CN114413512B - Engine-driven air source heat pump - Google Patents
Engine-driven air source heat pump Download PDFInfo
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- CN114413512B CN114413512B CN202210060671.1A CN202210060671A CN114413512B CN 114413512 B CN114413512 B CN 114413512B CN 202210060671 A CN202210060671 A CN 202210060671A CN 114413512 B CN114413512 B CN 114413512B
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- Prior art keywords
- heat exchanger
- flue gas
- engine
- air
- refrigerant
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Links
- 239000003507 refrigerant Substances 0.000 claims abstract description 136
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 claims abstract description 93
- 239000003546 flue gas Substances 0.000 claims abstract description 93
- 239000000779 smoke Substances 0.000 claims abstract description 20
- 239000000498 cooling water Substances 0.000 claims description 66
- 238000005192 partition Methods 0.000 claims description 12
- 238000010438 heat treatment Methods 0.000 claims description 11
- 238000010257 thawing Methods 0.000 claims description 9
- 230000000149 penetrating effect Effects 0.000 claims description 3
- 239000011810 insulating material Substances 0.000 claims description 2
- 239000007789 gas Substances 0.000 description 35
- 239000007788 liquid Substances 0.000 description 18
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 14
- 239000000446 fuel Substances 0.000 description 13
- 238000002485 combustion reaction Methods 0.000 description 11
- MWUXSHHQAYIFBG-UHFFFAOYSA-N nitrogen oxide Inorganic materials O=[N] MWUXSHHQAYIFBG-UHFFFAOYSA-N 0.000 description 9
- 230000008878 coupling Effects 0.000 description 6
- 238000010168 coupling process Methods 0.000 description 6
- 238000005859 coupling reaction Methods 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 238000006386 neutralization reaction Methods 0.000 description 5
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical compound CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 description 4
- 239000003054 catalyst Substances 0.000 description 4
- 230000002093 peripheral effect Effects 0.000 description 4
- 239000002918 waste heat Substances 0.000 description 4
- OKKJLVBELUTLKV-UHFFFAOYSA-N Methanol Chemical compound OC OKKJLVBELUTLKV-UHFFFAOYSA-N 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 3
- 238000001816 cooling Methods 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- 239000002028 Biomass Substances 0.000 description 2
- 230000002528 anti-freeze Effects 0.000 description 2
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 description 2
- 229920001971 elastomer Polymers 0.000 description 2
- 239000001257 hydrogen Substances 0.000 description 2
- 229910052739 hydrogen Inorganic materials 0.000 description 2
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 239000001301 oxygen Substances 0.000 description 2
- 229910052760 oxygen Inorganic materials 0.000 description 2
- 239000001294 propane Substances 0.000 description 2
- 239000000126 substance Substances 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 229910021536 Zeolite Inorganic materials 0.000 description 1
- 239000011358 absorbing material Substances 0.000 description 1
- 230000002378 acidificating effect Effects 0.000 description 1
- RWRIWBAIICGTTQ-UHFFFAOYSA-N anhydrous difluoromethane Natural products FCF RWRIWBAIICGTTQ-UHFFFAOYSA-N 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- HNPSIPDUKPIQMN-UHFFFAOYSA-N dioxosilane;oxo(oxoalumanyloxy)alumane Chemical compound O=[Si]=O.O=[Al]O[Al]=O HNPSIPDUKPIQMN-UHFFFAOYSA-N 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 150000002431 hydrogen Chemical class 0.000 description 1
- 239000012774 insulation material Substances 0.000 description 1
- JEIPFZHSYJVQDO-UHFFFAOYSA-N iron(III) oxide Inorganic materials O=[Fe]O[Fe]=O JEIPFZHSYJVQDO-UHFFFAOYSA-N 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
- 229910052757 nitrogen Inorganic materials 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 229920006395 saturated elastomer Polymers 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 230000001502 supplementing effect Effects 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
- 238000003786 synthesis reaction Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
- 239000010457 zeolite Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/06—Heat pumps characterised by the source of low potential heat
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
-
- 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
- F25B43/003—Filters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
- F25B47/022—Defrosting cycles hot gas defrosting
- F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- 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
Abstract
The present invention provides an engine-driven air source heat pump having the features that it includes: the air cleaner and the internal air inlet are communicated through a first air pipe, the air cleaner and the engine are communicated through a second air pipe, the flue gas refrigerant heat exchanger is provided with a flue gas outlet, the flue gas outlet is connected with the first air pipe or the second air pipe through a bypass pipe, an EGR valve is arranged in the bypass pipe, the flue gas outlet is further connected with a smoke outlet through a second smoke exhaust pipe, and the smoke outlet is arranged outside the second heat exchanger and is higher than a heat exchange part of the second heat exchanger.
Description
Technical Field
The invention belongs to the technical field of heat pumps, and particularly relates to an air source heat pump driven by an engine.
Background
The engine-driven air source heat pump has the characteristics of high efficiency, low running cost and low carbon emission level, and the high-efficiency engine-driven air source heat pump adopting biomass fuel or solar energy to synthesize clean fuel is used for replacing a boiler or cogeneration, so that the fuel consumption can be greatly reduced, the thermocouple can be used, the low-temperature heat supply of communities is realized, and the water and heat loss of a central long heat supply pipeline in northern areas is reduced.
