CN114440445A - Engine-driven large-temperature-difference high-temperature heat pump hot water unit - Google Patents
Engine-driven large-temperature-difference high-temperature heat pump hot water unit Download PDFInfo
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- CN114440445A CN114440445A CN202210149027.1A CN202210149027A CN114440445A CN 114440445 A CN114440445 A CN 114440445A CN 202210149027 A CN202210149027 A CN 202210149027A CN 114440445 A CN114440445 A CN 114440445A
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- cooling water
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims abstract description 177
- 239000003507 refrigerant Substances 0.000 claims abstract description 233
- 239000000498 cooling water Substances 0.000 claims abstract description 172
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 claims abstract description 96
- 239000003546 flue gas Substances 0.000 claims abstract description 96
- 239000007788 liquid Substances 0.000 claims abstract description 37
- 238000009833 condensation Methods 0.000 claims abstract description 18
- 230000005494 condensation Effects 0.000 claims abstract description 18
- 238000001704 evaporation Methods 0.000 claims abstract description 6
- 239000013589 supplement Substances 0.000 claims abstract description 5
- 239000007789 gas Substances 0.000 claims description 34
- 238000010438 heat treatment Methods 0.000 claims description 24
- 238000010257 thawing Methods 0.000 claims description 9
- 230000002528 anti-freeze Effects 0.000 claims description 4
- 229910001220 stainless steel Inorganic materials 0.000 claims description 4
- 239000010935 stainless steel Substances 0.000 claims description 4
- 239000000463 material Substances 0.000 claims description 3
- 230000009467 reduction Effects 0.000 claims description 3
- 230000006698 induction Effects 0.000 claims 1
- 230000008020 evaporation Effects 0.000 abstract description 4
- 238000010521 absorption reaction Methods 0.000 abstract description 2
- 239000010687 lubricating oil Substances 0.000 description 21
- 239000003921 oil Substances 0.000 description 20
- 230000002093 peripheral effect Effects 0.000 description 17
- 238000010586 diagram Methods 0.000 description 16
- 230000003472 neutralizing effect Effects 0.000 description 16
- 239000000779 smoke Substances 0.000 description 16
- 230000005540 biological transmission Effects 0.000 description 11
- 239000000126 substance Substances 0.000 description 8
- 239000003054 catalyst Substances 0.000 description 7
- 238000006386 neutralization reaction Methods 0.000 description 6
- 239000002918 waste heat Substances 0.000 description 6
- ATUOYWHBWRKTHZ-UHFFFAOYSA-N Propane Chemical compound CCC ATUOYWHBWRKTHZ-UHFFFAOYSA-N 0.000 description 4
- 229910021536 Zeolite Inorganic materials 0.000 description 4
- 230000002378 acidificating effect Effects 0.000 description 4
- HNPSIPDUKPIQMN-UHFFFAOYSA-N dioxosilane;oxo(oxoalumanyloxy)alumane Chemical compound O=[Si]=O.O=[Al]O[Al]=O HNPSIPDUKPIQMN-UHFFFAOYSA-N 0.000 description 4
- 238000012423 maintenance Methods 0.000 description 4
- QJGQUHMNIGDVPM-UHFFFAOYSA-N nitrogen group Chemical group [N] QJGQUHMNIGDVPM-UHFFFAOYSA-N 0.000 description 4
- 239000010457 zeolite Substances 0.000 description 4
- 239000000446 fuel Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 230000001502 supplementing effect Effects 0.000 description 3
- RWRIWBAIICGTTQ-UHFFFAOYSA-N anhydrous difluoromethane Natural products FCF RWRIWBAIICGTTQ-UHFFFAOYSA-N 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005485 electric heating Methods 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
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- 239000001294 propane Substances 0.000 description 2
- 239000000725 suspension Substances 0.000 description 2
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- 230000009471 action Effects 0.000 description 1
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- 238000004781 supercooling Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H4/00—Fluid heaters characterised by the use of heat pumps
- F24H4/02—Water heaters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
- F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
-
- 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
- F25B41/40—Fluid line arrangements
- F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
-
- 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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
Abstract
The invention provides an engine-driven large-temperature-difference high-temperature heat pump hot water unit, which comprises a compressor, a first heat exchanger, a second heat exchanger, an economizer and an engine, wherein the compressor is provided with an exhaust port, an air suction port and an air supplement port, and the engine is provided with an engine cylinder sleeve, and is characterized by also comprising: the system comprises a flue gas refrigerant heat exchanger, a flue gas cooling water heat exchanger and a subcooler, wherein refrigerant from an exhaust port is subjected to heat release and condensation in a first heat exchanger to form liquid, flows through a cooler to release heat and then is divided into two paths, one path of the refrigerant flows through the economizer to release heat and cool, and returns to a compressor from an air suction port after being subjected to heat absorption and evaporation in a second heat exchanger, the other path of the refrigerant flows through the economizer and the flue gas refrigerant heat exchanger to absorb heat and evaporate, and hot water partially or completely flows through the subcooler to absorb heat of liquid of the refrigerant, and then flows into the first heat exchanger to absorb condensation heat of the refrigerant, and then directly or indirectly absorbs heat from an engine cylinder sleeve and the flue gas cooling water heat exchanger in sequence.
