CN119196929A - A low ambient temperature gas-electric hybrid driven air source heat pump type hot and cold water unit - Google Patents
A low ambient temperature gas-electric hybrid driven air source heat pump type hot and cold water unit Download PDFInfo
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- CN119196929A CN119196929A CN202411720883.3A CN202411720883A CN119196929A CN 119196929 A CN119196929 A CN 119196929A CN 202411720883 A CN202411720883 A CN 202411720883A CN 119196929 A CN119196929 A CN 119196929A
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 50
- 239000003507 refrigerant Substances 0.000 claims abstract description 43
- 238000011084 recovery Methods 0.000 claims abstract description 35
- 238000005057 refrigeration Methods 0.000 claims abstract description 12
- 230000017525 heat dissipation Effects 0.000 claims abstract description 8
- 230000005540 biological transmission Effects 0.000 claims abstract description 5
- 239000007789 gas Substances 0.000 claims description 45
- 239000000498 cooling water Substances 0.000 claims description 33
- 239000007788 liquid Substances 0.000 claims description 19
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 claims description 12
- 239000003546 flue gas Substances 0.000 claims description 12
- 239000000779 smoke Substances 0.000 claims description 12
- 238000010438 heat treatment Methods 0.000 abstract description 18
- 238000004378 air conditioning Methods 0.000 abstract description 7
- 238000005265 energy consumption Methods 0.000 abstract description 3
- 238000010257 thawing Methods 0.000 abstract description 3
- 239000003570 air Substances 0.000 description 39
- 238000001816 cooling Methods 0.000 description 5
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000005461 lubrication Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
- 239000012080 ambient air Substances 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H4/00—Fluid heaters characterised by the use of heat pumps
- F24H4/02—Water heaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H9/00—Details
- F24H9/0005—Details for water heaters
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/06—Heat pumps characterised by the source of low potential heat
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/26—Disposition of valves, e.g. of on-off valves or flow control valves of fluid flow reversing valves
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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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
-
- 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
- F25B49/022—Compressor control arrangements
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Fluid Mechanics (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
本发明公开了一种低环温气电混合动力驱动的空气源热泵型冷热水机组，涉及空气源热泵空调的技术领域，本发明解决了低温环境下空气源热泵制热能力衰减和除霜能耗高，以及燃气发动机驱动的空调热泵在制冷低负荷时效率低和经济性差的问题。本发明包括燃气发动机，燃气发动机通过传动装置控制连接有制冷剂系统，燃气发动机上设置有热回收回路和散热回路，制冷剂系统包括：开启式压缩机和电动压缩机并联，开启式压缩机和电动压缩机的排气口分别通过单向阀连接有排气合流三通，排气合流三通的另一接口通过管路连接于油分离器的入口，开启式压缩机和电动压缩机的吸气口分别通过管路一和管路二连接有吸气分流三通。
The present invention discloses a low ambient temperature gas-electric hybrid driven air source heat pump type hot and cold water unit, which relates to the technical field of air source heat pump air conditioners. The present invention solves the problems of attenuation of heating capacity of air source heat pumps and high defrosting energy consumption in low temperature environments, as well as low efficiency and poor economy of air conditioning heat pumps driven by gas engines at low refrigeration loads. The present invention includes a gas engine, which is connected to a refrigerant system through a transmission device, and a heat recovery circuit and a heat dissipation circuit are arranged on the gas engine. The refrigerant system includes: an open compressor and an electric compressor are connected in parallel, and the exhaust ports of the open compressor and the electric compressor are respectively connected to an exhaust merging tee through a one-way valve, and the other interface of the exhaust merging tee is connected to the inlet of an oil separator through a pipeline, and the air intake ports of the open compressor and the electric compressor are respectively connected to an air intake splitter tee through pipeline one and pipeline two.
Description
Technical Field
The invention relates to the technical field of air source heat pump air conditioners, in particular to an air source heat pump type cold and hot water unit driven by low-temperature environment gas-electricity hybrid power.
