Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
  • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
• • 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
  • F25B1/00—Compression machines, plants or systems with non-reversible cycle
  • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
  • F25B1/053—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of turbine type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B1/00—Compression machines, plants or systems with non-reversible cycle
  • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
• • 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
  • F25B27/00—Machines, plants or systems, using particular sources of energy
  • F25B27/02—Machines, plants or systems, using particular sources of energy using waste heat, e.g. from internal-combustion engines
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B30/00—Heat pumps
  • F25B30/02—Heat pumps of the compression type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • 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
  • F25B2400/07—Details of compressors or related parts
  • F25B2400/075—Details of compressors or related parts with parallel compressors
• • 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
  • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
  • Y02A30/00—Adapting or protecting infrastructure or their operation
  • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
  • Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine
• • 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
  • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
  • Y02E20/00—Combustion technologies with mitigation potential
  • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]

Definitions

• the invention relates to a method of operating a heat pump system, a heat pump system with at least two Ver ⁇ absorbers as well as a power plant, in particular a gas-and-steam combined-cycle power plant (hereinafter abbreviated: combined-cycle power plant) with an ER inventive heat pump system.
• thermo energy i.e. heat
• a heat source i.e. heat
• the absorbed thermal energy is brought by means of a compressor to an elevated pressure level and then liquefied at a condensing temperature which is higher than that of an evaporation temperature.
• the efficiency of a heat pump is measured by means of a Coefficient of Performance (COP), which is best given by the reciprocal efficiency of a Carnot process.
• COP Coefficient of Performance
• the Leis ⁇ tung number is 4.13.
• the liquefaction of the working fluid is carried out at a liquefaction temperature of 140 ° C.
• the evaporation temperature that is, the temperature at which the evaporation of the working fluid takes place, should be as high as possible. Furthermore, it is advantageous if the transmission of the thermal energy from the heat source to the working fluid with the smallest possible difference between the temperature of the heat source and the evaporation temperature.
• a plurality of various ⁇ the temperature controlled heat sources of their heat content can be used by a known heat pump or a known heat pump system is typically not efficient in terms. The majority of the heat of such heat sources therefore remains unused in the prior art.
• the present invention has for its object to improve the heat recovery or heat recovery from a plurality of different heat sources.
• a working fluid circulates within a controlled working cycle of the heat pump system.
• the Ar Beitsfluid is compressed by means of a compressor and liquefied with ⁇ means of a condenser.
• a mass flow of the working fluid before the lead is divided into at least a first and a second evaporator and at least applied in parallel to the first and second evaporators ⁇ leads, wherein the working fluid second at a first evaporation ⁇ pressure in the first evaporator and at a relative to the first evaporation pressure reduced Evaporating pressure in the second evaporator evaporates.
• the first evaporator is thermally coupled with a first heat source having a first heat source temperature and the second evaporator is thermally coupled with a second heat source having a lower second heat source temperature than the first heat source temperature.
• the mass flow of the working fluid is divided before the supply line to the first and second evaporator at least in a first and second partial mass flow, wherein the first partial mass flow to the first and the second partial mass flow directed to the second evaporator.
• the evaporation of the working fluid is carried out in two parallel process steps, that is, the evaporation of the working fluid takes place in two with respect to the mass ⁇ flow of the working fluid connected in parallel evaporators.
• the first evaporator to a ge ⁇ genüber enlarged the second evaporator evaporating pressure. Due to the second evaporation pressure, which is lower than the first evaporation pressure, the evaporation of the working fluid by means of the second evaporator takes place at a second evaporation temperature, which is reduced compared to a first evaporation temperature in the first evaporator.
• the thermal energy of Wär ⁇ mettlen is used in cascade.
• the heat sources are thus thermally coupled in series with the evaporators, with the temperature of the heat sources (heat source temperature) decreasing in series with the evaporators.