The engine combustion temperature of the air source heat pump driven by the existing engine is high, and the combustion temperature of the engine influences the combustion efficiency, the knocking tendency and the emission temperature of the engine. For an air source heat pump driven by an engine, the combustion temperature in an engine cylinder is higher than the optimal combustion temperature under most working conditions, so that the fuel consumption and the emission of the nitrogen oxides in the flue gas are high. Reducing engine combustion temperature is an effective way to reduce fuel consumption and emissions.
Accordingly, there is a need for an engine-driven air source heat pump that reduces engine combustion temperatures and emissions.
Disclosure of Invention
The present invention has been made to solve the above-described problems, and an object of the present invention is to provide an air source heat pump driven by an engine.
The present invention provides an engine-driven air source heat pump having the features that it includes: the air cleaner and the internal air inlet are communicated through a first air pipe, the air cleaner and the engine are communicated through a second air pipe, the flue gas refrigerant heat exchanger is provided with a flue gas outlet, the flue gas outlet is connected with the first air pipe or the second air pipe through a bypass pipe, an EGR valve is arranged in the bypass pipe, the flue gas outlet is further connected with a smoke outlet through a second smoke exhaust pipe, and the smoke outlet is arranged outside the second heat exchanger and is higher than a heat exchange part of the second heat exchanger.
In the engine-driven air source heat pump provided by the invention, the engine-driven air source heat pump may further have the following characteristics: wherein, inside air inlet is located inside the second heat exchanger, and outside air flows through the second heat exchanger and gets into inside air inlet.
In the engine-driven air source heat pump provided by the invention, the engine-driven air source heat pump may further have the following characteristics: the second heat exchanger comprises a fin coil type heat exchanger and a fan, and the heat exchange part of the second heat exchanger is the fin coil type heat exchanger.
In the engine-driven air source heat pump provided by the invention, the engine-driven air source heat pump may further have the following characteristics: wherein the fin coil heat exchanger is any one of a flat plate type, an L type and a U type.
The engine-driven air source heat pump according to the present invention may further have the feature that it further includes: and the external air inlet comprises a fin side of the fin coil type heat exchanger and a fan, the air source heat pump driven by the engine has a heating mode and a defrosting mode, when in the heating mode, external air is only introduced into the second heat exchanger from the fin side of the fin coil type heat exchanger, and when in the defrosting mode, external air is introduced into the second heat exchanger from the fin side of the fin coil type heat exchanger and the fan.
In the engine-driven air source heat pump provided by the invention, the engine-driven air source heat pump may further have the following characteristics: the engine, the air filter, the compressor, the flue gas cooling water heat exchanger and the flue gas refrigerant heat exchanger are all arranged in the first cavity.
In the engine-driven air source heat pump provided by the invention, the engine-driven air source heat pump may further have the following characteristics: the lower part of the second heat exchanger is provided with a baffle plate, a first air pipe hole is formed in the baffle plate, a first air pipe penetrates through the first air pipe hole, a rain cap is covered on the first air pipe close to the inner air inlet, two sides of the baffle plate are in slope shape, and downward flanging is arranged on the periphery of the baffle plate.
In the engine-driven air source heat pump provided by the invention, the engine-driven air source heat pump may further have the following characteristics: the second smoke exhaust pipeline is positioned below the heat exchange part of the second heat exchanger in the first cavity.
In the engine-driven air source heat pump provided by the invention, the engine-driven air source heat pump may further have the following characteristics: wherein, the inside sound insulation material that has of pasting of first cavity, air cleaner are located the engine top and transversely place.
In the engine-driven air source heat pump provided by the invention, the engine-driven air source heat pump may further have the following characteristics: wherein the second heat exchangers are provided in plurality, and the internal air inlet is provided inside one of the second heat exchangers.
Effects and effects of the invention
According to the engine-driven air source heat pump (hereinafter referred to as a unit) related to the invention, compared with the prior art, the engine-driven air source heat pump has the following gain actions and effects:
The exhaust gas of the engine is cooled and dehumidified by the gas cooling water heat exchanger and the gas refrigerant heat exchanger, and is mixed with air entering the engine through the EGR valve, so that the combustion temperature in the engine cylinder can be greatly reduced. The flue gas flow rate after being cooled by the flue gas cooling water heat exchanger and the flue gas refrigerant heat exchanger is stable, the temperature is lower than that of the flue gas cooled by the traditional water cooling or air cooling, the flue gas can be fully mixed with air to enter the engine, and as the water in the mixed flue gas is mostly removed by the flue gas refrigerant heat exchanger, the air is in an unsaturated state after being mixed into the flue gas, the air filter, the EGR valve and the pipeline through which the air flows are not easy to rust, the rotation speed of the engine is regulated and the flue gas flow regulating valve is regulated and released, the equivalent combustion effect of the engine is ensured, and the nitrogen oxide content in the flue gas exhausted by the engine is low.
In addition, the flue gas heat energy is utilized in a grading way, and the high-grade flue gas waste heat is directly dissipated to cooling water through a flue gas cooling water heat exchanger, so that the direct waste heat is utilized. The low-grade flue gas waste heat containing the latent heat of the water vapor is radiated to the refrigerant through the flue gas refrigerant heat exchanger. The heat exchange temperature difference of the flue gas cooling water heat exchanger and the flue gas refrigerant heat exchanger is large, the heat exchange area is saved, the structure is compact, and the heat exchanger cost is low.