Background
In recent years, electric air source heat pump units have been widely developed and play an important role in refrigerating and heating systems of buildings. However, in the north of the Yangtze river, winter heating is often faced with low temperature capacity decay and frosting problems, which result in a significant increase in energy consumption. In contrast, the air-conditioning heat pump unit driven by the gas engine can recover heat in the engine cylinder sleeve and the smoke, so that the heating capacity can be effectively improved in a low-temperature environment without defrosting, and the air-conditioning heat pump unit has obvious advantages in heating performance compared with an air source heat pump driven by electric power.
However, the air-conditioning heat pump unit driven by the gas engine has lower efficiency in low-load refrigeration, and particularly has lower running cost effectiveness than the electric air source heat pump, particularly the electric variable-frequency air source heat pump under the conditions of higher gas price and larger low-load occupation. Therefore, developing a heat pump system that can maintain high efficiency and economy under different loads and environmental conditions is a critical issue in the development of technology.
Disclosure of Invention
The invention provides an air source heat pump type cold and hot water unit driven by low-temperature gas-electricity hybrid power, which comprises a gas engine, wherein the gas engine is controlled and connected with a refrigerant system through a transmission device, the gas engine is provided with a heat recovery loop and a heat dissipation loop, the refrigerant system comprises an open compressor and an electric compressor which are connected in parallel, exhaust ports of the open compressor and the electric compressor are respectively connected with an exhaust confluence tee joint through a one-way valve, the other port of the exhaust confluence tee joint is connected with an inlet of an oil separator through a pipeline, an air suction port of the open compressor and an air suction port of the electric compressor are respectively connected with an air suction diversion tee joint through a pipeline I and a pipeline II, the other port of the air suction diversion tee joint is connected with an outlet of a gas-liquid separator through a pipeline, the bottoms of the oil separator are respectively provided with an electromagnetic valve and a capillary tube, the other ends of the two branches are respectively connected with a pipeline I and a pipeline II, a first port of a refrigerant-water heat exchanger is connected with a second port of the air heat exchanger through a pipeline III, and the other port of the refrigerant-water heat exchanger is connected with a second port of the air exchanger through a reversing valve.
The invention is further arranged that the D port of the four-way reversing valve is connected with the outlet of the oil separator through a pipeline, and the S port of the four-way reversing valve is connected with the inlet of the gas-liquid separator through a pipeline.
The invention is further characterized in that a main expansion valve is arranged on the third pipeline, a third branch is further arranged on the third pipeline which is close to one side of the refrigerant-water heat exchanger, the third branch is connected to the refrigerant side inlet of the heat recovery heat exchanger through an auxiliary expansion valve, and the refrigerant side outlet of the heat recovery heat exchanger is connected to the fourth pipeline through a pipeline.
The heat recovery circuit is further arranged in the invention, the heat recovery circuit comprises a radiator, a flue gas heat exchanger and a cooling water pump, an outlet of the radiator is connected with an inlet of the cooling water pump through a pipeline five, an outlet of the cooling water pump is connected with a water side inlet of the flue gas heat exchanger through a pipeline, a water side outlet of the flue gas heat exchanger is connected with a cooling water inlet of a gas engine through a pipeline, and a cooling water outlet of the gas engine is connected with a first interface of a split-flow three-way valve through a pipeline.
The heat dissipation loop comprises a radiator, a heat recovery heat exchanger and a split-flow three-way valve, wherein a second interface of the split-flow three-way valve is connected to a water side inlet of the heat recovery heat exchanger through a pipeline, a water side outlet of the heat recovery heat exchanger is connected to a pipeline five through a pipeline, and a third interface of the split-flow three-way valve is connected to an inlet of the radiator through a pipeline.
The invention is further arranged that the gas engine is connected with a smoke outlet through a smoke heat exchanger.
The invention is further arranged that the rated refrigeration capacity range of the electric compressor is 20% -50% of the rated refrigeration capacity of the open-type compressor.
The invention has the beneficial technical effects that the gas-electric hybrid power driving can select the most suitable driving mode under different environment temperatures and load conditions, thereby improving the overall energy efficiency. When the gas engine is stopped at the time of low load cooling, only the electric compressor is used for operation, so that the energy consumption can be reduced. When heating, particularly when the ambient temperature is lower than 5 ℃, the heat release of the gas engine is recovered, so that the attenuation of the heating capacity is remarkably relieved, the heating effect is ensured, and the pollution to the environment is reduced. In addition, the heating capacity is increased through the heat recovery loop, defrosting is not needed, and the heating efficiency is improved. The system can automatically adjust the working mode according to the actual load and the ambient temperature, and has good flexibility and adaptability.