• the respective evaporation temperature that is in takes place, the temperature ⁇ tur the evaporation of the working fluid in the first and / or second evaporator, be adapted to the heat source temperature of the thermally oppel- with the respective evaporator th heat source.
• each evaporator is thermally coupled to a different heat source.
• the evaporators are connected in parallel with respect to the working cycle. This results in a multi-stage, at least two-stage evaporation of the working fluid at afford defenceli ⁇ chen pressure levels.
• Heat source side of the heat pump system allows. This can be used efficiently thermally with the heat pump system ⁇ a plurality of different temperatures heat sources (first and second heat source), the efficiency of the heat pump installation without reducing. In other words, it is possible whil efficiently with the present invention, a plurality of heat sources at different temperature levels ⁇ bind.
• the heat pump system according to the invention comprises at least ei ⁇ nen compressor, a condenser and at least a first and second evaporator, wherein the heat pump system comprises a directed working circuit for a circulating working fluid.
• the working cycle of the heat pump system is designed to divide a mass flow of the working fluid before a supply of the working fluid to the first and second evaporators and to supply them in parallel to the first and second evaporators, the first evaporator a first evaporation pressure and the second evaporator has a second evaporation pressure lower than the first evaporation pressure.
• the heat pump system comprises we ⁇ iquess first and second heat source, wherein the first heat source, a first heat source temperature and the second heat source has a relation to the first heat source temperature lower second heat source temperature, and the first heat source thermally connected to the first evaporator and the second heat source thermally coupled coupled to the second evaporator.
• the power plant according to the invention comprises a heat pump system according to the present invention.
• the power plant according to the invention comprises a heat pump system according to the present invention.
• the heat sources are designed as different temperature-controlled waste heat sources of the power plant.
• the first and second heat source each have a different waste heat of a power plant, in particular a gas and steam combined cycle power plant (combined cycle power plant).
• a waste heat from a flue gas and a second heat source is a waste heat from a transformer cooling is used as the first sources of heat ⁇ le.
• a waste heat of a flue ⁇ gases at least for one of the heat sources, a waste heat of a flue ⁇ gases, transformer cooling, transmission cooling, engine cooling, a condenser cooling a housing of a heat recovery steam generator, a gas turbine acoustic hood, a generator cooling and / or a lubricating medium supply.
• a multiplicity of waste heat sources of a power plant can thus be used for the recovery of thermal energy. This increases the efficiency of the power ⁇ plant.
• the working fluid in front of the supply line to the first evaporator a first expansion valve and in front of the supply line to the second evaporator a second expansion valve parallel ⁇ leads.
• relaxation or expansion of the working fluid preferably takes place in parallel by means of the first and second expansion valves .
• the working fluid is brought to the first and second evaporation pressure.
• the first expansion valve the first evaporation pressure in the first evaporator and by means of the second expansion valve the second evaporation pressure in the second evaporator is set.
• a first and a second compressor is used for compressing the working fluid, wherein the working fluid discharged from the first evaporator is supplied to the first compressor and the working fluid discharged from the second evaporator to the second compressor.
• the compression of the working fluid as already the evaporation of the working fluid, preferably pa ⁇ rallel.
• the mass flow of the working fluid is divided, passed to a first and second expansion valve, to ⁇ finally fed to a first and second evaporator and introduced after the first and second evaporator in the respective input of the first and second compressor. Consequently, the expansion, evaporation and compression of the working fluid by means of the two partial mass flows occur in parallel.
• first and the second compressor use a common motor shaft.
• a common compressor is used for compression, wherein the discharged from the first and second evaporator working fluid is supplied to the common compressor.
• the compression of the working fluid takes place in one process step, that is, in a common compressor.
• a common compressor in this case is a compressor in which the partial mass flows of the first and the second evaporator are introduced to compress the working fluid. This results in a efficien ⁇ te and preferred compression of the working fluid within the working circuit of the heat pump system.