In addition, the position of the smoke outlet is reasonably arranged, so that smoke is not directly blown to the heat exchange part of the second heat exchanger, and the saturated wet smoke is prevented from being strung into the heat exchange part of the second heat exchanger to cause local frosting, so that the heat transfer of the second heat exchanger is deteriorated.
In conclusion, the engine-driven air source heat pump has the advantages of high engine efficiency, full flue gas waste heat recovery, low emission of nitrogen oxides and long service life of a unit.
Drawings
FIG. 1 is an exterior view of an engine-driven air source heat pump in an embodiment of the present invention;
FIG. 2 is a schematic illustration of the connection and flow of the main body portion of an engine-driven air source heat pump in an embodiment of the present invention;
FIG. 3 is a schematic illustration of the connection and flow of the peripheral portion of an engine-driven air source heat pump in an embodiment of the present invention;
FIG. 4 is a cross-sectional view of a second heat exchanger in an embodiment of the invention;
FIG. 5 is a schematic view of the structure of a septum in an embodiment of the present invention;
FIG. 6 is a schematic diagram showing the internal structure of a first chamber according to an embodiment of the present invention;
fig. 7 is a schematic diagram showing an internal structure of the first cavity according to the second embodiment of the present invention.
Description of the drawings: the flue gas cooling water heat exchanger 8, the engine 10, the compressor 12, the intake port 13, the exhaust port 14, the first heat exchanger 15, the first throttle valve 16, the flue gas refrigerant heat exchanger 17, the first pipe 18, the first connection point 19, the second connection point 20, the second throttle valve 21, the second heat exchanger 22, the first flow port 23, the second flow port 24, the third switching valve 27, the first exhaust gas pipe 28, the air supplementing port 29, the oil separator 30, the lubricating oil circuit 31, the dry filter 32, the economizer 33, the first branch 34, the second branch 35, the first refrigerant three-way valve 36, the second refrigerant three-way valve 37, the coupling 38, the common chassis 39, the internal air inlet 71, the rain cover 72, the first air pipe 73, the second air pipe 74, the air cleaner 75, the partition 76, the fin coil heat exchanger 77, the blower 78, the first air pipe hole 79, the bypass pipe 81, the EGR valve 82, the flue gas outlet 83, the second exhaust gas pipe 84, the frame 91, the panel 92, the electronic control unit 93, the first chassis 94, the fuel pipe 96, the exhaust gas pump 97, the exhaust gas pump 138, the water pump 138, the coolant three-way valve 37, the cooling water tank 146, the cooling water pump 144, the cooling water tank 144, the cooling water pump 144, the three-way valve 144, the cooling water pump 144, the cooling water tank and the cooling water pump 144.
Detailed Description
In order to make the technical means, creation features, achievement of objects and effects achieved by the present invention easy to understand, the following embodiments specifically describe an engine-driven air source heat pump of the present invention with reference to the accompanying drawings.
< Example >
FIG. 1 is an exterior view of an engine-driven air source heat pump in an embodiment of the present invention; FIG. 2 is a schematic illustration of the connection and flow of the main body portion of an engine-driven air source heat pump in an embodiment of the present invention; FIG. 3 is a schematic diagram of the connection and flow of the peripheral portion of an engine-driven air source heat pump in an embodiment of the present invention.
As shown in fig. 1 to 3, the present embodiment provides an engine-driven air source heat pump 10000 including a first chamber 1000, a main body portion, and a peripheral portion. The main body portion includes, among other things, the engine 10, the compressor 12, the first heat exchanger 15, the first throttle valve 16, the flue gas refrigerant heat exchanger 17, the first pipe 18, the second throttle valve 21, the second heat exchanger 22, the first flywheel 25, the economizer 33, the first refrigerant three-way valve 36, the second refrigerant three-way valve 37, the coupling 38, the first connecting shaft 61, the second connecting shaft 62, the cooling water refrigerant heat exchanger 149, the outside air inlet (not shown in the drawing), and the inside air inlet. The peripheral portion includes the flue gas cooling water heat exchanger 28, the cooling water pump 138, the thermostat 140, the three-way catalyst 141, the cooling water three-way valve 143, and the radiator 147.
Fig. 4 is a cross-sectional view of a second heat exchanger in an embodiment of the invention.
As shown in fig. 1 and 4, the second heat exchanger 22 and the first chamber 1000 may be disposed up and down or left and right. In this embodiment, the second heat exchanger 22 is located at the upper portion of the first chamber 1000. The second heat exchanger 22 includes a fan 78, a finned coil heat exchanger 77 and a baffle 76.
The first chamber 1000 includes a frame 91, a panel 92, a first chassis 94, and a partition 76.
The baffle 76 is located in the lower portion of the second heat exchanger 22, the baffle 76 is provided with a first air pipe hole 79, the first air pipe 73 penetrates through the first air pipe hole 79, and the outer portion of the first air pipe 73 is sealed with the first air pipe hole 79 by welding or is sealed by rubber plastic, a rubber sealing ring or fire mud, so that the second heat exchanger 22 is separated from the inner portion of the first cavity 100 through the baffle 76, and air and rainwater in the second heat exchanger 22 are not streamed into the first cavity 1000.
