CN112361654A - Heat pump driven by gas engine - Google Patents
Heat pump driven by gas engine Download PDFInfo
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- CN112361654A CN112361654A CN202011174936.8A CN202011174936A CN112361654A CN 112361654 A CN112361654 A CN 112361654A CN 202011174936 A CN202011174936 A CN 202011174936A CN 112361654 A CN112361654 A CN 112361654A
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- Prior art keywords
- heat exchanger
- refrigerant
- economizer
- flue gas
- gas
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/06—Heat pumps characterised by the source of low potential heat
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B43/00—Engines characterised by operating on gaseous fuels; Plants including such engines
- F02B43/10—Engines or plants characterised by use of other specific gases, e.g. acetylene, oxyhydrogen
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B63/00—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/30—Use of alternative fuels, e.g. biofuels
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Combustion & Propulsion (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The invention discloses a heat pump driven by a gas engine, which comprises the gas engine, a cylinder sleeve water heat exchanger, a transmission device, a compressor, a first refrigerant heat exchanger, a second refrigerant heat exchanger, a first throttling device, a first flue gas heat exchanger and a second flue gas heat exchanger. The second flue gas heat exchanger is arranged on a first flue of the gas engine, and the refrigerant side of the second flue gas heat exchanger is connected with the refrigerant side of the economizer in series or in parallel. The high-grade flue gas waste heat discharged by the engine is directly radiated to the cylinder sleeve water through the first flue gas heat exchanger, and then is radiated to hot water or air through the cylinder sleeve water heat exchanger for direct waste heat utilization. The refrigerant is heated and gasified by the low-grade flue gas waste heat in the second flue gas heat exchanger, then enters the inlet of the compressor economizer, is compressed again to improve the grade, and then is used for heat dissipation through the second refrigerant heat exchanger. The invention realizes the grading and high-efficiency use of the flue gas waste heat.
Description
Technical Field
The invention relates to a heat pump, in particular to a heat pump driven by a gas engine.
Background
The heat pump driven by the gas engine has continuous progress, and is widely applied to the field of refrigeration and heating. The heat pump units driven by the gas engine popular in the market are mostly small multi-split air-conditioning units developed by companies such as Japan Mars, Sanyo and the like, are mostly used for family residences, small businesses or small office buildings, have limited use occasions, particularly fail to realize graded utilization of the waste heat of the engine smoke, and have remarkable economic and social benefits when developing a heat pump driven by the gas engine along with implementation of a sustainable development strategy, continuous strengthening of energy conservation and environmental protection awareness and promotion of a northern winter coal supply and gas change policy.
Chinese patent CN101865501B discloses a semi-heat recovery type GHP gas engine driven air conditioner/heat pump unit, in which a refrigerant heat recovery heat exchanger is arranged in a refrigerant system, a cooling water heat recovery heat exchanger is arranged in the engine system, and a domestic hot water loop is connected in series with the refrigerant heat recovery heat exchanger and the cooling water heat recovery heat exchanger. The flue gas heat exchanger only has one flue gas heat exchanger, and the flue gas in the flue gas heat exchanger is radiated to cylinder liner water, and the exhaust gas temperature is high, and the recovered flue gas heat is less, and the condensation heat recovery to the flue gas is difficult to realize, causes the flue gas waste heat utilization insufficient.
Japanese patent JP2001248935A discloses a method for recovering engine waste heat in an engine heat pump, where heat from engine exhaust gas is absorbed by cylinder water in a flue gas heat exchanger and refrigerant in a second auxiliary heat exchanger. After the flue gas in the flue gas heat exchanger radiates heat to the cylinder liner water, the cylinder liner water radiates heat to the refrigerant in the first auxiliary heat exchanger arranged on the path of the indoor heat exchanger and the return compressor, and the second auxiliary heat exchanger is arranged on the path of the indoor heat exchanger and the return compressor. The flue gas heat recovery volume of this patent is big, but the flue gas heat energy all transmits the return circuit of breathing in of compressor, and this heat energy is all consumed the power compression by the compressor and just can realize flue gas heat utilization through heat pump technology, and the high temperature part in the flue gas heat can not directly utilize through the heat transfer.