Drawings
Fig. 1 shows a schematic structure of the present invention.
Fig. 2 shows a first unit efficiency map of the present invention.
Fig. 3 shows a second unit efficiency map of the present invention.
Fig. 4 shows a refrigeration efficiency graph of the present invention.
Fig. 5 shows a graph of the heating capacity VS ambient temperature variation of the present invention.
The air-fuel separator comprises the following components of a starting compressor 1, an electric compressor 2, an oil separator 3, an oil separator 4, a gas-liquid separator 5, a refrigerant-water heat exchanger 6, an air heat exchanger 7, a radiator 8, a heat recovery heat exchanger 9, a flue gas heat exchanger 10, a cooling water pump 11, a gas engine 12, a transmission device 13, a capillary tube 14, an exhaust converging tee joint, 15, an air suction splitting tee joint, 16, a four-way reversing valve 17, a main expansion valve 18, an auxiliary expansion valve 19 and a splitting tee joint valve.
Detailed Description
Preferred embodiments of the present invention are described below with reference to fig. 1-5. It should be understood by those skilled in the art that these embodiments are merely for explaining the technical principles of the present invention, and are not intended to limit the scope of the present invention.
The invention provides a low-temperature environment-friendly gas-electric hybrid power driven air source heat pump type cold and hot water unit, which comprises a gas engine 11, wherein the gas engine 11 is controlled and connected with a refrigerant system through a transmission device 12, an open-type compressor 1 is driven by the gas engine 11, an electric compressor 2 is driven by electric power, and the two are arranged in the refrigerant system in a parallel connection mode. The rated refrigerating capacity of the electric compressor 2 is selected within the range of 20% -50% of the rated refrigerating capacity of the open compressor 1, and the check valve can be replaced by a check mechanism at the exhaust ports inside the open compressor 1 and the electric compressor 2.
The refrigerant system comprises an open-type compressor 1 and an electric compressor 2 which are connected in parallel, wherein exhaust ports of the open-type compressor 1 and the electric compressor 2 are respectively connected with an exhaust converging tee joint 14 through one-way valves, and the one-way valves ensure that refrigerant steam can flow only in one direction and prevent backflow. The other port of the exhaust confluence tee 14 is connected to the inlet of the oil separator 3 through a pipeline, the air inlets of the open compressor 1 and the electric compressor 2 are respectively connected with an air suction diversion tee 15 through a pipeline I and a pipeline II, and the air suction diversion tee 15 enables refrigerant liquid to enter the respective compressors after being split. The other interface of the air suction and distribution tee 15 is connected with the outlet of the air-liquid separator 4 through a pipeline, and the air-liquid separator 4 is used for separating air and liquid in the refrigerant, so that the system efficiency is improved.
The bottom of the oil separator 3 is also provided with two branches, the two branches are respectively provided with an electromagnetic valve and a capillary tube 13 in sequence, and the electromagnetic valve and the capillary tube 13 can control the oil return quantity of the compressor. The other ends of the two branches are respectively connected to a first pipeline and a second pipeline, the D port of the four-way reversing valve 16 is connected to the outlet of the oil separator 3 through a pipeline, and the S port of the four-way reversing valve 16 is connected to the inlet of the gas-liquid separator 4 through a pipeline.
The third pipeline is provided with a main expansion valve 17, and the main expansion valve 17 controls the flow of the refrigerant flowing into the refrigerant-water heat exchanger 5 and adjusts the flow of the refrigerant according to the load demand of the system. The main expansion valve 17 is further provided with a third branch on a third line on a side close to the refrigerant-water heat exchanger 5, the third branch being connected to a refrigerant side inlet of the heat recovery heat exchanger 8 through an auxiliary expansion valve 18, the auxiliary expansion valve 18 controlling a flow rate of the refrigerant flowing into the heat recovery heat exchanger 8. The refrigerant side outlet of the heat recovery heat exchanger 8 is connected to a fourth line through a pipe. The heat recovery heat exchanger 8 is used as a second evaporator to recover the heat discharged by the engine, so that the heat supply capacity and the energy efficiency at the low ring temperature are improved.