The inside air inlet 71 is located inside the second heat exchanger 22, and a rain cap 72 is covered on the first air tube 73 near the inside air inlet 71. The second exhaust duct 84 communicates with the atmosphere through the cavity 1000 or the second heat exchanger 22. In this embodiment, the second exhaust duct 84 is vented to the atmosphere through the second heat exchanger 22 via an exhaust port 130, the exhaust port 130 being located higher than the heat exchanging portion of the fin coil heat exchanger 77.
The second heat exchanger 22 includes at least one fin coil heat exchanger 77 and at least one fan 78. The fin coil heat exchanger 77 is one of a flat plate type, an L-type or a U-type, and the second heat exchanger 22 in this embodiment includes four U-type fin coil heat exchangers 77 and 2 fans 78. The fan 78 may be one of an ac fan or a dc brushless fan, or may be one of an axial fan or a centrifugal fan.
Fig. 5 is a schematic view of the structure of the partition in the embodiment of the present invention.
As shown in fig. 5, both sides of the partition 76 are sloped and the periphery of the partition 76 is provided with a downward flange. The slope and the flanging can be formed by splicing flanging or steel plates. The partition 76 is provided with a first air pipe hole 79, the first air pipe 73 is arranged on the first air pipe hole 79 in a penetrating manner, and the second smoke exhaust pipeline 84 is arranged on the partition 76 in a penetrating manner. In addition, a sound absorbing and insulating material 97 is attached to the lower portion of the partition 76.
FIG. 6 is a schematic diagram showing the internal structure of a first chamber according to an embodiment of the present invention; fig. 7 is a schematic diagram showing an internal structure of the first cavity according to the second embodiment of the present invention.
As shown in fig. 6 and 7, these two figures are actually interior views of the first cavity 1000 without the baffle 76 and the faceplate 92. The engine 10, the air cleaner 75, the compressor 12, the flue gas cooling water heat exchanger 8, the flue gas refrigerant heat exchanger 17, and the first heat exchanger 15 are all disposed within the first cavity 1000.
The air cleaner 75 communicates with the inside air inlet 71 through a first air pipe 73, and the air cleaner 75 communicates with the engine 10 through a second air pipe 74. The air cleaner 75 may further filter air from the interior air inlet 71.
As shown in fig. 2, the flue gas refrigerant heat exchanger 17 is provided with a flue gas outlet 83. The smoke outlet 83 is connected to the first air pipe 73 or the second air pipe 74 through a bypass pipe 81, and in this embodiment, the smoke outlet 83 is connected to the first air pipe 73 through the bypass pipe 81, and an EGR valve 82 is provided in the bypass pipe 81.
The engine 10 and the compressor 12 may be connected by a coupling or step-up gearbox, in this embodiment by a coupling 38. The engine 10 and the compressor 12 are fixed to a common chassis 39, and the common chassis 39 is mounted to a first chassis 94. Engine 10 also has a first exhaust duct 28 capable of exhausting smoke generated during operation of engine 10.
Engine 10 is one of the naturally aspirated or turbocharged forms, and coupling 38 is a double diaphragm coupling. The thermostat 140 is an electronic or mechanical thermostat, and may be an electronically controlled three-way valve or an electronically controlled two-way valve.
The compressor 12 has an intake port 13, an exhaust port 14, and a supply port 29. Refrigerant gas enters through the inlet port 13 and the supply port 29, is compressed, and is discharged through the discharge port 14. The compressor 12 is any one of an open screw compressor, an open magnetic suspension centrifugal compressor or an open scroll compressor, and the refrigerant in the compressor 12 is any one of propane, NH 3, R718, HFC32, HFC134a, HFC407C, HFC a, HFC245fa, HFC507A, HFO1234 ze, HFO1234yf or HFO1234 zf.
An air cleaner 75 is positioned laterally above engine 10.
The outside air inlet includes the fin side of the fin coil heat exchanger 77 and the fan 78.
The engine-driven air source heat pump 10000 provided in the present embodiment has a heating mode and a defrosting mode.
During heating or defrosting (fan on) operation, outside air enters the second heat exchanger 22 through the fin coil heat exchanger 77, and at this time, exchanges heat with the fin coil heat exchanger 77, the temperature is lowered, the engine 10 sucks in low-temperature air inside the second heat exchanger 22 through the inside air inlet 71, and then the low-temperature air flows through the first air pipe 73, the air cleaner 75, the second air pipe 74 into the engine 10, is mixed with fuel from the fuel line 96, power is generated by combustion expansion, high-temperature smoke is generated, and the power is transmitted to the compressor 12 through the engine 10. The high-temperature flue gas flows through the three-way catalyst 141, the flue gas cooling water heat exchanger 8 and the flue gas refrigerant heat exchanger 17 to discharge sensible heat and latent heat in the flue gas to cooling water and refrigerant respectively, and the flue gas flows out through the flue gas outlet 83 and flows out to the atmosphere outside the flue gas outlet 130 through the second flue gas exhaust pipeline 84. Because the engine 10 is operated at partial load, the EGR valve is opened during partial load operation, and part of the flue gas is mixed with the air in the first air pipe 73 pipe through the bypass pipe 81, and the air mixed with the flue gas flows back to the engine 10, thereby reducing the temperature of the flue gas discharged by the engine 10 and reducing the emission of NOx and the like.