Description
Technical Field
The invention belongs to the technical field of heat pumps, and particularly relates to an engine-driven large-temperature-difference high-temperature heat pump hot water unit.
Background
The temperature difference of primary water for regional heat supply in winter in the north is generally between 25 ℃ and 40 ℃, the temperature of outlet water is between 75 ℃ and 90 ℃, a boiler is widely adopted as a heating source, the thermal efficiency of the boiler is low, and the fuel consumption is large. The maximum temperature of hot water prepared by a conventional electric heating pump is about 73 ℃, and the electric heating pump cannot directly replace a winter heat supply boiler because the outlet water temperature is not high enough. The engine-driven heat pump has the characteristics of high efficiency, low operating cost and low emission level, and along with implementation of a sustainable development strategy and continuous enhancement of energy-saving and environment-friendly consciousness, biomass fuel or solar energy synthetic fuel is adopted, and the development of the high-efficiency engine-driven heat pump for replacing a boiler or cogeneration for winter heat supply and similar industrial heat is a necessary choice. The engine-driven heat pump has obvious economic benefit and environmental protection benefit, but the existing engine-driven heat pump is still a small multi-connected air conditioner or a product with the temperature of supplied hot water of about 50 ℃.
Therefore, the engine-driven large-temperature-difference high-temperature heat pump water heater unit which is reasonable in design structure, high in efficiency, and capable of enabling the hot water temperature difference to be 25-40 ℃ and the hot water outlet temperature to reach about 90 ℃ is urgently needed.
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 high temperature heat pump hot water unit having a large temperature difference.
The invention provides an engine-driven large-temperature-difference high-temperature heat pump hot water unit, which comprises a compressor, a first heat exchanger, a second heat exchanger, an economizer and an engine, wherein the compressor is provided with an exhaust port, an air suction port and an air supplement port, and the engine is provided with an engine cylinder sleeve, and the engine-driven large-temperature-difference high-temperature heat pump hot water unit is characterized by also comprising: the system comprises a flue gas refrigerant heat exchanger, a flue gas cooling water heat exchanger and a subcooler, wherein refrigerant from an exhaust port is subjected to heat release and condensation in a first heat exchanger to form liquid, flows through a cooler to release heat and is divided into two paths, one path of the refrigerant flows through an economizer to release heat and cool, and returns to a compressor from an air suction port after being subjected to heat absorption and evaporation in a second heat exchanger, the other path of the refrigerant flows through the economizer and a flue gas refrigerant heat exchanger to absorb heat and evaporate, and then returns to the compressor from an air supplementing port, after part or all of hot water flows through the subcooler and absorbs heat of refrigerant liquid, all hot water flows into the first heat exchanger to absorb condensation heat of the refrigerant, and then directly or indirectly absorbs heat from an engine cylinder sleeve and the flue gas cooling water heat exchanger in sequence.
In the engine-driven large-temperature-difference high-temperature heat pump hot water unit provided by the invention, the engine-driven large-temperature-difference high-temperature heat pump hot water unit further has the following characteristics that: the cooling water enters the engine cylinder sleeve after being pressurized by the cooling water pump, absorbs heat to raise the temperature, then flows to the radiator, releases heat to hot water and then flows back to the cooling water pump, the first heat exchanger is connected with the radiator in series, the radiator is also connected with the flue gas cooling water heat exchanger in series, and the hot water from the first heat exchanger sequentially flows through the radiator and the flue gas cooling water heat exchanger to absorb heat to raise the temperature.
In the engine-driven large-temperature-difference high-temperature heat pump hot water unit provided by the invention, the engine-driven large-temperature-difference high-temperature heat pump hot water unit further has the following characteristics that: the cooling water is pressurized by the cooling water pump, then enters the engine cylinder sleeve and the smoke cooling water heat exchanger in sequence to absorb heat and raise the temperature, then flows to the radiator to release heat to hot water and then flows back to the cooling water pump, the first heat exchanger is connected with the radiator in series, and the hot water from the first heat exchanger flows through the radiator to absorb heat and raise the temperature.
In the engine-driven large-temperature-difference high-temperature heat pump hot water unit provided by the invention, the engine-driven large-temperature-difference high-temperature heat pump hot water unit further has the following characteristics that: the cooling water refrigerant heat exchanger is connected with the radiator in series, wherein the running modes of the engine-driven large-temperature-difference high-temperature heat pump hot water unit comprise a heating mode and a defrosting mode, and in the defrosting mode, cooling water flows through the cooling water refrigerant heat exchanger to heat refrigerant in the cooling water refrigerant heat exchanger into refrigerant gas and then flows into the radiator.
In the engine-driven large-temperature-difference high-temperature heat pump hot water unit provided by the invention, the engine-driven large-temperature-difference high-temperature heat pump hot water unit further has the following characteristics that: the temperature saver comprises a temperature saver, wherein cooling water is pressurized by a cooling water pump, then flows through an engine cylinder sleeve to absorb heat and raise the temperature, then enters the temperature saver, and directly flows back to the cooling water pump from the temperature saver when the temperature of the cooling water entering the temperature saver is low; when the temperature of the cooling water entering the thermostat is high, the cooling water flows through the radiator again to release heat and then flows back to the cooling water pump.
