensed by an indoor unit heat exchanger serving as a condenser through a four-way reversing valve, the other path is condensed by an outdoor unit heat exchanger also serving as a condenser, the two paths of condensed liquid refrigerant in the second temperature and pressure state are combined and flow through an electronic expansion valve EXV2 to carry out throttling, pressure reduction and temperature reduction, the throttled gas-liquid two-phase refrigerant in the first temperature and pressure state firstly carries out first evaporation and heat absorption through a refrigerant-water heat exchanger serving as an evaporator, and the gas-liquid two-phase refrigerant in the first temperature and pressure state which is not completely evaporated continuously flows through a heat storage device serving as an evaporator to carry out second evaporation and heat absorption, then the gaseous refrigerant in the first temperature and pressure state formed after evaporation returns to the suction port of the compressor along the gas-liquid separator; meanwhile, the waste heat recovery unit recovers engine cylinder sleeve heat and flue gas waste heat to heat carrier water to obtain hot water;
under the mode that the outdoor units are connected in parallel for heating, the two air-conditioning systems are connected in parallel for use and respectively drive the compressors to work by using respective gas engines, the compressors of the two air-conditioning systems compress the gaseous refrigerant in the first temperature-pressure state sucked from the air suction ports of the compressors to form the gaseous refrigerant in the third temperature-pressure state and discharge the gaseous refrigerant from the air exhaust ports of the compressors, then the gaseous refrigerant in the third temperature-pressure state of the two air-conditioning systems flows through respective oil separators and then is converged along air pipes of the respective air-conditioning systems to enter the indoor heat exchangers serving as condensers together for condensation, the condensed liquid refrigerant in the second temperature-pressure state flows through the electronic expansion valves EXV1 of the two outdoor unit heat exchangers for throttling, pressure reduction and temperature reduction, the throttled gas-liquid two-phase refrigerant in the first temperature-pressure state is evaporated by the outdoor unit heat exchangers serving as evaporators to form the gaseous refrigerant in the first temperature-pressure state, then the gaseous refrigerant in the first temperature and pressure state returns to the corresponding air suction port of the compressor along the respective gas-liquid separator;
in the outdoor unit parallel connection high-efficiency defrosting operation mode, the two air-conditioning systems are used in parallel and are respectively in the high-efficiency defrosting operation mode and the first heating mode, for the air-conditioning system in the high-efficiency defrosting mode, the compressor compresses the gaseous refrigerant in the first temperature-pressure state sucked from the suction port of the compressor to form the gaseous refrigerant in the third temperature-pressure state and discharges the gaseous refrigerant from the exhaust port of the compressor, and then the gaseous refrigerant in the third temperature-pressure state flows through the oil separator to be divided into two paths, wherein one path of the gaseous refrigerant passes through the four-way reversing valve and then is converged with the refrigerant of the other air-conditioning system, and then the gaseous refrigerant is condensed by the indoor unit heat exchanger serving as a condenser, and the other path of the gaseous refrigerant flows through the outdoor unit heat exchanger serving as a condenser to be condensed; for the air-conditioning system in the first heating mode, the compressor compresses the gaseous refrigerant in the first temperature and pressure state sucked from the air suction port of the compressor to form the gaseous refrigerant in the third temperature and pressure state, and the gaseous refrigerant is discharged from the air discharge port of the compressor, and the gaseous refrigerant in the third temperature and pressure state flows out of the oil separator and then is converged with the gaseous refrigerant in the third temperature and pressure state of the other air-conditioning system to enter the heat exchanger of the indoor unit for condensation; the liquid refrigerant in the second temperature and pressure state after being condensed by the indoor machine heat exchanger is divided into two paths, one path flows to an outdoor machine heat exchanger of the air conditioning system in the first heating mode, the other path flows to a refrigerant-water heat exchanger of the air conditioning system in the high-efficiency defrosting mode, wherein,