During defrost operation, if the fan is turned off, air enters the interior of the second heat exchanger 22 through the openings in the fin coil 77 or the fan 78, the engine 10 draws in air from the interior of the second heat exchanger 22 through the interior air inlet 71, the air flows through the first air tube 73, the air cleaner 75, the second air tube 74 into the engine 10, mixes with fuel from the fuel line 96, combusts and expands to produce power and produces high temperature flue gas, and the power is transferred through the engine 10 to the compressor 12. The high-temperature flue gas flows through the three-way catalyst 141, the flue gas cooling water heat exchanger 8 and the flue gas refrigerant heat exchanger 17 to discharge sensible heat and latent heat in the flue gas to cooling water and refrigerant respectively, and the flue gas flows out through the flue gas outlet 83 and flows out to the atmosphere outside the flue gas outlet 130 through the second flue gas exhaust pipeline 84. Because the engine 10 is operated at partial load, the EGR valve is opened during partial load operation, and part of the flue gas is mixed with the air in the first air pipe 73 pipe through the bypass pipe 81, and the air mixed with the flue gas flows back to the engine 10, thereby reducing the temperature of the flue gas discharged by the engine 10 and reducing the emission of NOx and the like.
The second smoke evacuation duct 84 passes under the fins of the fin coil heat exchanger 77 in the first cavity 1000 and the smoke in the second smoke evacuation duct 84 heats the partition 76 such that the partition 76 maintains a zero upper temperature in the ice prone region under the fins of the fin coil heat exchanger 77.
In this embodiment, the fuel in the fuel line 96 is a gas or liquid clean fuel, such as natural gas, biomass gas, hydrogen-containing synthesis gas, hydrogen, methanol, etc. The first heat exchanger 15 is a shell-and-tube type, plate type, double pipe type, fin coil type, or the like, and if the refrigerant is a combustible refrigerant such as propane, the first heat exchanger 15 is a compact type heat exchanger such as a plate type, double pipe type, fin coil type, or the like.
In the present embodiment, the known technologies such as the provision of the oxygen sensor in the second air pipe 74, the provision of the oxygen sensor in the flue gas line of the engine 10, the pressure sensor, and the equivalent combustion control will not be described in detail.
The first heat exchanger 15 is for heat supply and has a first refrigerant inlet and a first refrigerant outlet, the first refrigerant inlet being in communication with the exhaust port 14. The heat supply mode of the first heat exchanger 15 is hot water heat supply or hot air heat supply.
The flue gas refrigerant heat exchanger 17 is disposed in the first exhaust duct 28, and refrigerant absorbs heat from the flue gas in the first exhaust duct 28 of the engine 10 to evaporate. The refrigerant in the cooling water refrigerant heat exchanger 149 absorbs heat from the cooling water to evaporate. The cooling water is water or antifreeze. The cooling water refrigerant heat exchanger 149 is connected in series or in parallel with the refrigerant side of the flue gas refrigerant heat exchanger 17. In the present embodiment, the cooling water refrigerant heat exchanger 149 is connected in series with the refrigerant side of the flue gas refrigerant heat exchanger 17, and the cooling water is an antifreeze solution. The cooling water refrigerant heat exchanger 149 has a cooling water inlet a and a cooling water outlet b.
The flue gas refrigerant heat exchanger 17 has a second refrigerant inlet and a second refrigerant outlet, the second refrigerant inlet is connected to the first refrigerant outlet through the first throttle valve 16, the second refrigerant outlet is connected to the refrigerant side of the cooling water refrigerant heat exchanger 149 in series, and then is connected to the E2 port of the second refrigerant three-way valve 37, the S2 port of the second refrigerant three-way valve 37 is connected to the suction port 13, and the D1 port of the second refrigerant three-way valve 37 is connected to the air supply port 29. The first throttle valve 16 is an electronic expansion valve.
The first refrigerant outlet is connected to the second refrigerant inlet by a first line 18. The first conduit 18 has a first connection point 19 and a second connection point 20, the second connection point 20 being closer to the flue gas refrigerant heat exchanger 17 than the first connection point 19.
The second heat exchanger 22 has a first flow port 23 and a second flow port 24. The first flow port 23 is connected to the second connection point 20 via the second throttle valve 21 and is also connected to the first connection point 19 via the third switching valve 27. The second flow port 24 is connected to the inlet port 13 through the E1 port of the first three-way refrigerant valve 36, the S1 port of the first three-way refrigerant valve 36 is connected to the outlet port 14, and the D1 port of the first three-way refrigerant valve 36 is connected to the outlet port 14. The second throttle valve 21 is an electronic expansion valve.