In the engine-driven large-temperature-difference high-temperature heat pump hot water unit provided by the invention, the engine-driven large-temperature-difference high-temperature heat pump hot water unit also has the following characteristics: the first heat exchanger is connected with the engine cylinder sleeve in series, the engine cylinder sleeve is connected with the flue gas cooling water heat exchanger in series, and hot water from the first heat exchanger sequentially flows through the engine cylinder sleeve and the flue gas cooling water heat exchanger to absorb heat and raise temperature.
In the engine-driven large-temperature-difference high-temperature heat pump hot water unit provided by the invention, the engine-driven large-temperature-difference high-temperature heat pump hot water unit also has the following characteristics: wherein, all hot water is divided into two paths, one path flows through the subcooler and then enters the first heat exchanger, and the other path directly flows into the first heat exchanger.
In the engine-driven large-temperature-difference high-temperature heat pump hot water unit provided by the invention, the engine-driven large-temperature-difference high-temperature heat pump hot water unit also has the following characteristics: wherein the temperature of the hot water flowing into the engine-driven large-temperature-difference high-temperature heat pump hot water unit is 40-60 ℃, and the temperature of the hot water flowing out of the engine-driven large-temperature-difference high-temperature heat pump hot water unit is 85-90 ℃.
In the engine-driven large-temperature-difference high-temperature heat pump hot water unit provided by the invention, the engine-driven large-temperature-difference high-temperature heat pump hot water unit also has the following characteristics: the flue gas refrigerant heat exchanger 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 is made of stainless steel.
In the engine-driven large-temperature-difference high-temperature heat pump hot water unit provided by the invention, the engine-driven large-temperature-difference high-temperature heat pump hot water unit also has the following characteristics: wherein the cooling water is one of antifreeze, softened water and desalted water, and the hot water is softened water or desalted water.
Action and Effect of the invention
According to the engine-driven large-temperature-difference high-temperature heat pump hot water unit (hereinafter referred to as unit) provided by the invention, because the unit also comprises the flue gas refrigerant heat exchanger, the flue gas cooling water heat exchanger and the subcooler, the waste heat of the flue gas exhausted by the engine is fully recovered and efficiently utilized, the subcooler and the flue gas refrigerant heat exchanger are combined to ensure that the compressor efficiently supplements air, and the unit output and efficiency are improved.
The first heat exchanger is used as a condenser, the condensation temperature is about 69-75 ℃, the refrigerant liquid flowing out of the condenser releases heat in the subcooler, and the supercooling degree of the refrigerant liquid is as high as about 22-23 ℃. The hot water absorbs about 22 to 32 percent of condensation heat of the refrigerant in the subcooler, the load of the economizer is greatly reduced, and the energy efficiency of the unit is improved. The temperature of the hot water with the temperature of 50 ℃ can be improved to 73 ℃ after the hot water flows through the subcooler and the first heat exchanger.
The refrigerant absorbs a large amount of low-grade flue gas waste heat containing latent heat of condensation water through the flue gas refrigerant heat exchanger and is evaporated into refrigerant gas, and the refrigerant gas returns to the compressor from the air supplementing port, so that the heating capacity of the unit can be improved by over 11 percent. The condensed water can also filter and clean the smoke, so that the discharged smoke is cleaner and more environment-friendly.
The hot water flowing out of the first heat exchanger sequentially absorbs the waste heat of the cylinder sleeve of the engine and the high-temperature waste heat of the flue gas in the flue gas cooling water heat exchanger, even under the condition of low ambient temperature of the second heat exchanger serving as an air source evaporator, the temperature of the hot water flowing out of the unit is up to 90 ℃, and the comprehensive heat supply energy efficiency of the unit in winter is up to more than 1.75.
In conclusion, the engine-driven large-temperature-difference high-temperature heat pump hot water unit is reasonable in structure, high in working efficiency and high in outlet water temperature.
Drawings
FIG. 1 is a schematic connection and flow diagram of a main body part of an engine-driven large temperature difference high temperature heat pump water heater unit according to a first embodiment of the present invention;
FIG. 2 is a schematic diagram of the connection and flow of the peripheral parts of an engine-driven large temperature difference high temperature heat pump hot water unit according to a first embodiment of the present invention;
FIG. 3 is a schematic diagram of the connection and flow of the main body of the engine-driven large temperature difference high temperature heat pump water heater unit according to the second embodiment of the present invention;
FIG. 4 is a schematic connection and flow diagram of the peripheral parts of an engine-driven large temperature difference high temperature heat pump hot water unit according to a third embodiment of the present invention;
FIG. 5 is a schematic connection and flow diagram of the main body of an engine-driven large temperature difference high temperature heat pump water heater unit according to a fourth embodiment of the present invention;
FIG. 6 is a schematic connection and flow diagram of the peripheral parts of an engine-driven large temperature difference high temperature heat pump hot water unit according to the fourth embodiment of the present invention;
FIG. 7 is a schematic connection and flow diagram of the peripheral part of an engine-driven large temperature difference high temperature heat pump hot water unit according to the fifth embodiment of the present invention;
fig. 8 is a schematic connection and flow diagram of the peripheral part of an engine-driven large-temperature-difference high-temperature heat pump hot water unit in the sixth embodiment of the invention.
