CN114413512A - Air source heat pump driven by engine - Google Patents
Air source heat pump driven by engine Download PDFInfo
- Publication number
- CN114413512A CN114413512A CN202210060671.1A CN202210060671A CN114413512A CN 114413512 A CN114413512 A CN 114413512A CN 202210060671 A CN202210060671 A CN 202210060671A CN 114413512 A CN114413512 A CN 114413512A
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- Prior art keywords
- heat exchanger
- air
- engine
- refrigerant
- flue gas
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Links
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- 239000003546 flue gas Substances 0.000 claims abstract description 83
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 claims abstract description 82
- 239000000498 cooling water Substances 0.000 claims abstract description 64
- 239000000779 smoke Substances 0.000 claims description 29
- 238000005192 partition Methods 0.000 claims description 13
- 238000010438 heat treatment Methods 0.000 claims description 12
- 238000010257 thawing Methods 0.000 claims description 7
- 239000011810 insulating material Substances 0.000 claims description 3
- 230000000149 penetrating effect Effects 0.000 claims description 3
- 239000007789 gas Substances 0.000 abstract description 27
- 238000012546 transfer Methods 0.000 abstract description 3
- 238000007599 discharging Methods 0.000 abstract description 2
- 239000003517 fume Substances 0.000 abstract description 2
- 239000007788 liquid Substances 0.000 description 17
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 15
- 239000000446 fuel Substances 0.000 description 13
- 238000002485 combustion reaction Methods 0.000 description 10
- 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 6
- 239000003054 catalyst Substances 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical compound CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 description 4
- 238000001816 cooling Methods 0.000 description 4
- 230000003472 neutralizing effect Effects 0.000 description 4
- 230000002093 peripheral effect Effects 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
- 238000006386 neutralization reaction Methods 0.000 description 3
- 239000002918 waste heat Substances 0.000 description 3
- 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
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 230000005494 condensation Effects 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
- 238000000034 method Methods 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
- 230000002378 acidificating effect Effects 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- RWRIWBAIICGTTQ-UHFFFAOYSA-N anhydrous difluoromethane Natural products FCF RWRIWBAIICGTTQ-UHFFFAOYSA-N 0.000 description 1
- 229910052799 carbon Inorganic materials 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 230000006866 deterioration Effects 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
- 230000009977 dual effect Effects 0.000 description 1
- 150000002431 hydrogen Chemical class 0.000 description 1
- 239000012774 insulation material Substances 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000002156 mixing Methods 0.000 description 1
- 239000003345 natural gas Substances 0.000 description 1
- 229910052757 nitrogen Inorganic materials 0.000 description 1
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- 239000003921 oil Substances 0.000 description 1
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- 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
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- 239000010959 steel Substances 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
- 238000003786 synthesis reaction Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
- 239000010457 zeolite Substances 0.000 description 1
Images
Classifications
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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
- F25B30/02—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 comprising: the engine, the compressor, flue gas cooling water heat exchanger, the flue gas refrigerant heat exchanger, first heat exchanger, the second heat exchanger, air cleaner, inside air inlet and first cavity, wherein, air cleaner passes through first air pipe intercommunication with inside air inlet, air cleaner passes through the second air pipe intercommunication with the engine, flue gas refrigerant heat exchanger has the exhanst gas outlet, the exhanst gas outlet passes through bypass pipe and first air pipe or second air piping connection, be equipped with the EGR valve in the bypass pipe, the exhanst gas outlet still is connected with the exhaust port through the second pipeline of discharging fume, the exhaust port sets up the heat transfer part outside and higher than the second heat exchanger at 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 air source heat pump driven by the engine has the characteristics of high efficiency, low operating cost and low carbon emission level, and the boiler or cogeneration can be replaced by the high-efficiency air source heat pump driven by the engine and adopting biomass fuel or solar energy to synthesize clean fuel, so that not only can the fuel consumption be greatly reduced, but also the heat and power can be decoupled, the low-temperature heat supply of a community can be realized, and the water and heat loss of a centralized long heat supply pipeline in the northern area can be reduced.