Chinese patent CN201610203393.5 discloses a gas-driven air source heat pump heat supply unit for central heating system, in which a flue gas waste heat recoverer is arranged on a flue gas pipeline of an internal combustion engine, a water outlet pipeline of the flue gas waste heat recoverer is connected with a water supply pipeline of the heating system, a flue gas secondary heat exchanger is used as a second evaporator of the heat pump, a refrigerant flows through a first evaporator first and then flows through the second evaporator to return to a compressor, and the flue gas pipeline is further connected with a defrosting device of the first evaporator. Japanese patent JP2001248935A has been improved to this patent, has realized the hierarchical waste heat recovery of flue gas, but the heating water directly passes through flue gas waste heat recoverer, and heating hot water quality of water is not good easily causes the scale deposit of flue gas waste heat recoverer, flue gas waste heat recoverer efficiency greatly reduced. The pressure and the temperature of the heating water are high and exceed the pressure bearing of a water connecting pipe of a cylinder sleeve of the engine; the direct access can lead to the clamp type rubber connecting piece of the water pipeline of the cylinder sleeve to fall off and burst. The flue gas is low in temperature and high in humidity after being subjected to heat dissipation by the flue gas waste heat recoverer and the flue gas secondary heat exchanger, so that a frost layer covered on the surface of the air source evaporator is not melted enough, and even the frost layer is thickened and encrypted.
Therefore, a new gas engine driven heat pump with reasonable structural design, high heat energy recovery and utilization rate and safe and stable operation is needed to at least solve the problems existing in the prior art.
Disclosure of Invention
In order to make up for the defects of the prior art, the invention provides the novel heat pump driven by the gas engine, which has reasonable structural design, high heat energy recovery utilization rate and safe and stable operation.
The technical scheme adopted by the invention for solving the technical problems is as follows:
the invention provides a heat pump driven by a gas engine, which comprises the gas engine, a cylinder sleeve water heat exchanger, a compressor, a first refrigerant heat exchanger, a second refrigerant heat exchanger, a first flue gas heat exchanger, a second flue gas heat exchanger and an economizer, wherein the first flue gas heat exchanger and the second flue gas heat exchanger are arranged on a first flue of the gas engine, the first flue gas heat exchanger is connected with the cylinder sleeve water heat exchanger through a pipeline, the compressor is connected with the gas engine through a transmission device, the second flue gas heat exchanger is connected with the economizer through a pipeline in series or in parallel and then is connected with the compressor through a pipeline, and the economizer and the compressor are respectively connected with the second refrigerant heat exchanger through pipelines.
Optionally, the economizer is piped to the first refrigerant heat exchanger.
Optionally, the method further comprises: the first throttling device is arranged between the economizer and the first refrigerant heat exchanger and used for throttling the refrigerant flowing out of the economizer; and the second throttling device is arranged between the economizer and the second refrigerant heat exchanger and used for throttling the refrigerant flowing into the economizer.
Optionally, the condensed refrigerant liquid in the second refrigerant heat exchanger is divided into two paths of refrigerant liquid which flow into the economizer, one path of refrigerant liquid flows into the economizer, and after the refrigerant liquid is throttled by the second throttling device and cools the rest of refrigerant liquid in the other path of the economizer, the refrigerant liquid flows through the second flue gas heat exchanger to become refrigerant gas, and then the refrigerant gas flows back to the compressor; and after being cooled, the refrigerant liquid in the other path flows into the first refrigerant heat exchanger after being throttled by the first throttling device, absorbs heat energy of external air or water in the first refrigerant heat exchanger, and then flows back to the compressor.
Optionally, the condensed refrigerant liquid in the second refrigerant heat exchanger is divided into two paths, one path flows into the economizer, the other path is divided into two branches, the refrigerant in the first branch is heated into refrigerant gas through the second flue gas heat exchanger, the refrigerant in the second branch is throttled by the second throttling device and cools the rest refrigerant liquid in the economizer to form refrigerant gas, and the refrigerants in the first branch and the second branch flow back to the compressor after being converged; after being cooled, the refrigerant liquid in the economizer flows into the first refrigerant heat exchanger after being throttled by the first throttling device, and flows back to the compressor after absorbing heat energy of outside air or water in the first refrigerant heat exchanger.
Optionally, the method further comprises: an oil separator for separating lubricating oil from refrigerant gas discharged from the compressor; and the four-way reversing valve is arranged on pipelines between the oil separator and the second refrigerant heat exchanger and between the first refrigerant heat exchanger and the compressor.