Description of the figure numbering: a flue gas cooling water heat exchanger 8, a subcooler 9, an engine 10, a transmission 11, a compressor 12, an air intake port 13, an air exhaust port 14, a first heat exchanger 15, a first throttle valve 16, a flue gas refrigerant heat exchanger 17, a first pipeline 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 first switching valve 25, a second switching valve 26, a third switching valve 27, a smoke exhaust duct 28, an air supply port 29, an oil separator 30, a lubricating oil circuit 31, a drying filter 32, an economizer 33, a first branch 34, a second branch 35, a first refrigerant three-way valve 36, a second refrigerant three-way valve 37, a fourth switching valve 38, a third heat exchanger 39, a fifth switching valve 40, an exhaust port 130, a cooling water pump 138, an expansion water tank 139, a thermostat 140, a three-way catalyst 141, a drain valve 142, a, 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 cooling water inlet a and a cooling water outlet b.
Detailed Description
In order to make the technical means, creation features, achievement purposes and effects of the invention easy to understand, the following embodiments specifically describe an engine-driven large-temperature-difference high-temperature heat pump water heater unit in combination with the accompanying drawings.
< first embodiment >
The embodiment provides an engine-driven large-temperature-difference high-temperature heat pump hot water unit.
FIG. 1 is a schematic connection and flow diagram of a main body part of an engine-driven large temperature difference high temperature heat pump water heater unit according to a first embodiment of the present invention; fig. 2 is a schematic connection and flow diagram of the peripheral part of an engine-driven large temperature difference high temperature heat pump hot water unit according to an embodiment of the present invention.
As shown in fig. 1 and 2, the engine-driven large temperature difference high temperature heat pump water heating unit includes a main body portion and a peripheral portion. The main body part comprises a subcooler 9, an engine 10, a transmission device 11, a compressor 12, a first heat exchanger 15, a first throttle valve 16, a flue gas refrigerant heat exchanger 17, a first pipeline 18, a second throttle valve 21, a second heat exchanger 22, an economizer 33, a first refrigerant three-way valve 36, a second refrigerant three-way valve 37 and a cooling water refrigerant heat exchanger 149. The peripheral part comprises a flue gas cooling water heat exchanger 8, a cooling water pump 138, a thermostat 140, a three-way catalyst 141, a cooling water three-way valve 143 and a radiator 147.
As shown in fig. 1, an output end of the engine 10 is connected to a compressor 12 through a transmission 11, and the compressor 12 is driven to compress refrigerant gas therein. The rotation speed of the engine 10 is continuously adjustable, and the rotation speed of the compressor 12 is adjusted according to the requirements under different operation conditions by adjusting the rotation speed of the engine 10. The engine 10 also has a smoke exhaust duct 28 capable of exhausting smoke generated during operation of the engine 10.
The engine 10 is one of a naturally aspirated or turbocharged form, and the transmission 11 is any one of a coupling, an electromagnetic clutch, a change-speed gear box, or a belt with pulleys.
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 NH3、R718、HFC32、HFC134a、HFC407C、HFC410a、HFC245fa、HFC507A、HFO1234ze、HFEither O1234yf or HFO1234 zf.
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 first heat exchanger 15 supplies heat by hot water.
The subcooler 9 is used to subcool the refrigerant liquid. The subcooler 9 may be provided independently or may be placed in the first heat exchanger 15. The subcooler 9 of this embodiment is independently disposed outside the first heat exchanger 15.
The flue gas refrigerant heat exchanger 17 is disposed within the exhaust flue 28 and the refrigerant absorbs heat from the flue gas within the exhaust flue 28 of the engine 10 for evaporation. The refrigerant in the cooling water refrigerant heat exchanger 149 absorbs heat from the cooling water to evaporate. The cooling water is one of antifreeze, softened water and desalted water. 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 replenishment 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. 2, the flue gas discharged from the engine 10 sequentially enters the flue gas cooling water heat exchanger 8 and the flue gas refrigerant heat exchanger 17 in the smoke exhaust duct 28 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 smoke exhaust port 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, and the radiator 147 and the flue gas cooling water heat exchanger 8 are connected in series.
The hot water partially or entirely passes through the subcooler 9. In the embodiment, part of hot water flows through the cooler 9, absorbs the heat of the refrigerant liquid from the subcooler 9, is heated, then flows to the first heat exchanger 15 together with the other part of hot water to absorb the condensation heat of the refrigerant, is heated, then flows through the radiator 147 and the flue gas cooling water heat exchanger 8 in sequence to absorb heat, and is heated, and finally high-temperature hot water is output.
The coolant three-way valve 143 has M ports, N ports, and P ports. The port P is connected with the thermostat 140, the port N is connected with the cooling water inlet a, and the port M is connected with the cooling water outlet of the cylinder sleeve 10 of the engine cylinder sleeve. The cooling water outlet b is connected between the P port and the cooling water inlet port of the radiator 147.