The combustion temperature of the engine of the air source heat pump driven by the engine at present is high, and the combustion efficiency, the engine knocking tendency and the emission temperature of the engine are influenced by the combustion 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 smoke nitrogen oxides are high. Reducing engine combustion temperatures 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 problems, and an object of the present invention is to provide an engine-driven air-source heat pump.
The present invention provides an engine-driven air-source heat pump having the features comprising: the engine, the compressor, flue gas cooling water heat exchanger, the flue gas refrigerant heat exchanger, first heat exchanger, the second heat exchanger, air cleaner, inside air inlet and first cavity, wherein, air cleaner passes through first air pipe intercommunication with inside air inlet, air cleaner passes through the second air pipe intercommunication with the engine, flue gas refrigerant heat exchanger has the exhanst gas outlet, the exhanst gas outlet passes through bypass pipe and first air pipe or second air piping connection, be equipped with the EGR valve in the bypass pipe, the exhanst gas outlet still is connected with the exhaust port through the second pipeline of discharging fume, the exhaust port sets up the heat transfer part outside and higher than the second heat exchanger at the second heat exchanger.
The engine-driven air source heat pump according to the present invention may further include: the inside air inlet is positioned inside the second heat exchanger, and outside air enters the inside air inlet after flowing through the second heat exchanger.
The engine-driven air source heat pump according to the present invention may further include: 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.
The engine-driven air source heat pump according to the present invention may further include: the fin coil type 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 include: the air source heat pump driven by the engine has a heating mode and a defrosting mode, during the heating mode, external air is introduced into the second heat exchanger from the fin side of the fin-coil heat exchanger only, and during the defrosting mode, the external air is introduced into the second heat exchanger from the fin side of the fin-coil heat exchanger and the fan.
The engine-driven air source heat pump according to the present invention may further include: 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.
The engine-driven air source heat pump according to the present invention may further include: wherein, second heat exchanger lower part has the baffle, has seted up first air pipe hole on the baffle, and first air pipe wears to establish on first air pipe hole, and first air pipe is close to inside air inlet and is covered with rain-proof cap outward, and the both sides of baffle are slope form, and the baffle is all around to have decurrent turn-ups.
The engine-driven air source heat pump according to the present invention may further include: and the second smoke exhaust pipeline is positioned in the first cavity and passes below the heat exchange part of the second heat exchanger.
The engine-driven air source heat pump according to the present invention may further include: wherein, the sound-absorbing and heat-insulating material is pasted in the first cavity, and the air filter is transversely arranged above the engine.
The engine-driven air source heat pump according to the present invention may further include: wherein the second heat exchanger is provided in plurality, and the inside air inlet is provided inside one of the second heat exchangers.
Action and Effect of the invention
Compared with the prior art, the engine-driven air source heat pump (hereinafter referred to as a unit) has the following gain effects and effects:
the exhaust gas of the engine is cooled and dehumidified by the exhaust gas cooling water heat exchanger and the exhaust gas refrigerant heat exchanger, and is mixed with the air entering the engine through the EGR valve, so that the combustion temperature in the cylinder of the engine can be greatly reduced. The flue gas flow after the cooling of flue gas cooling water heat exchanger and flue gas refrigerant heat exchanger is stable, the temperature is lower than the flue gas temperature of traditional water cooling or air cooling, can get into the engine with the air intensive mixing, and because the moisture has mostly been got rid of by flue gas refrigerant heat exchanger in the flue gas of sneaking into for the air is in the unsaturated state after sneaking into the flue gas, the air cleaner, EGR valve and the pipeline that it flowed through are difficult for the corrosion, the rotational speed regulation of engine and flue gas flow control valve adjustment are releivedly, the equivalent combustion effect of engine has been guaranteed, nitrogen oxide content is low in the flue gas of engine exhaust.
In addition, the grading utilization of the heat energy of the flue gas is realized, and the high-grade flue gas waste heat is directly radiated to cooling water through a flue gas cooling water heat exchanger to be directly 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 flue gas cooling water heat exchanger and the flue gas refrigerant heat exchanger have the advantages of large heat exchange temperature difference, saved heat exchange area, compact structure and low heat exchanger cost.