An air-conditioning water circulation pipeline is arranged in the refrigerant-water heat exchanger 5, and the refrigerant-water heat exchanger 5 is used for performing heat exchange between the refrigerant and air-conditioning water to realize refrigeration or heating. The first port of the refrigerant-water heat exchanger 5 is connected to the first port of the air heat exchanger 6 through a third pipeline, the second port of the refrigerant-water heat exchanger 5 is connected to the E port of the four-way reversing valve 16 through a pipeline, and the C port of the four-way reversing valve 16 is connected to the second port of the air heat exchanger 6 through a pipeline. In the case of cooling, the first port of the refrigerant-water heat exchanger 5 corresponds to an inlet, the second port of the refrigerant-water heat exchanger 5 corresponds to an outlet, the first port of the air heat exchanger 6 corresponds to an outlet, and the second port of the air heat exchanger 6 corresponds to an inlet, and in the case of heating, the first port of the refrigerant-water heat exchanger 5 corresponds to an outlet, the second port of the refrigerant-water heat exchanger 5 corresponds to an inlet, the first port of the air heat exchanger 6 corresponds to an inlet, and the second port of the air heat exchanger 6 corresponds to an outlet, as opposed to the case of cooling.
The gas engine 11 is provided with a heat recovery circuit and a heat radiation circuit, which constitute a power system. The heat recovery loop comprises a radiator 7, a flue gas heat exchanger 9 and a cooling water pump 10, wherein the radiator 7 is used for radiating heat and discharging superfluous heat in the system to the outside. The flue gas heat exchanger 9 recovers the flue gas heat discharged by the gas engine 11, and increases the heating capacity of the system. The cooling water pump 10 circulates cooling water for heat recovery and heat dissipation. The outlet of the radiator 7 is connected with the inlet of the cooling water pump 10 through a pipeline five, the outlet of the cooling water pump 10 is connected with the water side inlet of the flue gas heat exchanger 9 through a pipeline, the water side outlet of the flue gas heat exchanger 9 is connected with the cooling water inlet of the gas engine 11 through a pipeline, and the cooling water outlet of the gas engine 11 is connected with the first interface of the split-flow three-way valve 19 through a pipeline. The split three-way valve 19 controls the flow direction of the cooling water, directing the cooling water to the heat recovery heat exchanger or radiator as required.
The heat dissipation loop comprises a radiator 7, a heat recovery heat exchanger 8 and a split-flow three-way valve 19, wherein a second interface of the split-flow three-way valve 19 is connected to a water side inlet of the heat recovery heat exchanger 8 through a pipeline, a water side outlet of the heat recovery heat exchanger 8 is connected to a pipeline five through a pipeline, and a third interface of the split-flow three-way valve 19 is connected to an inlet of the radiator 7 through a pipeline. For controlling the heat release of the cooling water to the heat recovery heat exchanger 8 or the radiator 7.
The gas engine 11 is connected to a smoke outlet through a smoke heat exchanger 9. The gas engine 11 supplies power, drives the open compressor 1, and generates recoverable heat. The exhaust port discharges smoke generated by combustion of the gas engine 11.
The operation mode during cooling is that the gas engine 11 is stopped at the time of low load cooling, only the electric compressor 2 is started to operate alone, and the high efficiency of the electric compressor 2 is used for replacing the low-efficiency operation of the gas engine 11 at the time of low load, thereby improving the overall energy efficiency. In the intermediate load region, the gas-electric hybrid power operation can be selected, and the open-type compressor 1 can be driven only by the gas engine 11 so as to adapt to different load requirements. In the high-load region, the gas-electric hybrid power operation is adopted, so that the high-efficiency operation of the system is ensured while the high-load requirement of refrigeration is met.