in the outdoor unit heat exchanger of the air conditioning system in the first heating mode, throttling, cooling and depressurizing are carried out through an electronic expansion valve EXV1, the throttled gas-liquid two-phase refrigerant in the first temperature and pressure state is evaporated and absorbs heat through the outdoor unit heat exchanger serving as an evaporator, and then the evaporated gas-liquid refrigerant forming the first temperature and pressure state returns to the air suction port of the compressor along the gas-liquid separator;
in the refrigerant-water heat exchanger of the air conditioning system in the efficient defrosting mode, the refrigerant is firstly converged with a liquid refrigerant in a second temperature and pressure state condensed by an outdoor unit heat exchanger, throttling, cooling and pressure reduction are firstly carried out by an electronic expansion valve EXV2, the throttled gas-liquid two-phase refrigerant in a first temperature and pressure state is firstly subjected to primary evaporation and heat absorption by the refrigerant-water heat exchanger serving as an evaporator, the gas-liquid two-phase refrigerant in the first temperature and pressure state which is not completely evaporated continuously flows through a heat storage device serving as the evaporator to be subjected to secondary evaporation and heat absorption, and then the evaporated gas refrigerant in the first temperature and pressure state returns to an air suction port of a compressor along a gas-liquid separator.
2. A gas heat pump multi-split air conditioning system using the efficient defrosting control method as set forth in claim 1, the system at least comprising a power unit, a heat pump cycle unit and a waste heat recovery unit,
the heat pump circulating unit comprises a compressor, an oil separator, a four-way valve, an outdoor heat exchanger, an indoor heat exchanger, a throttling device and a gas-liquid separator, wherein an air outlet of the compressor is communicated with an inlet of the oil separator, a first outlet of the oil separator is connected into the four-way valve, a left port of the outdoor heat exchanger is connected into the four-way valve, a right port of the outdoor heat exchanger is communicated with an upper port of the indoor heat exchanger, a second outlet of the oil separator is connected to an air suction port of the compressor, a lower port of the indoor heat exchanger is connected into the four-way valve, an inlet of the gas-liquid separator is connected into the four-way valve, and an outlet of the gas-liquid separator is connected to the air suction port of the compressor;
the power unit comprises a gas engine for driving the compressor;
the waste heat recovery unit comprises a heat storage device and a refrigerant-water heat exchanger, wherein a right port of the refrigerant-water heat exchanger is connected to a left port of the outdoor heat exchanger and an upper port of the indoor heat exchanger through two independent pipelines respectively; the left port of the refrigerant-water heat exchanger is connected to the inlet of the gas-liquid separator through two independent pipelines, and one pipeline is provided with the heat storage device.
3. A gas heat pump multi-split air conditioning system as claimed in claim 2, wherein the waste heat recovery unit further comprises an engine cylinder sleeve, a first heat recoverer, a flue gas waste heat recoverer, wherein,
the gas engine is connected with the engine cylinder sleeve, cooling liquid flows out through the engine cylinder sleeve and the first heat recoverer, and at the moment, cold water is recovered by the first heat recoverer and the flue gas waste heat recoverer to form hot water which is supplied through a plurality of branches.
4. A gas heat pump multi-split air conditioning system as claimed in claim 2, wherein the flue gas of the gas engine passes through the flue gas waste heat recoverer to recover heat and discharge waste heat.
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| CN205619616U (en) * | 2016-05-05 | 2016-10-05 | 广东志高暖通设备股份有限公司 | Multi -split air conditioning system |
| JP2018155456A (en) * | 2017-03-17 | 2018-10-04 | 大阪瓦斯株式会社 | Hybrid heat pump system |
| CN110030763A (en) * | 2019-04-18 | 2019-07-19 | 蓝焰高科（天津）燃气技术有限公司 | Gas engine drives steam compression type Air Resource Heat Pump Unit operation method |
| CN110360767A (en) * | 2019-06-05 | 2019-10-22 | 天津城建大学 | A kind of driving compression heat pump system of flexible gas engine with combustion-compensating device |
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