In addition, the smoke exhaust port is reasonably arranged, so that smoke exhaust cannot be directly blown to the heat exchange part of the second heat exchanger, and therefore partial frosting caused by the fact that saturated wet smoke flows into the heat exchange part of the second heat exchanger in a series mode is avoided, and heat transfer deterioration of the second heat exchanger is further caused.
In conclusion, the air source heat pump driven by the engine has the advantages of high engine efficiency, sufficient recovery of flue gas waste heat, low emission of nitrogen oxides and long service life of the unit.
Drawings
FIG. 1 is an external view of an engine-driven air source heat pump in an embodiment of the present invention;
FIG. 2 is a schematic diagram of the connection and flow of the main body portion of an engine driven air source heat pump according to 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 according to 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 structural view of a separator in an embodiment of the invention;
FIG. 6 is a first schematic diagram illustrating an internal structure of a first chamber according to an embodiment of the present invention;
fig. 7 is a second schematic view of the internal structure of the first cavity in the embodiment of the invention.
Description of the figure numbering: a flue gas cooling water heat exchanger 8, an engine 10, a compressor 12, an intake port 13, an exhaust port 14, a first heat exchanger 15, a first throttle valve 16, a flue gas refrigerant heat exchanger 17, a first pipe 18, a first connection point 19, a second connection point 20, a second throttle valve 21, a second heat exchanger 22, a first circulation port 23, a second circulation port 24, a third switching valve 27, a first exhaust pipe 28, an air replenishment port 29, an oil separator 30, a lubricating oil circuit 31, a dry filter 32, an economizer 33, a first branch line 34, a second branch line 35, a first refrigerant three-way valve 36, a second refrigerant three-way valve 37, a coupling 38, a common chassis 39, an internal air inlet 71, a rain cover 72, a first air pipe 73, a second air pipe 74, an air cleaner 75, a partition 76, a fin coil heat exchanger 77, a fan 78, a first air pipe hole 79, a bypass pipe 81, an EGR valve 82, a bypass pipe 81, and a compressor, The device comprises a flue gas outlet 83, a second smoke exhaust pipeline 84, a frame 91, a panel 92, an electronic control unit 93, a first chassis 94, a fuel pipeline 96, a heat insulation material 97, a smoke exhaust port 130, a cooling water pump 138, an expansion water tank 139, a three-way catalyst 141, a drain valve 142, a cooling water three-way valve 143, a water condensation port 144, a neutralization tank 145, a neutralization ball 146, a radiator 147, a cooling water refrigerant heat exchanger 149, a first cavity 1000, a cooling water inlet a and a cooling water outlet b.
Detailed Description
In order to make the technical means, the original features, the achieved objects and the effects of the present invention easily understood, the following embodiments are specifically described with reference to the accompanying drawings.
< example >
FIG. 1 is an external view of an engine-driven air source heat pump in an embodiment of the present invention; FIG. 2 is a schematic diagram of the connection and flow of the main body portion of an engine driven air source heat pump according to 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 according to 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, which includes a first cavity 1000, a main body portion and a peripheral portion. Wherein the main body portion includes an engine 10, a compressor 12, a first heat exchanger 15, a first throttle 16, a flue gas refrigerant heat exchanger 17, a first pipe 18, a second throttle 21, a second heat exchanger 22, a first flywheel 25, an economizer 33, a first refrigerant three-way valve 36, a second refrigerant three-way valve 37, a coupling 38, a first connecting shaft 61, a second connecting shaft 62, a cooling water refrigerant heat exchanger 149, an outside air inlet (not shown in the figure), and an inside air inlet. The peripheral part comprises a flue gas cooling water heat exchanger 28, a cooling water pump 138, a thermostat 140, a three-way catalyst 141, a cooling water three-way valve 143 and a 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 bottom plate 94, and a partition 76.