• the being initiated from the first evaporator Ar ⁇ beitsfluid is preferred tet gelei- before inlet to the common compressor to a first check valve and being directed from the second Ver ⁇ steam working fluid prior to supply to the ge ⁇ common compressor to a second non-return valve.
• a common compressor which is designed as a multi-stage turbocompressor.
• the working fluid discharged from the first evaporator is supplied to a first compressor stage of the turbocompressor and the working fluid discharged from the second evaporator to a second compressor stage of the turbocompressor.
• the partial mass flows of the working fluid are thus brought together again via the compressor stages of the turbocompressor to form a mass flow.
• Characterized the mass flow of working increases beitsfluids within the turbo-compressor of the compressor stage at ⁇ to compressor stage.
• this makes it possible to dispense with the use of mass flow controllers, since the mass flow can be regulated by means of the compressor stages of the turbocompressor.
• a regulation of a partial mass flow of the first and / or second evaporator discharged working fluid before Zulei device to the common compressor is provided.
• the control can be done by means of mass flow controllers.
• the working fluid discharged from the first and second or the common compressor is directed to the condenser.
• the liquefaction of the working fluid advantageously takes place within the working cycle of the heat pump system in a common condenser.
• the working cycle of the heat pump system can be designed such that the working fluid conducted from the first evaporator to the first compressor and the working fluid discharged from the second evaporator to the second compressor are conducted.
• the working cycle of the heat pump system can be designed to direct the working fluid discharged from the first and second evaporators to the common compressor, in particular a multi-stage turbocompressor being provided for the common compressor.
• an expansionary ⁇ onsventil and / or at least one mass flow controller for Re gelung the mass flow and / or for the partial mass flows scheme may include at least the heat pump system.
• FIG. 1 Showing: a schematic diagram of a 9,pumpenanla ⁇ ge with five compressors, five evaporators and five different heat sources, the compressor and the evaporator are connected in parallel with respect to a mass flow of a working fluid of the heat pump system; a schematic diagram of a 9,pumpenanla ⁇ ge with a common compressor, five evaporators and five different heat sources, the evaporators are parallel maral ⁇ tet with respect to a mass flow of a working fluid of the heat pump system;
• Figure 3 is a further schematic circuit diagram of a heat pump ⁇ system with a turbo compressor, five evaporators and five different heat sources, the evaporator are connected in parallel with respect to a mass flow of the working fluid of the heat pump system; and
• Figure 4 is a pressure-enthalpy diagram of an embodiment of the method according to the invention. Similar, equivalent or equivalent elements Kings ⁇ NEN be provided in the figures with the same reference numerals.
• relative terms such as, for example, after a condenser or generally after or in front of an element of a heat pump system, with respect to a directed working To understand the circulation of the heat pump system.
• the working cycle of the heat pump system has a direction with respect to which a method step can take place after or in front of an element.
• the heat pump system 1 shows a circuit diagram of a réellepum ⁇ penstrom 1 is shown schematically.
• the heat pump system 1 comprises five evaporators 31,..., 35 and five compressors 21,..., 25. Furthermore, the heat pump system 1 has five expansion valves 51,..., 55.
• a condenser 4 is provided for liquefying a working fluid circulating within a directed working cycle 100 of the heat pump system 1.
• the five compressors 21, ..., 25 are arranged on a common motor shaft 10 ⁇ . In other words, the five compressors
• the mass flow will be ⁇ divided into five partial mass flows (indicated by reference numeral 102), JE the evaporator 31, ..., 35 exactly one of the five partial mass flows is supplied.
• Each of the five evaporators 31,..., 35 of the heat pump system 1 is in each case thermally coupled to a heat source 41,..., 45 assigned to it.
• the first heat source 41,..., 45 assigned to it For example, the first heat source
• waste heat sources 41 at least partially the waste heat of a flue gas
• the two ⁇ te heat source 42 at least partially the waste heat of a transformer cooling
• the third heat source 43 at least partially the waste heat of an engine cooling
• fourth heat source 44 at least partially the waste heat of a transmission ⁇ cooling.