The radiator 147, the cooling water pump 138 and the cylinder liner of the engine 10 are connected in sequence, and the cooling water is pressurized by the cooling water pump 138, enters the cylinder liner of the engine 10 to absorb heat and raise temperature, and then flows through the cooling water three-way valve 143. The cooling water leaving the cooling water three-way valve 143 enters the thermostat 140 in a heating mode. 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 enters the radiator 147 and then flows back to the cooling water pump 138; 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, cooling water flows through the radiator 147 and then flows back to the cooling water pump 138, and in the defrosting mode, the cooling water flows through the cooling water refrigerant heat exchanger 149 and the radiator 147 and then flows back to the cooling water pump. 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 engine-driven large-temperature-difference high-temperature heat pump hot water unit provided by the embodiment has a heating mode and a defrosting mode, and the specific working process is as follows:
as shown in fig. 1, 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 subcooler 9 to continue heat release and temperature reduction, and is divided into two paths at the first pipeline 18 and the first connection point 19 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 subcooler 9 to continue heat release and temperature reduction, and is divided into two paths at the first pipeline 18 and the first connection point 19 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 discharges from the first refrigerant outlet and flows through the cooler 9 to continue release heat and reduce the temperature; 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 engine driving large-temperature-difference high-temperature heat pump hot water unit (hereinafter referred to as unit) can fully utilize high-grade flue gas waste heat as a first-stage high-temperature heat source, and engine cylinder sleeve waste heat as a second-stage heating heat source at about 85 ℃ through a radiator, so that the condensation temperature of a heat pump is below 75 ℃, and a first heat exchanger and a subcooler are used as third and fourth-stage heating heat sources. The hot water is sequentially heated in a cascade manner, so that high-temperature heating hot water at 90 ℃ is efficiently obtained. Table 1 shows the analysis results of the second heat exchanger for the outdoor air source heat exchanger in the case of typical outdoor temperatures in winter of the software calculated based on the engine external characteristic parameters and the compressor performance:
TABLE 1 analysis of the working performance of the unit of example one at typical outdoor temperatures in winter
As shown in table 1, the comprehensive heat supply energy efficiency in winter of the engine-driven large-temperature-difference high-temperature heat pump hot water unit of the embodiment is as high as 1.75, which is significantly higher than that of a boiler. If the temperature of hot water outlet in winter is reduced when the temperature is higher, the comprehensive heat supply energy efficiency of the engine-driven large-temperature-difference high-temperature heat pump hot water unit in winter can be improved by 5-15%. And as the outdoor air temperature is reduced, the heating capacity basically has no attenuation, and the condition that the heating capacity of the electric air source heat pump is greatly attenuated along with the outdoor air temperature is avoided.
< example two >
Fig. 3 is a schematic connection and flow diagram of the main body of the engine-driven large temperature difference high temperature heat pump water heater unit according to the second embodiment of the present invention.
As shown in fig. 3, the second embodiment provides an engine-driven large temperature difference high-temperature heat pump hot water unit, which is different from the first embodiment in that the main body of the engine-driven large temperature difference high-temperature heat pump hot water unit in this embodiment further includes an oil separator 30, a lubricating oil circuit 31, and a dry filter 32.
Other structures in this embodiment are the same as those in the first embodiment, and the same structures are given the same reference numerals.
In fig. 3, the oil separator 30 has an oil refrigerant inlet, an oil refrigerant outlet, and a lubricating oil discharge port, the oil refrigerant inlet communicates with the exhaust port 14, the oil refrigerant outlet communicates with the first refrigerant inlet, and the lubricating oil circuit 31 communicates the lubricating oil discharge port with the compressor 12. Therefore, the compressor can be recycled, the cost is reduced, and the service life of the compressor is prolonged.
The refrigerant gas containing the lubricating oil enters the oil separator 30 through the oil-separated refrigerant inlet, the refrigerant gas from which the lubricating oil has been separated is discharged from the oil-separated refrigerant outlet, and the separated lubricating oil returns to the compressor 12 through the lubricating oil circuit 31.
The dry filter 32 is disposed between the first connection point 19 and the second connection point 20, and can dry and filter the refrigerant flowing therethrough, thereby removing excessive moisture and impurities from the refrigerant and improving the overall working efficiency and reliability of the unit.
The working process of the second embodiment is basically the same as that of the first embodiment, except that:
as shown in fig. 3, in both the heating mode and the defrosting mode, the refrigerant gas discharged from the exhaust port 14 of the compressor 12 enters the oil separator 30 through the oil-separated refrigerant inlet, the oil separator 30 separates the lubricating oil in the refrigerant gas, and the separated lubricating oil returns to the compressor 12 through the lubricating oil circuit 31.
In either the heating mode or the defrosting mode, the refrigerant liquid must be dried by the dry filter 32. The heating mode enters the flue gas refrigerant heat exchanger 17 and the cooling water refrigerant heat exchanger 149 through the first throttling valve 16 and enters the second heat exchanger 22 through the second throttling valve 21; the defrost mode is passed through the first throttle valve 16 into the flue gas refrigerant heat exchanger 17 and the cooling water refrigerant heat exchanger 149.
< example three >
Fig. 4 is a schematic connection and flow diagram of the peripheral part of an engine-driven large temperature difference high temperature heat pump hot water unit in the third embodiment of the present invention.