The partition plate 76 is located at the lower part of the second heat exchanger 22, the partition plate 76 is provided with a first air pipe hole 79, the first air pipe 73 penetrates through the first air pipe hole 79, the outer part of the first air pipe 73 and the first air pipe hole 79 are sealed by welding or rubber, rubber sealing rings and fireproof mud, so that the second heat exchanger 22 is separated from the inner part of the first cavity 100 through the partition plate 76, and air and rainwater in the second heat exchanger 22 cannot flow into the first cavity 1000 in series.
The interior air inlet 71 is located within the second heat exchanger 22 and the first air duct 73 is externally covered by a rain cap 72 adjacent the interior air inlet 71. The second flue gas duct 84 communicates with the atmosphere through the cavity 1000 or the second heat exchanger 22. In this embodiment, the second flue gas duct 84 passes through the second heat exchanger 22 and is vented to the atmosphere through a flue gas outlet 130, the flue gas outlet 130 being located at a higher level than the heat exchange portion of the finned coil heat exchanger 77.
The second heat exchanger 22 includes at least one finned coil heat exchanger 77 and at least one fan 78. The finned 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 fin coil heat exchangers 77 of a U-type and 2 blowers 78. The fan 78 may be one of an ac fan or a dc brushless fan, or one of an axial fan or a centrifugal fan.
Fig. 5 is a schematic structural view of a separator in an embodiment of the present invention.
As shown in FIG. 5, the partition 76 is sloped on both sides and has a downward flange around the partition 76. The slope and the flanging can be formed by splicing flanging or steel plates. The partition plate 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 mode, and the second smoke exhaust pipe 84 is arranged on the partition plate 76 in a penetrating mode. In addition, a sound-absorbing and heat-insulating material 97 is attached to the lower portion of the partition plate 76.
FIG. 6 is a first schematic diagram illustrating an internal structure of a first chamber according to an embodiment of the present invention; fig. 7 is a second schematic view of the internal structure of the first cavity in the embodiment of the invention.
As shown in fig. 6 and 7, these two figures are actually internal views of the first chamber 1000 that do not include the partition 76 and the panel 92. The engine 10, the air filter 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 arranged in the first cavity 1000.
The air cleaner 75 communicates with the inside air inlet 71 through the first air pipe 73, and the air cleaner 75 communicates with the engine 10 through the second air pipe 74. The air filter 75 may further filter the 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 a bypass pipe 81, and an EGR valve 82 is installed 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 compressor 12 are secured to a common chassis 39, and the common chassis 39 is mounted on a first chassis 94. The engine 10 also has a first exhaust duct 28 capable of exhausting flue gases generated during operation of the engine 10.
The engine 10 is one form of naturally aspirated or turbocharged engine, and the coupling 38 is a dual diaphragm coupling. The thermostat 140 is an electronic or mechanical thermostat, and may also be an electrically controlled three-way or two-way valve.
The compressor 12 has a suction port 13, a discharge port 14, and a suction port 29. The refrigerant gas enters from the suction port 13 and the supplementary port 29, is compressed, and is discharged from the discharge port 14. The compressor 12 is any one of an open-type screw compressor, an open-type magnetic suspension centrifugal compressor or an open-type scroll compressor, and the refrigerant in the compressor 12 is propane or NH3R718, HFC32, HFC134a, HFC407C, HFC410a, HFC245fa, HFC507A, HFO1234 ze, HFO1234yf or HFO1234 zf.
The air cleaner 75 is placed laterally above the engine 10.
The outside air inlet includes the fin side of the fin-and-coil heat exchanger 77 and the fan 78.
The engine-driven air source heat pump 10000 provided by the embodiment has a heating mode and a defrosting mode.
During heating or defrosting (fan on) operation, outside air enters the inside of the second heat exchanger 22 after passing through the finned coil heat exchanger 77, at this time, heat exchange with the finned coil heat exchanger 77 is performed, the temperature is reduced, the engine 10 sucks 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 filter 75 and the second air pipe 74 to enter the engine 10, and is mixed with fuel from the fuel pipeline 96, and the low-temperature air is combusted and expanded to generate power and high-temperature flue gas, 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 to the atmosphere outside the smoke outlet 130 through the second smoke exhaust pipeline 84. Because the engine 10 is mostly operated at partial load, during the operation of the partial load, the EGR valve is opened, part of the smoke is mixed with the air in the first air pipe 73 through the bypass pipe 81, and the air mixed with the smoke flows back to the engine 10, so that the temperature of the smoke discharged by the engine 10 is reduced, and the emission of NOx and the like is reduced.