Optionally, a third throttling device is further included, and is arranged on the refrigerant pipeline of the second flue gas heat exchanger.
Optionally, the system further comprises a cylinder liner water pump, and the cylinder liner water pump is used for boosting the cylinder liner water after the cylinder liner water is heated in the first flue gas heat exchanger and the cylinder liner of the gas engine respectively, so as to discharge heat through the cylinder liner water heat exchanger.
Optionally, a steam generator is arranged in the smoke exhaust flue between the gas engine and the first smoke heat exchanger, and water absorbs heat of high-temperature smoke in the steam generator to generate steam.
Compared with the prior art, the invention has the following advantages:
(1) the heat energy of the flue gas is utilized in stages. The high-grade flue gas waste heat is directly radiated to the cylinder sleeve water through the first flue gas heat exchanger, and then is radiated to hot water or air through the cylinder sleeve water heat exchanger for direct waste heat utilization. The refrigerant is heated and gasified by the low-grade flue gas waste heat in the second flue gas heat exchanger, then is sucked in through the compressor economizer inlet, is used through heat dissipation of the second refrigerant heat exchanger after being compressed and upgraded, and the pressure of the refrigerant at the suction inlet of the compressor economizer is higher than that of the suction inlet of the compressor, so that the energy consumption of the compressor is better reduced than that of JP2001248935A and Chinese patent CN 201610203393.5.
(2) The heat transfer temperature difference between the flue gas and the cylinder sleeve water in the first flue gas heat exchanger is large, the heat exchange temperature difference between the flue gas and the refrigerant in the second flue gas heat exchanger is large, and the first flue gas heat exchanger and the second flue gas heat exchanger are small in heat exchange area, compact in structure and low in heat exchanger cost.
(3) In the prior art, hot water directly flows into the flue gas heat exchanger, and if the quality of the heating hot water is poor, the scale of the flue gas waste heat recoverer is easy to cause, and the efficiency of the flue gas waste heat recoverer is greatly reduced.
The advantages and features of the present invention are described in detail below with reference to the accompanying drawings.
Drawings
FIG. 1 is a flow diagram of one embodiment of a gas engine driven heat pump of the present invention;
FIG. 2 is a flow diagram of an embodiment of a gas engine driven heat pump of the present invention;
FIG. 3 is a three-flow diagram of one embodiment of a gas engine driven heat pump of the present invention;
FIG. 4 is a flow diagram of a fourth embodiment of a gas engine driven heat pump of the present invention;
FIG. 5 is a flue gas extraction embodiment of a gas engine driven heat pump of the present invention;
FIG. 6 is a cylinder liner water heat exchange and steam generator embodiment of a gas engine driven heat pump of the present invention.
Description of the figure numbering: 1. the system comprises a gas engine, 2, a compressor, 3, a first refrigerant heat exchanger, 4, a second refrigerant heat exchanger, 5, a first throttling device, 6, a second throttling device, 7, an economizer, 8, a first flue gas heat exchanger, 9, a second flue gas heat exchanger, 13, a four-way reversing valve, 14, a cylinder sleeve water heat exchanger, 16, an oil separator, 18, a transmission device, 19, a first one-way valve, 20, a second one-way valve, 21, a third one-way valve, 22, a fourth one-way valve, 23, a drying filter, 27, an intercooler, 31, an economizer first valve, 34, hot water, 36, a third throttling device, 40, a compressor lubricating oil loop, 41, a cylinder sleeve water loop, 42, a first flue gas valve, 43, a second flue gas valve, 130, a first flue, 138, a cylinder sleeve water pump, 139, a second flue and a steam generator.
Detailed Description
In order to make the objects, embodiments and advantages of the embodiments of the present invention clearer, the following description of the present invention with reference to the accompanying drawings makes a more complete description of the present invention so that those skilled in the art can better understand the present invention and can implement the present invention, but the present invention is not limited to the illustrated embodiments.
It should be noted that the term "connected" as used herein includes both direct connection and indirect connection of two components through other components. The valve, the one-way valve, the four-way reversing valve and the like are necessary or unnecessary components.