• the abovementioned waste heat sources are typically present in power plants, in particular combined cycle power plants.
• the first heat source 41 having a heat source temperature (temperature of the heat source) of 90 ° C. comes in thermal contact with the first evaporator 31.
• the first evaporator 31 evaporates under a thermal absorption Energy from the first heat source 41.
• the second heat source 42 has a heat source temperature of 80 ° C. and is thermally coupled to the second evaporator 32.
• the third heat source 43 has a heat source temperature of 65 ° C and is thermally coupled to the third evaporator 33.
• the fourth heat source 44 has a heat source temperature of 55 ° C and is thermally coupled to the fourth evaporator 34.
• Another fifth heat source 45 is thermally coupled to the fifth evaporator 35.
• 41 have the heat sources, ..., 45, a different temperature or a Various ⁇ nes temperature level on.
• the thermal energy of the heat sources 41, ..., 45 is theoretically absorbed by the working fluid only by its evaporation (latent heat).
• latent heat In real heat pump system 1, an additional slight increase in the temperature of the working fluid, for example by 5 K (Graßtechnik in the heat ⁇ meübertragung) take place.
• the first heat source 41 After cooling the first heat source 41 by the first evaporator 31, the first heat source 41 has a temperature of 75 ° C.
• the second heat source 42 After the cooling of the second heat source 42 by the second evaporator 32, the second heat source 42 has a Tempe ⁇ temperature of 65 ° C.
• Analog comprise the third, fourth and fifth heat source 43, 44, 45 after each of them zugeord ⁇ Neten evaporators 33, 34, 35 each have a reduced tempering temperature on ⁇ .
• Heat pump system 1 thus takes place in at least five vapor ⁇ flash steps 411, ..., 415, the first evaporation step 411 in the first evaporator 31, an evaporation temperature of 70 ° C, the second evaporation step 412 in the second evaporation ⁇ fer 32 a vaporizing temperature of 60 ° C, the third evaporation step 413 in the third evaporator 33, an evaporation temperature of 50 ° C and the fourth evaporation step 414 in the fourth evaporator 34, an evaporation temperature of 40 ° C having.
• the power ⁇ number of heat pump system 1 Through the multi-stage evaporation to below ⁇ different union pressure and temperature levels is the power ⁇ number of heat pump system 1, despite the use of various ⁇ tempered heat sources 41, ..., 45, increased.
• At least one of the expansion valve 51, ..., 55 and at least one of the compressors 21, ..., 25 is arranged in each case within a partial mass flow.
• the mass flow of the working fluid after the condenser 4 is divided 102 into the five partial mass flows, wherein a first partial mass flow to the first expansion valve 51, a second partial mass flow to the second expansion valve 52, a third partial mass flow to the third
• Expansion valve 53 a fourth sub-mass flow to the fourth expansion valve 54 and finally a fifth sub-mass flow to the fifth expansion valve 55 is performed.
• the partial mass flows to each one of the evaporators 31 are, ..., 35 and then passed each one of the five compressor 21, ..., 25 ge ⁇ leads.
• the partial mass flows again fauxge ⁇ leads to a common mass flow of the working fluid and passed to the condenser 4, whereby the directed working cycle of the working fluid of the heat pump ⁇ system 1 closes.
• FIG. 1 shows a schematic diagram of a heat pump ⁇ plant 1 with five evaporators 21, ..., 25 and 20, a common compressor Further, the heat pump system 1 for liquefaction of the working fluid 4 and thus for discharging the heat to a heat sink 14 a Condenser 4 on.
• At least part of the thermal energy of the heat sources 41,..., 45 is generated by means of five evaporators 31,..., 35 connected in parallel by the at least partial evaporation of the working fluid within the five evaporators 31,. , 35 transferred to the working fluid.