During defrost operation, if the fan is turned off, air enters the interior of the second heat exchanger 22 through openings in the finned coil 77 or fan 78, the engine 10 draws air into the interior of the second heat exchanger 22 through the interior air inlet 71, the air flows through the first air duct 73, the air filter 75, the second air duct 74 into the engine 10, mixes with fuel from the fuel line 96, combusts and expands to produce power and 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 to the atmosphere outside the smoke outlet 130 through the second smoke exhaust pipeline 84. Because the engine 10 is mostly operated at partial load, during the operation of the partial load, the EGR valve is opened, part of the smoke is mixed with the air in the first air pipe 73 through the bypass pipe 81, and the air mixed with the smoke flows back to the engine 10, so that the temperature of the smoke discharged by the engine 10 is reduced, and the emission of NOx and the like is reduced.
The second flue gas duct 84 passes under the fins of the finned coil heat exchanger 77 in the first cavity 1000, and the flue gas in the second flue gas duct 84 heats the baffle 76, so that the baffle 76 maintains an above-zero temperature in the areas prone to icing below the fins of the finned 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, and the like. The first heat exchanger 15 is a shell-and-tube type, plate type, sleeve type, finned coil, or other type heat exchanger, and if the refrigerant is a flammable refrigerant such as propane, the first heat exchanger 15 is a plate type, sleeve type, finned coil, or other compact heat exchanger.
In the present embodiment, the well-known techniques such as providing an oxygen sensor in the second air pipe 74, providing an oxygen sensor in the flue gas pipe of the engine 10, providing a pressure sensor, and controlling the equivalent combustion are not described in detail.
The first heat exchanger 15 is for supplying heat, and has a first refrigerant inlet and a first refrigerant outlet, the first refrigerant inlet communicating with the discharge 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 pipe 28, and the refrigerant absorbs heat from the flue gas in the first exhaust pipe 28 of the engine 10 and evaporates. 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 in series or 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. 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 in series with the refrigerant side of the cooling water refrigerant heat exchanger 149 and then connected to the port E2 of the second refrigerant three-way valve 37, the port S2 of the second refrigerant three-way valve 37 is connected to the suction port 13, and the port D1 of the second refrigerant three-way valve 37 is connected to the gas replenishing 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 line 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 circulation port 23 and a second circulation port 24. The first communication 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 port 24 is connected to the port E1 of the first refrigerant three-way valve 36, the port S1 of the first refrigerant three-way valve 36 is connected to the suction port 13, and the port D1 of the first refrigerant three-way valve 36 is connected to the discharge port 14. The second throttle 21 is an electronic expansion valve.
The first refrigerant three-way valve 36 is any one of an electromagnetic valve, an electric butterfly valve, an electric ball valve, and an electric stop valve, and the first refrigerant three-way valve 36 may be a single valve or a valve block. The first refrigerant three-way valve 36 may also be configured to have the same function by 2 two-way valves. The second refrigerant three-way valve 37 is any one of an electromagnetic valve, an electric butterfly valve, an electric ball valve, and an electric stop 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 have the same function by 2 two-way valves. The third switching valve 27 is any one of a check valve, an electromagnetic valve, an electric ball valve, and an electric shutoff valve.
As shown in fig. 3, the flue gas discharged from the engine 10 flows through the first exhaust pipe 28, sequentially enters the flue gas cooling water heat exchanger 8 and the flue gas refrigerant heat exchanger 17 through the three-way catalyst 141 to release heat to the cooling water and the refrigerant, the flue gas after heat release is discharged through the flue gas outlet 83, the second flue gas pipe 84 and the smoke outlet 130, and the water condensed from the flue gas enters the neutralization tank 145 through the water condensation port 144. The neutralizing tank 145 is filled with a neutralizing ball 146, the neutralizing ball 146 is a zeolite substance, the nitrogen-containing acidic substance in the condensed water is neutralized, and the neutralized condensed water is discharged through an overflow port of the neutralizing tank 145 or is 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 for heating.