Fig. 1 shows a first embodiment of a heat pump driven by a gas engine according to the present invention, which includes a gas engine 1, a compressor 2, a first refrigerant heat exchanger 3, a second refrigerant heat exchanger 4, a first throttling device 5, a first flue gas heat exchanger 8, a second flue gas heat exchanger 9, a four-way reversing valve 13, a cylinder liner water heat exchanger 14, an oil separator 16, a transmission device 18, a first check valve 19, a second check valve 20, a third check valve 21, a fourth check valve 22, a drying filter 23, an economizer first valve 31, hot water 34, a third throttling device 36, a compressor lubricating oil circuit 40, a cylinder liner water circuit 40, a first flue 41, and a cylinder liner water pump 138. Wherein, the economizer 7 has the function of a heat exchanger for improving the heat exchange efficiency. Which absorbs heat by throttling evaporation of the refrigerant itself to subcool another portion of the refrigerant.
The gas engine 1 and the compressor 2 are connected by a transmission 18. The gas engine 1 is a natural air suction or turbocharging type, and an air inlet filtering pipeline, a gas inlet pipeline, a smoke silencer and the like which are attached to the gas engine belong to the prior art and are not described again. The transmission 18 is in the form of one of a change speed gearbox, a pulley or a flywheel disc, connected at one end to the engine and at the other end to the compressor, to transmit the power of the gas engine 1 to the compressor 2. The rotating speed of the gas engine 1 is continuously adjustable, and the rotating speed of the gas engine 1 under different operating conditions is adjusted to adjust the rotating speed of the compressor 2, so that the gas engine 1 drives the compressor 2. The compressor 2, the first refrigerant heat exchanger 3, the second refrigerant heat exchanger 4, the first throttling device 5, the second flue gas heat exchanger 9, the four-way reversing valve 13, the cylinder liner water heat exchanger 14, the oil separator 16, the first check valve 19, the second check valve 20, the third check valve 21, the fourth check valve 22, the drying filter 23, the economizer first valve 31, the third throttling device 36 and the compressor lubricating oil loop 40 form a vapor compression heat pump cycle with an economizer. The compressor 2 has an economizer suction inlet. The compressor 2 is one of an open-type screw compressor, an open-type single-machine two-stage screw compressor, an open-type magnetic suspension centrifugal compressor, an open-type single-machine two-stage magnetic suspension centrifugal compressor, an open-type scroll compressor and an open-type single-machine two-stage scroll compressor. The refrigerant in the compressor 2 is one of NH3, R718, HCFC22, HFC134a, HFC407C, HFC410a, HFC245fa, HFC507A, HFO1234yf and HFO1234 zf. The first throttling device 5 and the second throttling device 6 are one of an electronic expansion valve, a thermal expansion valve, a capillary tube and a ball float valve.
High-temperature flue gas generated after the mixed combustion of the fuel gas and the air in the gas engine 1 flows through the first flue gas heat exchanger 8 in the first flue 130, and a part of flue gas waste heat is dissipated into the cylinder liner water. The liner water flows through the first flue gas heat exchanger 8 in the liner water pipeline 41 to be heated, then flows through the liner of the gas engine 1 to be heated, and flows through the liner water heat exchanger 14 after being boosted by the liner water pump 138 installed on the gas engine 1, and the heat is discharged to the external hot water 34 (the hot water with low temperature, for example, the hot water with 30 ℃ to higher temperature) for waste heat utilization. The first flue gas heat exchanger 8 is one of a plate-shell type heat exchanger, a plate-fin type heat exchanger and a fin-tube type heat exchanger.
In the heating mode, the refrigerant gas containing the lubricant oil discharged from the compressor 2 first passes through the oil separator 16, and the separated lubricant oil flows back to the compressor 2 through the compressor lubricant oil circuit 40. The refrigerant gas flowing out of the oil separator 16 continues to pass through the four-way reversing valve 13 to the second refrigerant heat exchanger 4, and heat in the refrigerant gas is condensed in the second refrigerant heat exchanger 4 and discharged to external water or air, so that heat energy utilization is realized. The refrigerant liquid condensed in the second refrigerant heat exchanger 4 passes through the second check valve 20, passes through the dry filter 23, and the economizer 7. In the economizer 7, a part of refrigerant liquid is throttled by the second throttling device 6 and then becomes low-temperature low-pressure gas-liquid two-phase refrigerant, and after cooling the rest refrigerant liquid in the economizer 7, the low-temperature low-pressure gas-liquid two-phase refrigerant flows through the second flue gas heat exchanger 9 and becomes refrigerant gas, and then flows back to the economizer port of the compressor 2 through the economizer first valve 31. The economizer first valve 31 is one of a check valve, a solenoid valve, or an electric ball valve. After being cooled, the refrigerant liquid in the economizer 7 is throttled by the first throttling device 5, flows through the third check valve 21 to the first refrigerant heat exchanger 3, and absorbs heat energy of the outside air or water in the first refrigerant heat exchanger 3. In the heating mode, the first check valve 19 and the fourth check valve 22 are closed.