Specifically, the circulation principle of the refrigerant system during refrigeration is that the opening type compressor 1 or the electric compressor 2 discharges the mixed gas of the refrigerant and the refrigerating oil, and the mixed gas enters the oil separator 3 through the one-way valve, and the purpose of the one-way valve is to prevent the exhaust gas of the compressor in the working state from flowing back into the compressor in the stopping state. The refrigerating oil in the oil separator 3 is separated, and the refrigerating oil returned by the first branch and the second branch of the two throttling capillaries 13 arranged at the bottom of the oil separator 3 respectively returns to the first pipeline and the second pipeline at the air suction ports of the open type compressor 1 and the electric compressor 2, and returns to the working compressor together with the air suction refrigerant, so that the lubrication of the compressor is ensured. In addition, after the oil separator 3 separates the frozen oil, purer refrigerant gas enters through the D port of the four-way reversing valve 16, is discharged from the C port of the four-way reversing valve 16, then enters the air heat exchanger 6 to be condensed into liquid by air, the condensed liquid enters the refrigerant-water heat exchanger 5 through the pipeline III, and the main expansion valve 17 on the pipeline III controls the flow of the refrigerant to be matched with the water load of the air conditioner. The liquid refrigerant absorbs the heat of the air conditioner water in the refrigerant-water heat exchanger 5, is gasified, enters the E port of the four-way reversing valve 16 through the pipeline, flows out of the S port and enters the pipeline four. The refrigerant vapor enters the gas-liquid separator 4 after passing through the pipeline IV, then enters the suction diversion tee 15, and then enters the corresponding compressor for recompression through the pipeline I or the pipeline II. The auxiliary expansion valve 18 in the third branch is closed during refrigeration.
The principle of engine cooling water circulation during refrigeration is that cooling water sequentially passes through the gas engine 11 and the smoke heat exchanger 9 under the drive of the cooling water pump 10, absorbs heat of the gas engine 11 cylinder body and smoke, flows to the radiator 7 through the split-flow three-way valve 19 for heat dissipation, and enters the cooling water pump 10 again after the temperature of the cooling water is reduced.
The operation mode during heating is that under the conditions of higher ambient temperature and lower heating requirement, only the electric compressor 2 is started to independently operate so as to meet lower heat load with high efficiency. Conversely, when the ambient temperature falls below 5 ℃, the operation is switched to the open compressor 1 driven by the gas engine 11 to be operated alone. At this time, the split-flow three-way valve 19 adjusts the flow direction of the cooling water to enter the heat recovery heat exchanger 8 to release heat, and the auxiliary expansion valve 18 is opened accordingly, so that the refrigerant flows into the heat recovery heat exchanger 8 to be used as an auxiliary evaporator.
Specifically, the refrigerant circulation principle during heating is that the opening type compressor 1 or the electric compressor 2 discharges the mixed gas of the refrigerant and the refrigerating oil, and the mixed gas enters the oil separator 3 through the one-way valve, and the purpose of the one-way valve is to prevent the exhaust gas of the compressor in the working state from flowing back into the compressor in the stopping state. The refrigerating oil in the oil separator 3 is separated, and the branches of the two throttling capillaries 13 arranged at the bottom of the oil separator 3 return to the first pipeline and the second pipeline at the air suction ports of the open type compressor 1 and the electric compressor 2 respectively, and the returned refrigerating oil and the suction refrigerant return to the working compressor together to ensure the lubrication of the compressors. In addition, after the oil separator 3 separates the frozen oil, purer refrigerant gas enters through the D port of the four-way reversing valve 16, is discharged from the E port of the four-way reversing valve 16, then enters the refrigerant-water heat exchanger 5, and the gaseous refrigerant is liquefied and condensed after being discharged to the air-conditioning water. The condensed refrigerant liquid enters the air heat exchanger 6 through a third pipeline, and a main expansion valve 17 on the third pipeline controls the flow rate of the refrigerant to be matched with the load of the air heat exchanger 6. The liquid refrigerant absorbs heat from the ambient air in the air heat exchanger 6 and evaporates and passes through the line into port C of the four-way reversing valve 16 and then out port S into line four. The refrigerant vapor enters the gas-liquid separator 4 after passing through the pipeline IV, then enters the suction diversion tee 15, and then enters the corresponding compressor for recompression through the pipeline I or the pipeline II. Meanwhile, the liquid refrigerant enters the third branch from the third pipeline, the auxiliary expansion valve 18 controls the flow of the refrigerant flowing into the heat recovery heat exchanger 8 to be matched with the heat of cooling water, and the liquid refrigerant absorbing the heat in the heat recovery heat exchanger 8 is gasified and then enters the fourth pipeline.