As shown in fig. 4, the third embodiment provides an engine-driven large temperature difference high temperature heat pump hot water unit, which is different from the first embodiment only in that: in the structure of the peripheral portion, the flue gas cooling water heat exchanger 8 is disposed between the cylinder liner of the engine 10 and the cooling water inlet port of the radiator 147, and in this embodiment, the flue gas cooling water heat exchanger 8 is disposed between the cylinder liner of the engine 10 and the cooling water three-way valve 143. Therefore, the cooling water from the cylinder liner of the engine 10 flows through the flue gas cooling water heat exchanger 8 and then enters the M port of the cooling water three-way valve 143. Other structures are completely the same as those of the first embodiment, and are not described herein again.
As shown in fig. 4, part or all of the hot water flows through the subcooler 9, in this embodiment, part of the hot water flows through the subcooler 9, absorbs heat of the refrigerant liquid from the subcooler 9, heats up, then flows together with the other part of the hot water to the first heat exchanger 15, absorbs heat of the refrigerant condensation, heats up, and then flows through the radiator 147, absorbs heat and heats up.
< example four >
FIG. 5 is a schematic connection and flow diagram of the main body of the engine-driven large temperature difference high temperature heat pump water heater according to the fourth embodiment of the present invention; fig. 6 is a schematic connection and flow diagram of the peripheral part of an engine-driven large temperature difference high temperature heat pump hot water unit according to the fourth embodiment of the present invention.
As shown in fig. 5 and 6, the engine-driven large temperature difference high temperature heat pump water heating unit according to the fourth embodiment includes a main body portion and a peripheral portion. The main body part comprises a subcooler 9, an engine 10, a transmission device 11, a compressor 12, a first heat exchanger 15, a first throttle valve 16, a flue gas refrigerant heat exchanger 17, a first pipeline 18, a second throttle valve 21, a second heat exchanger 22, an oil separator 30, an economizer 33, a first refrigerant three-way valve 36, a second refrigerant three-way valve 37 and a cooling water refrigerant heat exchanger 149. The peripheral part comprises a flue gas cooling water heat exchanger 8, a thermostat 140 and a three-way catalyst 141.
As shown in fig. 5, an output end of the engine 10 is connected to the compressor 12 through a transmission 11, and the compressor 12 is driven to compress refrigerant gas therein. The rotation speed of the engine 10 is continuously adjustable, and the rotation speed of the compressor 12 is adjusted according to the requirements under different operation conditions by adjusting the rotation speed of the engine 10. The engine 10 also has a smoke exhaust duct 28 capable of exhausting smoke generated during operation of the engine 10.
The engine 10 is one of a naturally aspirated or turbocharged form, and the transmission 11 is any one of a coupling, an electromagnetic clutch, a change-speed gear box, or a belt with pulleys.
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 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, NH3, R718, HFC32, HFC134a, HFC407C, HFC410a, HFC245fa, HFC507A, HFO1234ze, HFO1234yf or HFO1234 zf.
The oil separator 30 has an oil refrigerant inlet, an oil refrigerant outlet, and a lubricating oil discharge port, the oil refrigerant inlet communicates with the exhaust port 14, the oil refrigerant outlet communicates with the first refrigerant inlet, and the lubricating oil circuit 31 communicates the lubricating oil discharge port with the compressor 12. The oil separator 30 may be provided independently or may be incorporated in the first heat exchanger 15. The oil separator 30 of the present embodiment is provided separately.
The refrigerant gas containing the lubricating oil enters the oil separator 30 through the oil-separated refrigerant inlet, the refrigerant gas from which the lubricating oil has been separated is discharged from the oil-separated refrigerant outlet, and the separated lubricating oil returns to the compressor 12 through the lubricating oil circuit 31.
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 first heat exchanger 15 supplies heat by hot water.
The subcooler 9 is used to subcool the refrigerant liquid. The subcooler 9 may be provided independently or may be placed in the first heat exchanger 15. The subcooler 9 of this embodiment is independently disposed outside the first heat exchanger 15.
The flue gas refrigerant heat exchanger 17 is disposed within the exhaust flue 28 and the refrigerant absorbs heat from the flue gas within the exhaust flue 28 of the engine 10 for evaporation. In the embodiment, the cooling water is hot water, and the water quality is softened water or desalted water.
The flue gas refrigerant heat exchanger 17 has a second refrigerant inlet connected to the first refrigerant outlet through the first throttle valve 16 and a second refrigerant outlet connected to the air make-up 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 second connection point 20 thereon.
The second heat exchanger 22 has a first circulation port 23 and a second circulation port 24. The first through-flow opening 23 is connected to the second connection point 20 via a second throttle 21. The second flow port 24 is connected to the suction port 13. The second throttle 21 is an electronic expansion valve.
As shown in fig. 6, the flue gas discharged from the engine 10 sequentially enters the flue gas cooling water heat exchanger 8 and the flue gas refrigerant heat exchanger 17 in the smoke exhaust duct 28 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 smoke exhaust port 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 is connected with a cylinder sleeve of the engine 10 in series, and the cylinder sleeve of the engine 10 is connected with the flue gas cooling water heat exchanger 8 in series. The hot water partially or entirely passes through the subcooler 9. In the embodiment, part of hot water flows through the cooler 9, absorbs the heat of the refrigerant liquid from the subcooler 9, is heated, then flows to the first heat exchanger 15 together with the other part of hot water to absorb the condensation heat of the refrigerant, is heated, then flows through the cylinder liner of the engine 10 and the flue gas cooling water heat exchanger 8 in sequence to absorb heat, and is heated, and finally high-temperature hot water is output.