The first three-way refrigerant valve 36 is any one of a solenoid valve, an electric butterfly valve, an electric ball valve, and an electric shutoff valve, and the first three-way refrigerant valve 36 may be a single valve or a valve block. The first refrigerant three-way valve 36 may also be configured to function the same by 2 two-way valves. The second refrigerant three-way valve 37 is any one of a solenoid valve, an electric butterfly valve, an electric ball valve, and an electric shutoff valve, and the second refrigerant three-way valve 37 may be a single valve or a valve block. The second refrigerant three-way valve 37 may also be configured to the same function by 2 two-way valves. The third switching valve 27 is any one of a check valve, a solenoid valve, an electric ball valve, or an electric shut-off valve.
As shown in fig. 3, the exhaust gas from the engine 10 flows through the first exhaust duct 28, sequentially enters the gas cooling water heat exchanger 8 and the gas refrigerant heat exchanger 17 through the three-way catalyst 141, releases heat to the cooling water and the refrigerant, and the released gas is discharged through the gas outlet 83, the second gas duct 84 and the gas outlet 130, and the water condensed from the gas enters the neutralization tank 145 through the water condensation port 144. The neutralization tank 145 is provided with a neutralization ball 146, the neutralization ball 146 is zeolite substance, the acidic substances containing nitrogen in the condensate are neutralized, the neutralized condensate is discharged through an overflow port of the neutralization tank 145, and the condensate can be discharged through a drain valve 142 during maintenance.
The first heat exchanger 15 and the radiator 147 are connected in series or in parallel. In this embodiment, the first heat exchanger 15 and the radiator 147 are connected in series, and hot water or hot air sequentially enters the first heat exchanger 15 and the radiator 147 to be heated.
The cooling water three-way valve 143 has an M port, an N port, and a P port. The M port is connected with the thermostat 140, the N port is connected with the cooling water inlet a, and the P port is connected with the cooling water inlet of the radiator 147. The cooling water outlet b is connected between the P port and the cooling water inlet port of the radiator 147.
The cooling water is pressurized by the cooling water pump 138, flows through the flue gas cooling water heat exchanger 8, absorbs heat in the flue gas, flows through a cylinder sleeve of the engine 10, heats up, and enters the thermostat 140. When the temperature of the cooling water entering the thermostat 140 is low, the cooling water directly flows back to the cooling water pump 138; when the temperature of the cooling water entering the thermostat 140 is high, the cooling water flows through the cooling water three-way valve 143 in whole or in part. The cooling water leaving the three-way valve 143 flows through the radiator 147 in the heating mode or the cooling and heating mode and then flows back to the cooling water pump 138; if the heat exchange capacity of the flue gas refrigerant heat exchanger 17 is insufficient to share the frostless requirement of the second heat exchanger 22 in the heating mode, the port P and the port N circulate simultaneously, the cooling water refrigerant heat exchanger 149 exchanges heat to ensure frostless operation of the second heat exchanger 22, cooling water flows through the radiator 147 and then flows back to the cooling water pump 138, and in the defrosting mode flows through the cooling water refrigerant heat exchanger 149 and the radiator 147 and then flows back to the cooling water pump. An expansion water tank 139 is arranged in the inlet pipeline of the cooling water pump 138, and the expansion water tank 139 is used for adding cooling water and setting pressure to the inlet of the cooling water pump 138.
The flue gas refrigerant heat exchanger 17 is any one of a fin coil heat exchanger, a plate-fin heat exchanger, a plate-shell heat exchanger and a double-pipe heat exchanger, and the flue gas cooling water heat exchanger 8 is any one of a fin coil heat exchanger, a plate-fin heat exchanger, a plate-shell heat exchanger and a double-pipe heat exchanger. The flue gas refrigerant heat exchanger 17 is made of stainless steel.
The specific working process of the engine-driven air source heat pump 10000 provided in this embodiment is as follows:
As shown in fig. 2, in the heating mode, if the air flowing through the second heat exchanger 22 is in the non-frosting zone: the port E1 and the port S1 of the first refrigerant three-way valve 36 are communicated, the port E2 and the port D2 of the second refrigerant three-way valve 37 are communicated, the third switching valve 27 is closed, and the first throttle valve 16 and the second throttle valve 21 are normally adjusted. The engine 10 compresses the refrigerant gas and discharges the compressed refrigerant gas to the first refrigerant inlet through the transmission 11, and the compressed refrigerant gas enters the first heat exchanger 15, and the refrigerant gas is condensed by heat release in the first heat exchanger 15 to become refrigerant liquid. The refrigerant liquid discharged from the first refrigerant outlet of the first heat exchanger 15 passes through the first pipe 18 and the first connection point 19, is split into two paths at the second connection point 20, and enters the first branch 34 and the second branch 35. Wherein the first branch 34 is fitted with a second throttle valve 21 and the second branch 35 is fitted with a first throttle valve 16. The refrigerant in the second branch 35 is converted into a gas-liquid two-phase refrigerant by the first throttle valve 16, enters the economizer 33 and the flue gas refrigerant heat exchanger 17 to absorb heat and evaporate, flows through the cold water refrigerant heat exchanger 149, flows through the ports E2 and D2 of the second refrigerant three-way valve, and returns to the compressor 12 through the gas-supplementing port 29. The refrigerant liquid in the first branch 34 is converted into a gas-liquid two-phase refrigerant through the second throttle valve 21, then enters the second heat exchanger 22 through the first flow port 23 to absorb heat and evaporate, is converted into refrigerant gas, then passes through the E1 port and the S1 port of the first refrigerant three-way valve 36, and returns to the compressor 12 through the air suction port 13.