In the heating mode, the flue gas flowing out of the first flue gas heat exchanger 8 flows through the second flue gas heat exchanger 9 again, heat dissipation is continued to the refrigerant flowing out of the economizer 7 in the second flue gas heat exchanger 9, and the refrigerant is changed into a gaseous state after absorbing the waste heat of the flue gas in the second flue gas heat exchanger 9. The second flue gas heat exchanger 9 is one of a plate-shell type heat exchanger, a plate-fin type heat exchanger and a fin-tube type heat exchanger.
Fig. 2 is a second embodiment of a gas engine driven heat pump of the present invention, fig. 2 differing from fig. 1 in that the second flue gas heat exchanger 9 is changed from being in series with the refrigerant side of the economizer 7 to being in parallel. In the heating mode, after the refrigerant liquid condensed by the second refrigerant heat exchanger 4 passes through the second one-way valve 20 and flows through the drying filter 23, one path of refrigerant liquid is throttled by the third throttling device 36 to become gas-liquid two-phase refrigerant, and flows through the second flue gas heat exchanger 9 to become refrigerant gas; the other path of refrigerant liquid flows into the economizer 7, in the economizer 7, a part of refrigerant liquid is throttled by the second throttling device 6 and then becomes low-temperature low-pressure gas-liquid two-phase refrigerant, the low-temperature low-pressure gas-liquid two-phase refrigerant cools the rest of refrigerant liquid in the economizer 7 and then becomes refrigerant gas, and the refrigerant gas is converged with the refrigerant gas flowing out of the second flue gas heat exchanger 9 and then flows back to the economizer port of the compressor 2 through the economizer first valve 31. The economizer first valve 31 is one of a check valve, a solenoid valve, or an electric ball valve. After being cooled, the refrigerant liquid in the economizer 7 is throttled by the first throttling device 5, flows through the third one-way valve 21 to the first refrigerant heat exchanger 3, absorbs the heat energy of the external air or water in the first refrigerant heat exchanger 3, and finally flows back to the suction port of the compressor through the four-way reversing valve 13. In the heating mode, the first check valve 19 and the fourth check valve 22 are closed.
Fig. 3 shows a third embodiment of the heat pump driven by the gas engine according to the present invention, which includes the gas engine 1, the compressor 2, the first refrigerant heat exchanger 3, the second refrigerant heat exchanger 4, the first throttling device 5, the second throttling device 6, the economizer 7, the first flue gas heat exchanger 8, the second flue gas heat exchanger 9, the cylinder liner water heat exchanger 14, the oil separator 16, the transmission device 18, the economizer first valve 31, the hot water 34, the compressor lubricating oil circuit 40, the cylinder liner water circuit 41, the first flue 130, and the cylinder liner water pump 138.
In the heating mode, the refrigerant gas containing the lubricant oil discharged from the compressor 2 first passes through the oil separator 16, and the separated lubricant oil flows back to the compressor 2 through the compressor lubricant oil circuit 40. The refrigerant gas flowing out of the oil separator 16 continues to pass through the four-way reversing valve 13 to the second refrigerant heat exchanger 4, and heat in the refrigerant gas is condensed in the second refrigerant heat exchanger 4 and discharged to external water or air, so that heat energy utilization is realized. The refrigerant liquid condensed in the second refrigerant heat exchanger 4 flows into the economizer 7, in the economizer 7, a part of the refrigerant liquid is throttled by the second throttling device 6 and then is changed into low-temperature low-pressure gas-liquid two-phase refrigerant, one path of low-temperature low-pressure gas-liquid two-phase refrigerant cools the rest refrigerant liquid in the economizer 7 and then is changed into refrigerant gas, the other path of low-temperature low-pressure gas-liquid two-phase refrigerant flows through the second flue gas heat exchanger 9 and is changed into refrigerant gas, and after the two paths of refrigerant gas are converged, the refrigerant gas flows back to the economizer port of the compressor 2 through the economizer first valve 31. The economizer first valve 31 is one of a check valve, a solenoid valve, or an electric ball valve. After being cooled, the refrigerant liquid in the economizer 7 enters the first refrigerant heat exchanger 3 after being throttled by the first throttling device 5, and the heat energy of the outside air or water is extracted in the first refrigerant heat exchanger 3. In the heating mode, the first check valve 19 and the fourth check valve 22 are closed.