The coolant three-way valve 143 has M ports, N ports, and P ports. The M port is connected to the thermostat 140, the N port is connected to the cooling water inlet a, and the P port is connected to 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 the cylinder liner of the engine 10, is heated, 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 entirely or partially through the cooling water three-way valve 143. The cooling water leaving the cooling water three-way valve 143 flows back to the cooling water pump 138 after flowing through the radiator 147 in the heating mode or the cooling and heating mode; if the heat exchange amount of the flue gas refrigerant heat exchanger 17 is not enough to share the frost-free requirement of the second heat exchanger 22 during the heating mode, the ports P and N are simultaneously circulated, the cooling water refrigerant heat exchanger 149 exchanges heat to ensure the frost-free operation of the second heat exchanger 22, the cooling water flows through the radiator 147 and then flows back to the cooling water pump 138, and flows through the cooling water refrigerant heat exchanger 149 and the radiator 147 and then flows back to the cooling water pump during the defrosting mode. An inlet pipeline of the cooling water pump 138 is provided with an expansion water tank 139, and the expansion water tank 139 is used for adding cooling water and keeping the pressure of the inlet of the cooling water pump 138 constant.
The flue gas refrigerant heat exchanger 17 is any one of a fin coil type heat exchanger, a plate fin type heat exchanger, a plate shell type heat exchanger and a sleeve type heat exchanger, and the flue gas cooling water heat exchanger 8 is any one of a fin coil type heat exchanger, a plate fin type heat exchanger, a plate shell type heat exchanger and a sleeve type heat exchanger. The material of the flue gas refrigerant heat exchanger 17 is stainless steel.
The specific working process of the engine-driven air source heat pump 10000 provided by the embodiment is as follows:
as shown in fig. 2, in the heating mode, if the air passing through the second heat exchanger 22 is in the non-frost region: the port E1 of the first refrigerant three-way valve 36 communicates with the port S1, the port E2 of the second refrigerant three-way valve 37 communicates with the port D2, 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 drives the compressor 12 through the transmission device 11 to compress the refrigerant gas, the compressed refrigerant gas is discharged to the first refrigerant inlet and enters the first heat exchanger 15, and the refrigerant gas releases heat and condenses 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 line 18, the first connection point 19, is split into two paths at the second connection point 20, and enters the first branch path 34 and the second branch path 35. Wherein the first branch 34 is provided with the second throttle 21 and the second branch 35 is provided with the first throttle 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, then flows through the cold water refrigerant heat exchanger 149, then flows through the second refrigerant three-way valve E2 and the D2, and returns to the compressor 12 through the air supplement port 29. The refrigerant liquid in the first branch passage 34 is converted into a gas-liquid two-phase refrigerant by the second throttle valve 21, enters the second heat exchanger 22 through the first flow port 23 to absorb heat and evaporate the refrigerant gas, and is returned to the compressor 12 through the suction port 13 via the ports E1 and S1 of the first refrigerant three-way valve 36.
In the heating mode, if the air flowing through the second heat exchanger 22 is in the frost formation zone: the port E1 of the first refrigerant three-way valve 36 communicates with the port S1, the port E2 of the second refrigerant three-way valve 37 communicates with the port S2, 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 drives the compressor 12 through the transmission device 11 to compress the refrigerant gas, the compressed refrigerant gas is discharged to the first refrigerant inlet and enters the first heat exchanger 15, and the refrigerant gas releases heat and condenses 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 line 18, the first connection point 19, is split into two paths at the second connection point 20, and enters the first branch path 34 and the second branch path 35. The refrigerant in the second branch 35 is converted into a 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; the refrigerant is also sucked and evaporated in the cooling water refrigerant heat exchanger 149 as necessary, and the sucked and evaporated refrigerant flows through the second refrigerant three-way valve E2 and the S2. The refrigerant liquid in the first branch passage 34 is converted into a gas-liquid two-phase refrigerant by the second throttle valve 21, enters the second heat exchanger 22 through the first flow port 23 to absorb heat, is evaporated and converted into a refrigerant gas, and then passes through the port E1 and the port S1 of the first refrigerant three-way valve 36. The two refrigerant streams flowing out of the ports S1 and S2 are collected and returned to the compressor 12 through the suction port 13.