In the heating mode, if the air flowing through the second heat exchanger 22 is in the frosting zone: the port E1 and the port S1 of the first refrigerant three-way valve 36 are communicated, the port E2 and the port S2 of the second refrigerant three-way valve 37 are communicated, the third switching valve 27 is closed, and the first throttle valve 16 and the second throttle valve 21 are normally adjusted. The engine 10 compresses the refrigerant gas and discharges the compressed refrigerant gas to the first refrigerant inlet through the transmission 11, and the compressed refrigerant gas enters the first heat exchanger 15, and the refrigerant gas is condensed by heat release in the first heat exchanger 15 to become refrigerant liquid. The refrigerant liquid discharged from the first refrigerant outlet of the first heat exchanger 15 passes through the first pipe 18 and the first connection point 19, is split into two paths at the second connection point 20, and enters the first branch 34 and the second branch 35. The refrigerant in the second branch 35 is converted into gas-liquid two-phase refrigerant through the first throttle valve 16, and then enters the economizer 33 and the flue gas refrigerant heat exchanger 17 to absorb heat and evaporate; if necessary, the refrigerant is also sucked into the cooling water refrigerant heat exchanger 149 and evaporated, and the sucked refrigerant flows through the ports E2 and S2 of the second refrigerant three-way valve. The refrigerant liquid in the first branch 34 is converted into a gas-liquid two-phase refrigerant through the second throttle valve 21, then enters the second heat exchanger 22 through the first flow port 23 to absorb heat and evaporate, and is converted into refrigerant gas, and then passes through the E1 port and the S1 port of the first refrigerant three-way valve 36. The two-way refrigerant flowing out of the S1 port and the S2 port is collected and returned to the compressor 12 through the suction port 13.
In the defrosting mode, the D1 and E1 ports of the first three-way refrigerant valve 36 are communicated, the E2 and S2 ports of the second three-way refrigerant valve 37 are communicated, the third switching valve 27 is opened, the first throttle valve 16 is normally adjusted, and the second throttle valve 21 is closed. The engine 10 drives the compressor 12 through the transmission device 11 to compress the refrigerant gas and then divide the refrigerant gas into two paths, wherein one path enters the first heat exchanger 15 through the first refrigerant inlet, the refrigerant gas releases heat in the first heat exchanger 15, and is condensed into refrigerant liquid, and the refrigerant liquid is discharged from the first refrigerant outlet; after the other path of refrigerant gas flows into the second heat exchanger 22 through the ports D1 and E1 of the first refrigerant three-way valve 36 and the second flow port 24, the refrigerant gas condenses into refrigerant liquid, so that heat is released to the surface frost layer of the second heat exchanger 22 for defrosting, then the refrigerant liquid flows out from the first flow port 23, passes through the third switching valve 27, and then the two paths of refrigerant liquid are converged at the first connecting point 19. The collected refrigerant liquid flows into the second branch 35, is converted into a gas-liquid two-phase refrigerant by the first throttle valve 16, flows through the economizer 33, then enters the flue gas refrigerant heat exchanger 17 and the cooling water refrigerant heat exchanger 149, absorbs heat and evaporates, is converted into refrigerant gas, and returns to the compressor 12 through the suction port 13.
The above embodiments are preferred examples of the present invention, and are not intended to limit the scope of the present invention. In addition, it will be understood by those skilled in the art that the present invention is not limited to the embodiments described above, and that many variations and modifications are possible in light of the teachings of the invention, which variations and modifications are within the scope of the invention as claimed. The scope of the invention is defined by the appended claims and equivalents thereof.
For example, in the above embodiment, the number of the second heat exchangers is one, and in actual use, the number of the second heat exchangers may be plural, and in this case, the internal air inlet may be provided only inside one of the second heat exchangers.
Claims (7)
1. An engine-driven air source heat pump, comprising:
An engine, a compressor, a flue gas cooling water heat exchanger, a flue gas refrigerant heat exchanger, a first heat exchanger, a second heat exchanger, an air filter, an internal air inlet, an external air inlet and a first cavity,
Wherein the air cleaner communicates with the internal air inlet through a first air pipe, the air cleaner communicates with the engine through a second air pipe,
The flue gas refrigerant heat exchanger is provided with a flue gas outlet, the flue gas outlet is connected with the first air pipe or the second air pipe through a bypass pipe, an EGR valve is arranged in the bypass pipe,
The flue gas outlet is also connected with a flue gas outlet through a second flue gas pipeline, the flue gas outlet is arranged outside the second heat exchanger and is higher than the heat exchange part of the second heat exchanger,
The high-temperature flue gas flows through the flue gas cooling water heat exchanger and the flue gas refrigerant heat exchanger to discharge sensible heat and latent heat in the flue gas to cooling water and refrigerant respectively, and then flows to the smoke outlet and the bypass pipe through the flue gas outlet,
The internal air inlet is positioned inside the second heat exchanger, and the external air flows through the second heat exchanger and then enters the internal air inlet,
The second heat exchanger comprises a fin coil type heat exchanger and a fan, the heat exchange part of the second heat exchanger is the fin coil type heat exchanger,
The outside air inlet includes a fin side of the fin coil heat exchanger and the blower,
The engine-driven air source heat pump has a heating mode and a defrosting mode,
In the heating mode, the air outside is only introduced into the second heat exchanger from the fin side of the fin coil heat exchanger,
In the defrosting mode, the air outside is introduced into the second heat exchanger from the fin side of the fin coil heat exchanger and the fan.