The principle of engine cooling water circulation during heating is that cooling water sequentially passes through the gas engine 11 and the smoke heat exchanger 9 under the driving of the cooling water pump 10, absorbs heat of the gas engine 11 cylinder body and smoke, flows to the heat recovery heat exchanger 8 through the split-flow three-way valve 19 to release heat to the refrigerant, and enters the cooling water pump 10 again after the temperature of the cooling water is reduced.
GHP represents a single gas engine driven compressor;
EHP represents a single electrically driven compressor;
ghp+ehp stands for gas-electric hybrid drive compressor.
While the invention has been described with reference to a preferred embodiment, various modifications may be made and equivalents may be substituted for elements thereof without departing from the scope of the invention, and in particular, the technical features set forth in the various embodiments may be combined in any manner so long as there is no structural conflict. The present invention is not limited to the specific embodiments disclosed herein, but encompasses all technical solutions falling within the scope of the claims.
In the description of the present invention, terms such as "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", and the like, which indicate a direction or a positional relationship, are based on the direction or the positional relationship shown in the drawings, are merely for convenience of description, and do not indicate or imply that the apparatus or elements must have a specific orientation, be constructed and operated in a specific orientation, and thus are not to be construed as limiting the present invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In addition, it should be noted that, in the description of the present invention, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, detachably connected, integrally connected, mechanically connected, electrically connected, directly connected, indirectly connected through an intermediate medium, or in communication between two elements. The specific meaning of the above terms in the present invention can be understood by those skilled in the art according to the specific circumstances.
The terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, article, or apparatus/means that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, article, or apparatus/means.
Thus far, the technical solution of the present invention has been described in connection with the preferred embodiments shown in the drawings, but it is easily understood by those skilled in the art that the scope of protection of the present invention is not limited to these specific embodiments. Equivalent modifications and substitutions for related technical features may be made by those skilled in the art without departing from the principles of the present invention, and such modifications and substitutions will fall within the scope of the present invention.
Claims (7)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202411720883.3A CN119196929A (en) | 2024-11-28 | 2024-11-28 | A low ambient temperature gas-electric hybrid driven air source heat pump type hot and cold water unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202411720883.3A CN119196929A (en) | 2024-11-28 | 2024-11-28 | A low ambient temperature gas-electric hybrid driven air source heat pump type hot and cold water unit |
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| CN119196929A true CN119196929A (en) | 2024-12-27 |
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| CN202411720883.3A Pending CN119196929A (en) | 2024-11-28 | 2024-11-28 | A low ambient temperature gas-electric hybrid driven air source heat pump type hot and cold water unit |
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| EP3770531A1 (en) * | 2019-07-25 | 2021-01-27 | Panasonic Intellectual Property Management Co., Ltd. | Air-conditioning apparatus |
| CN116294290A (en) * | 2023-03-27 | 2023-06-23 | 南京天加环境科技有限公司 | Gas heat pump unit for realizing extremely low temperature refrigeration and control method thereof |
| WO2023119865A1 (en) * | 2021-12-22 | 2023-06-29 | パナソニックＩｐマネジメント株式会社 | Air conditioner |
-
2024
- 2024-11-28 CN CN202411720883.3A patent/CN119196929A/en active Pending
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| JPS63243668A (en) * | 1987-03-30 | 1988-10-11 | 株式会社東芝 | Engine drive type air conditioner |
| JP2003056944A (en) * | 2001-08-20 | 2003-02-26 | Mitsubishi Heavy Ind Ltd | Air conditioner |
| JP2003056932A (en) * | 2001-08-20 | 2003-02-26 | Mitsubishi Heavy Ind Ltd | Air conditioner |
| EP3425308A1 (en) * | 2017-07-05 | 2019-01-09 | Panasonic Intellectual Property Management Co., Ltd. | Air conditioning apparatus |
| EP3770531A1 (en) * | 2019-07-25 | 2021-01-27 | Panasonic Intellectual Property Management Co., Ltd. | Air-conditioning apparatus |
| WO2023119865A1 (en) * | 2021-12-22 | 2023-06-29 | パナソニックＩｐマネジメント株式会社 | Air conditioner |
| CN116294290A (en) * | 2023-03-27 | 2023-06-23 | 南京天加环境科技有限公司 | Gas heat pump unit for realizing extremely low temperature refrigeration and control method thereof |
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