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 engine-driven large-temperature-difference high-temperature heat pump hot water unit provided by the embodiment has a heating mode, and the specific working process is as follows:
as shown in fig. 5, the engine 10 drives the compressor 12 through the transmission 11 to compress the refrigerant gas and discharge the compressed refrigerant gas to the oil separator 30, the separated lubricating oil returns to the compressor 12 through the lubricating oil circuit 31, the separated refrigerant gas enters the first heat exchanger 15 through the first refrigerant inlet, and the refrigerant gas releases heat and condenses in the first heat exchanger 15 to become a refrigerant liquid. The refrigerant liquid discharged from the first refrigerant outlet of the first heat exchanger 15 continues to release heat and cool through the subcooler 9, passes through the first pipeline 18, is divided 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, and returns to the compressor 12 through the air supplementing 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 circulation port 23 to absorb heat, is evaporated and converted into a refrigerant gas, and then returns to the compressor 12 through the suction port 13.
< example five >
Fig. 7 is a schematic connection and flow diagram of the peripheral part of an engine-driven large-temperature-difference high-temperature heat pump hot water unit according to a fifth embodiment of the present invention. The difference between the sixth embodiment and the fifth embodiment is mainly the connection and the flow of the peripheral portions.
As shown in fig. 7, the flue gas discharged from the engine 10 sequentially enters the flue gas cooling water heat exchanger 8 and the flue gas refrigerant heat exchanger 17 in the smoke exhaust duct 28 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 smoke exhaust port 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, and the radiator 147 and the flue gas cooling water heat exchanger 8 are connected in series. The cooling water outlet of the radiator 147, the cooling water pump 138 and the cooling water inlet of the cylinder liner of the engine 10 are connected in sequence, and the cooling water enters the cylinder liner of the engine 10 after being pressurized by the cooling water pump 138 to absorb heat and raise temperature, then flows to the front 7 of the radiator to release heat to hot water and then flows back to the cooling water pump 138.
Part or all of the hot water flows through the subcooler 9, in this embodiment, the hot water flows through the subcooler 9, absorbs the heat of the refrigerant liquid from the subcooler 9, heats up, then flows to the first heat exchanger 15 to absorb the condensation heat of the refrigerant, heats up, then flows through the radiator 147 and the flue gas cooling water heat exchanger 8 in sequence to absorb heat, heats up, and finally outputs high-temperature hot water.
The thermostat 140 is connected to the cylinder jacket cooling water outlet of the engine 10, the radiator 147, and the inlet of the cooling water pump 138, respectively. When the temperature of the cooling water leaving the cylinder sleeve of the engine 10 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 enters the radiator 147 and flows back. The 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.
< example six >
Fig. 8 is a schematic connection and flow diagram of the peripheral part of an engine-driven large temperature difference high temperature heat pump hot water unit according to a sixth embodiment of the present invention. The seventh embodiment is different from the fifth embodiment mainly in the connection and flow of the peripheral portions.
As shown in fig. 8, the flue gas discharged from the engine 10 sequentially enters the flue gas cooling water heat exchanger 8 and the flue gas refrigerant heat exchanger 17 in the smoke exhaust duct 28 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 smoke exhaust port 130, and the water condensed from the flue gas enters the neutralization tank 145 through the water condensing 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. The cooling water outlet of the radiator 147, the cooling water pump 138, the cylinder liner of the engine 10 and the flue gas cooling water heat exchanger 8 are sequentially connected, the cooling water is pressurized by the cooling water pump 138 and then enters the cylinder liner of the engine 10 to absorb heat and raise the temperature, then flows through the flue gas cooling water heat exchanger 8 to continue to absorb the residual heat of the flue gas to raise the temperature, and then flows to the radiator to release heat to hot water and then flows back to the cooling water pump 138.
The hot water partially or entirely passes through the subcooler 9. In the embodiment, part of hot water flows through the cooler 9, absorbs heat of refrigerant liquid from the subcooler 9, is heated, then is converged with the other part of hot water in the first heat exchanger 15, absorbs heat of condensation of the refrigerant, is heated, then flows through the radiator 147, absorbs heat, and is heated, and finally high-temperature hot water is output.
The thermostat 140 is respectively connected with the cooling water outlet of the flue gas cooling water heat exchanger 8, the radiator 147 and the inlet pipeline of the cooling water pump 138. When the temperature of the cooling water entering the thermostat 140 of the flue gas cooling water heat exchanger 8 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 enters the radiator 147 and flows back. The 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 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.