2. The engine-driven air source heat pump of claim 1 wherein:
Wherein, the fin coil heat exchanger is any one of a flat plate type, an L type and a U type.
3. The engine-driven air source heat pump of claim 1 wherein:
The engine, the air filter, the compressor, the flue gas cooling water heat exchanger and the flue gas refrigerant heat exchanger are all arranged in the first cavity.
4. The engine-driven air source heat pump of claim 1 wherein:
wherein the lower part of the second heat exchanger is provided with a baffle plate, a first air pipe hole is arranged on the baffle plate, a first air pipe is arranged on the first air pipe hole in a penetrating way, a rain cap is covered on the first air pipe close to the internal air inlet,
The two sides of the partition board are slope-shaped, and the periphery of the partition board is provided with downward flanging.
5. The engine-driven air source heat pump of claim 1 wherein:
Wherein the second smoke exhaust duct passes below the heat exchange portion of the second heat exchanger in the first cavity.
6. The engine-driven air source heat pump of claim 1 wherein:
Wherein, the first cavity is internally stuck with a sound-absorbing heat-insulating material,
The air filter is arranged above the engine transversely.
7. The engine-driven air source heat pump of claim 1 wherein:
wherein the second heat exchanger is arranged in a plurality,
The internal air inlet is disposed inside one of the second heat exchangers.
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| CN202210060671.1A CN114413512B (en) | 2022-01-19 | 2022-01-19 | Engine-driven air source heat pump |
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| CN202210060671.1A CN114413512B (en) | 2022-01-19 | 2022-01-19 | Engine-driven air source heat pump |
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| CN114413512B true CN114413512B (en) | 2024-04-16 |
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Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003232582A (en) * | 2002-02-06 | 2003-08-22 | Sanyo Electric Co Ltd | Air conditioner |
| KR100634809B1 (en) * | 2005-07-12 | 2006-10-16 | 엘지전자 주식회사 | Cogeneration system |
| CN101071050A (en) * | 2007-07-10 | 2007-11-14 | 王诗英 | Improved low temperature heat pipe heat exchanger |
| CN101520210A (en) * | 2008-02-29 | 2009-09-02 | 日立空调·家用电器株式会社 | Indoor built-in type heat source unit |
| CN103867335A (en) * | 2013-03-08 | 2014-06-18 | 摩尔动力(北京)技术股份有限公司 | External-combustion working medium heater |
| CN106969430A (en) * | 2017-03-27 | 2017-07-21 | 广东美的制冷设备有限公司 | Outdoor unit and air conditioner |
| CN110043953A (en) * | 2019-04-30 | 2019-07-23 | 广东美的制冷设备有限公司 | Air conditioner indoor unit |
| KR20210081034A (en) * | 2019-12-23 | 2021-07-01 | 엘지전자 주식회사 | Method for driving engine |
| CN213687038U (en) * | 2020-07-27 | 2021-07-13 | 深圳市筑梦空间科技有限公司 | Ceiling type air conditioner and ceiling type air conditioning system |
| CN113899106A (en) * | 2021-11-22 | 2022-01-07 | 上海本家空调系统有限公司 | Engine-driven air source heat pump |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11137195B2 (en) * | 2019-03-06 | 2021-10-05 | Ford Global Technologies, Llc | De-icing control in a vehicle heat pump system |
-
2022
- 2022-01-19 CN CN202210060671.1A patent/CN114413512B/en active Active
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003232582A (en) * | 2002-02-06 | 2003-08-22 | Sanyo Electric Co Ltd | Air conditioner |
| KR100634809B1 (en) * | 2005-07-12 | 2006-10-16 | 엘지전자 주식회사 | Cogeneration system |
| CN101071050A (en) * | 2007-07-10 | 2007-11-14 | 王诗英 | Improved low temperature heat pipe heat exchanger |
| CN101520210A (en) * | 2008-02-29 | 2009-09-02 | 日立空调·家用电器株式会社 | Indoor built-in type heat source unit |
| CN103867335A (en) * | 2013-03-08 | 2014-06-18 | 摩尔动力(北京)技术股份有限公司 | External-combustion working medium heater |
| CN106969430A (en) * | 2017-03-27 | 2017-07-21 | 广东美的制冷设备有限公司 | Outdoor unit and air conditioner |
| CN110043953A (en) * | 2019-04-30 | 2019-07-23 | 广东美的制冷设备有限公司 | Air conditioner indoor unit |
| KR20210081034A (en) * | 2019-12-23 | 2021-07-01 | 엘지전자 주식회사 | Method for driving engine |
| CN213687038U (en) * | 2020-07-27 | 2021-07-13 | 深圳市筑梦空间科技有限公司 | Ceiling type air conditioner and ceiling type air conditioning system |
| CN113899106A (en) * | 2021-11-22 | 2022-01-07 | 上海本家空调系统有限公司 | Engine-driven air source heat pump |
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| CN114413512A (en) | 2022-04-29 |
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