In the heating mode, the flue gas flowing out of the first flue gas heat exchanger 8 flows through the second flue gas heat exchanger 9 again, heat dissipation is continued to the refrigerant flowing out of the economizer 7 in the second flue gas heat exchanger 9, and the refrigerant is changed into a gaseous state after absorbing the waste heat of the flue gas in the second flue gas heat exchanger 9. The second flue gas heat exchanger 9 is one of a plate-shell type heat exchanger, a plate-fin type heat exchanger and a fin-tube type heat exchanger.
Fig. 4 shows a fourth embodiment of the heat pump driven by the gas engine according to the present invention, and the difference between fig. 4 and fig. 3 is that the refrigerant sides of the second flue gas heat exchanger 9 and the economizer 7 are changed from series connection to parallel connection, one path of the refrigerant liquid flowing out of the second refrigerant heat exchanger 4 is changed into a gas-liquid two-phase refrigerant after being throttled by the second throttling device 6, the refrigerant liquid flowing to the first refrigerant heat exchanger 3 is cooled by the economizer 7 and then changed into a gas refrigerant, the other path of the refrigerant liquid is throttled by the third throttling device 36 and then changed into a gas refrigerant after absorbing the residual heat of the flue gas in the second flue gas heat exchanger 9, and the two paths of the gas refrigerant are converged and then flow through the economizer first valve 31 of the economizer to return. The third throttling device 36 is one of an electronic expansion valve, a thermostatic expansion valve, a capillary tube and a ball float valve. The rest of fig. 4 is the same as fig. 3.
Fig. 5 shows an embodiment of the smoke evacuation portion of a gas engine driven heat pump of the present invention. The embodiment of fig. 1 and 3 incorporates a first flue valve 42 in the first flue 130 and a second flue valve 43 in the second flue 139. In the heating mode, the first flue gas valve 42 is opened, the second flue gas valve 43 is closed, and flue gas flowing out of the first flue gas heat exchanger 8 flows through the third flue gas heat exchanger 10 to exchange heat with the refrigerant.
FIG. 6 is a cylinder liner water heat exchange and steam generator embodiment of a gas engine driven heat pump of the present invention. The engine 1 is a turbocharged engine with an intercooler 27. The flue gas discharged by the gas engine 1 is radiated to the cylinder liner water in the first flue gas heat exchanger 8. In the cylinder liner water pipeline 41, the cylinder liner water absorbs the residual heat of the flue gas in the first flue gas heat exchanger 8 to raise the temperature, then the temperature of the cylinder liner flowing through the gas engine 1 is continuously raised, the pressure of the cylinder liner water flowing through the cylinder liner water heat exchanger 14 is raised by the cylinder liner water pump 138 installed on the gas engine 1, and the heat is discharged to the external hot water or air to utilize the residual heat. The cylinder liner water flowing out of the cylinder liner water heat exchanger 14 flows through the intercooler to be heated and then flows to the first flue gas heat exchanger 8 to complete a cycle. The high-temperature flue gas discharged from the gas engine 1 flows into the steam generator 140 to exchange heat with water, and steam is generated. The first flue gas heat exchanger 8 is one of a plate-shell type heat exchanger, a plate-fin type heat exchanger and a fin-tube type heat exchanger. The liner water heat exchanger 14 is one or a combination of a water-water or water-air heat exchanger. The cylinder liner water heat exchanger 14 is one of a plate heat exchanger, a shell-and-tube heat exchanger, a plate fin heat exchanger, and a fin tube heat exchanger. The steam generator 140 is one of a plate-shell heat exchanger, a plate-fin heat exchanger, and a fin-tube heat exchanger.