In the defrosting mode, the ports D1 and E1 of the first refrigerant three-way valve 36 communicate with each other, the port E2 and the port S2 of the second refrigerant three-way valve 37 communicate with each other, 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 divides the refrigerant gas into two paths, 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; the other refrigerant gas flows into the second heat exchanger 22 through the ports D1, E1 of the first refrigerant three-way valve 36 and the second flow port 24, condenses into a refrigerant liquid, releases heat to the frost layer on the surface of the second heat exchanger 22 to defrost, and then flows out of the first flow port 23, passes through the third switching valve 27, and then the two refrigerant liquids are collected at the first connection 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, then flows through the economizer 33, enters the flue gas refrigerant heat exchanger 17 and the cooling water refrigerant heat exchanger 149 to absorb heat and evaporate, is converted into a 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. Furthermore, 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 may be made in accordance with the teachings of the present invention, which variations and modifications are within the scope of the present invention as claimed. The scope of the invention is defined by the appended claims and equivalents thereof.
For example, in the above-described embodiment, the second heat exchanger is provided as one, and in actual use, the second heat exchanger may be provided as a plurality of second heat exchangers, and in this case, the internal air inlet may be provided only inside one of the second heat exchangers.
Claims (10)
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 and a first cavity,
wherein the air cleaner is communicated with the internal air inlet through a first air pipe, the air cleaner is communicated with the engine through a second air pipe,
the smoke refrigerant heat exchanger is provided with a smoke outlet, the smoke 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 smoke outlet is also connected with a smoke outlet through a second smoke exhaust pipeline, and the smoke outlet is arranged outside the second heat exchanger and higher than the heat exchange part of the second heat exchanger.
2. The engine-driven air source heat pump of claim 1, wherein:
and the internal air inlet is positioned inside the second heat exchanger, and external air enters the internal air inlet after flowing through the second heat exchanger.
3. The engine-driven air source heat pump of claim 1, wherein:
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.
4. An engine driven air source heat pump according to claim 3, characterized in that:
wherein, the finned coil type heat exchanger is any one of a flat plate type, an L type and a U type.
5. The engine-driven air source heat pump of claim 3, further comprising:
an inlet for the outside air is provided,
wherein the external air inlet comprises the fan and a fin side of the fin-and-coil heat exchanger,
the engine-driven air source heat pump has a heating mode and a defrost mode,
in the heating mode, the external air is introduced into the second heat exchanger only from the fin side of the fin-and-coil heat exchanger,
in the defrosting mode, the outside air is introduced into the second heat exchanger from the fin side of the fin-and-coil heat exchanger and the fan.
6. 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.
7. 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, the baffle plate is provided with a first air pipe hole, the first air pipe is arranged on the first air pipe hole in a penetrating way, a rain-proof cap is covered outside the first air pipe close to the inner air inlet,
the two sides of the partition board are in a slope shape, and downward flanges are arranged around the partition board.
8. 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.
9. The engine-driven air source heat pump of claim 1, wherein:
wherein, the first cavity is internally stuck with sound-absorbing and heat-insulating materials,
the air filter is positioned transversely above the engine.
10. The engine-driven air source heat pump of claim 1, wherein:
wherein the second heat exchanger is provided in plurality,
the inside air inlet is provided inside one of the second heat exchangers.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210060671.1A CN114413512B (en) | 2022-01-19 | Engine-driven air source heat pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210060671.1A CN114413512B (en) | 2022-01-19 | Engine-driven air source heat pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114413512A true CN114413512A (en) | 2022-04-29 |
| CN114413512B CN114413512B (en) | 2024-04-16 |
Family
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