Claims (10)
1. The utility model provides a big difference in temperature high temperature heat pump hot water unit of engine drive, includes compressor, first heat exchanger, second heat exchanger, economizer and engine, the compressor has gas vent, induction port and tonifying qi mouth, the engine has the engine cylinder liner, its characterized in that still includes:
a flue gas refrigerant heat exchanger, a flue gas cooling water heat exchanger and a subcooler,
wherein, the refrigerant from the exhaust port is condensed into liquid by heat release of the first heat exchanger and divided into two paths after passing through the subcooler for heat release, wherein one path passes through the economizer for heat release and temperature reduction and returns to the compressor from the air suction port after absorbing heat and evaporating by the second heat exchanger, and the other path passes through the economizer and returns to the compressor from the air supplement port after absorbing heat and evaporating by the flue gas refrigerant heat exchanger,
after part or all of the hot water flows through the subcooler and absorbs the liquid heat of the refrigerant, all of the hot water flows into the first heat exchanger to absorb the condensation heat of the refrigerant, and then directly or indirectly absorbs heat from the engine cylinder sleeve and the flue gas cooling water heat exchanger in sequence.
2. The engine-driven large temperature difference high temperature heat pump water heater unit according to claim 1, further comprising:
a cooling water pump and a radiator are arranged in the cooling water tank,
wherein the radiator, the cooling water pump and the engine cylinder sleeve are sequentially connected, cooling water enters the engine cylinder sleeve after being pressurized by the cooling water pump to absorb heat and raise temperature, then flows to the radiator to release heat to the hot water and then flows back to the cooling water pump,
the first heat exchanger is connected with the radiator in series, the radiator is also connected with the flue gas cooling water heat exchanger in series, and the hot water from the first heat exchanger sequentially flows through the radiator and the flue gas cooling water heat exchanger to absorb heat and raise temperature.
3. The engine-driven large temperature difference high temperature heat pump water heater unit according to claim 1, further comprising:
a cooling water pump and a radiator are arranged in the cooling water tank,
wherein the radiator, the cooling water pump, the engine cylinder sleeve and the flue gas cooling water heat exchanger are sequentially connected, the cooling water is pressurized by the cooling water pump and then sequentially enters the engine cylinder sleeve and the flue gas cooling water heat exchanger to absorb heat and raise temperature, then flows to the radiator to release heat to the hot water and then flows back to the cooling water pump,
the first heat exchanger and the radiator are connected in series, and the hot water from the first heat exchanger flows through the radiator to absorb heat and raise temperature.
4. The engine-driven large temperature difference high temperature heat pump water heater unit according to claim 2 or 3, characterized by further comprising:
a cooling water refrigerant heat exchanger in series with the radiator,
the operation modes of the engine-driven large-temperature-difference high-temperature heat pump hot water unit comprise a heating mode and a defrosting mode, and in the defrosting mode, the cooling water flows through the cooling water refrigerant heat exchanger to heat the refrigerant in the cooling water refrigerant heat exchanger into refrigerant gas and then flows into the radiator.
5. The engine-driven large temperature difference high temperature heat pump water heater unit according to claim 2 or 3, characterized by further comprising:
a temperature-saving device for the temperature of the water tank,
wherein the cooling water is pressurized by the cooling water pump, flows through the engine cylinder sleeve to absorb heat and is heated, and then enters the thermostat,
when the temperature of the cooling water entering the thermostat is low, the cooling water directly flows back to the cooling water pump from the thermostat;
when the temperature of the cooling water entering the thermostat is high, the cooling water flows through the radiator again to release heat and then flows back to the cooling water pump.
6. The engine-driven large temperature difference high temperature heat pump water heater unit according to claim 1, characterized in that:
the first heat exchanger is connected with the engine cylinder sleeve in series, the engine cylinder sleeve is connected with the flue gas cooling water heat exchanger in series, and the hot water from the first heat exchanger sequentially flows through the engine cylinder sleeve and the flue gas cooling water heat exchanger to absorb heat and raise temperature.
7. The engine-driven large-temperature-difference high-temperature heat pump water heating unit according to claim 1, characterized in that:
all the hot water is divided into two paths, one path of the hot water flows through the subcooler and then enters the first heat exchanger, and the other path of the hot water directly flows into the first heat exchanger.
8. The engine-driven large-temperature-difference high-temperature heat pump water heating unit according to claim 1, characterized in that:
the temperature of the hot water flowing into the engine-driven large-temperature-difference high-temperature heat pump hot water unit is 40-60 ℃, and the temperature of the hot water flowing out of the engine-driven large-temperature-difference high-temperature heat pump hot water unit is 85-90 ℃.
9. The engine-driven large-temperature-difference high-temperature heat pump water heating unit according to claim 1, characterized in that:
wherein the flue gas refrigerant heat exchanger is any one of a finned 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 is stainless steel.
10. The engine-driven large-temperature-difference high-temperature heat pump water heating unit according to claim 1, characterized in that:
wherein the cooling water is one of antifreeze, softened water and desalted water,
the hot water is softened water or desalted water.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202210149027.1A CN114440445B (en) | 2022-02-18 | Engine-driven high-temperature-difference high-temperature heat pump water heater unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN202210149027.1A CN114440445B (en) | 2022-02-18 | Engine-driven high-temperature-difference high-temperature heat pump water heater unit |
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| CN114440445A true CN114440445A (en) | 2022-05-06 |
| CN114440445B CN114440445B (en) | 2024-04-26 |
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