In the description of the present invention, it is to be understood that the terms "upper", "lower", "front", "back", "inner", "outer", and the like, indicate orientations and positional relationships based on the orientations and positional relationships shown in the drawings, and are used for convenience in describing the present invention, but do not indicate or imply that the referred devices or elements must have a specific orientation, be constructed and operated in a specific orientation. The terms "mounted," "disposed," "connected," and "means" are to be construed broadly and therefore should not be construed to limit the invention. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
The present invention has been illustrated by the above embodiments, but it should be understood that the above embodiments are for illustrative and descriptive purposes only and are not intended to limit the invention to the scope of the described embodiments. 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 (9)
1. A gas engine driven heat pump characterized by: the heat pump comprises a gas engine, a cylinder sleeve water heat exchanger, a compressor, a first refrigerant heat exchanger, a second refrigerant heat exchanger, a first smoke heat exchanger, a second smoke heat exchanger and an economizer, wherein the first smoke heat exchanger and the second smoke heat exchanger are arranged on a first flue of the gas engine, the first smoke heat exchanger is connected with the cylinder sleeve water heat exchanger through a pipeline, the compressor is connected with the gas engine through a transmission device, the second smoke heat exchanger is connected with the economizer through a pipeline in series or in parallel, the second smoke heat exchanger is connected with the compressor through a pipeline, and the economizer and the compressor are respectively connected with the second refrigerant heat exchanger through pipelines.
2. A gas engine driven heat pump as set forth in claim 1, further comprising:
the first throttling device is arranged between the economizer and the first refrigerant heat exchanger and used for throttling the refrigerant flowing out of the economizer;
and the second throttling device is arranged between the economizer and the second refrigerant heat exchanger and used for throttling the refrigerant flowing into the economizer.
3. The gas engine driven heat pump according to claim 2, wherein the condensed refrigerant liquid in the second refrigerant heat exchanger flows into the economizer in two paths, one path flows into the economizer, and after being throttled by the second throttling device, the condensed refrigerant liquid in the other path in the economizer is cooled, flows through the second flue gas heat exchanger to become refrigerant gas, and then flows back to the compressor; and after being cooled, the refrigerant liquid in the other path flows into the first refrigerant heat exchanger after being throttled by the first throttling device, absorbs heat energy of external air or water in the first refrigerant heat exchanger, and then flows back to the compressor.
4. The gas engine driven heat pump according to claim 2, wherein the condensed refrigerant liquid in the second refrigerant heat exchanger is divided into two paths, one path flows into the economizer, the other path is divided into two branches, the refrigerant in the first branch is heated into refrigerant gas through the second flue gas heat exchanger, the refrigerant in the second branch is throttled by the second throttling device and is changed into refrigerant gas after cooling the rest refrigerant liquid in the economizer, and the refrigerant in the first branch and the refrigerant in the second branch are converged and then flow back to the compressor; after being cooled, the refrigerant liquid in the economizer flows into the first refrigerant heat exchanger after being throttled by the first throttling device, and flows back to the compressor after absorbing heat energy of outside air or water in the first refrigerant heat exchanger.
5. A gas engine driven heat pump as set forth in claim 1, further comprising:
an oil separator for separating lubricating oil from refrigerant gas discharged from the compressor;
and the four-way reversing valve is arranged on pipelines between the oil separator and the second refrigerant heat exchanger and between the first refrigerant heat exchanger and the compressor.
6. A gas engine driven heat pump according to claim 1, further comprising a third throttling means provided on the refrigerant line of the second flue gas heat exchanger.
7. The gas engine driven heat pump of claim 1, further comprising a liner water pump for boosting liner water after the liner water is heated in the first flue gas heat exchanger and the liner of the gas engine, respectively, to discharge heat through the liner water heat exchanger.
8. A gas engine driven heat pump according to claim 1, wherein the flue gas duct between the gas engine and the first flue gas heat exchanger is provided with a steam generator in which water absorbs heat from the high temperature flue gas to produce steam.
9. A gas engine driven heat pump as set forth in claim 1 wherein said economizer is piped to said first refrigerant heat exchanger.
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| CN202011174936.8A CN112361654A (en) | 2020-10-28 | 2020-10-28 | Heat pump driven by gas engine |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202011174936.8A CN112361654A (en) | 2020-10-28 | 2020-10-28 | Heat pump driven by gas engine |
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