• one of the evaporators 31,..., 35 is provided for each heat source 41,..., 45.
• a common compressor 20 is used for the compression of the working fluid.
• FIG. 3 shows a particularly preferred embodiment of the present invention, in which a heat pump system 1 ei ⁇ nen common compressor 20 includes, which is designed as a turbo compressor 20.
• the expansion or expansion of the working fluid is in turn carried out by means of a plurality of expansion valves 51, ..., 55.
• the distribution 102 of the mass flow of the working fluid into the partial mass flows takes place as already shown in FIG. 1 and / or FIG. 2 and explains the method ⁇ 4.
• the individual partial mass flows are in each case directed into a compressor stage 201,..., 205 of the multi-stage turbocompressor 20.
• the line of the partial mass flows to the individual compressor stages 201, ..., 205 after the evaporators 31, ..., 35 and after the check valves 61, ..., 65.
• a second partial mass flow, starting from the second evaporator 32, is conducted to the second check valve 62 and then to the second compressor stage 202 of the turbo-compressor 20.
• the individual compressor stages 201,..., 205 of the compressor 20 are arranged on a common motor shaft 10.
• FIG. 4 shows an exemplary pressure-enthalpy diagram of an embodiment of the method according to the invention.
• the ordinate 114 indicates the respective prevailing pressure p of the working fluid within the working cycle of the heat pump system 1.
• the abscissa 116 indicates the specific enthalpy h of the working fluid associated with the pressure p.
• a phase boundary in the pressure-enthalpy diagram is determined by a boiling line 124 and a dew line 126.
• the evaporation ⁇ evaporation of the working fluid takes place in the illustrated idealized manner along isotherms 112, wherein the isotherms 112 between the boiling point curve 124, and the dew line 126 approximately parallel to the abscissa 116th
• the diagram in FIG. 4 shows a plurality of isentropes 110.
• an isothermal liquefaction 230 of the working fluid initially takes place with a release of thermal energy to a heat sink 14. Thereby, a condition 2 of the working fluid enters into a closed ⁇ stood 3 over. The state is a point of the working fluid in the pressure-enthalpy diagram.
• the liquefaction 230 takes place at a Ver ⁇ liquid temperature of 130 ° C.
• a reduction 340 of the pressure for example by means of an expansion or expansion of the working fluid.
• the state 3 is in this case in a plurality of states 4.
• the expansion or expansion 340 of the working fluid can, as already explained with reference to FIGS. 1 to 3, take place in parallel.
• the evaporation of the working fluid takes place in parallel evaporation steps 411,..., 415 by means of a plurality of evaporators 31,..., 35 connected in parallel.
• the evaporation steps 411,..., 415 take place approximately or ideally isothermally.
• the states 4 of the working fluid consequently pass via the evaporations 411,..., 415 into a plurality of states 1.
• more than the five illustrated evaporation steps 411,..., 415 may be provided.
• a compression 120 that is, a He ⁇ increase the pressure of the working fluid, which returns the states 1 of the working fluid to state 2.
• the directed working cycle 100 of the working fluid is closed.
• the compression 120 of the working fluid can again take place by means of parallel compressors 21,..., 25 or by means of a common compressor 20.
• all working fluids known from the prior art can be used as working fluids of the heat pump system.
• working fluids containing at least one of the substances 1, 1, 1, 2, 2, 4, 5, 5, 5-nonafluoro-4- (trifluoromethyl) -3-pentanones (trade name Novec TM 649), perfluoromethylbutanone , l-chloro-3,3,3-trifluoro-1-propene, cis
• a method for a heat pump system in which a heat pump process Rankine ⁇ it is enables by a parallel connection of at least two evaporators, which allows for efficient heat receiving different tempered by a plurality of heat sources by means of a temperature glide.
• This makes it possible to use a plurality of different heat sources, in particular a plurality of different waste heat sources, as efficiently as possible.
• the Wär the ⁇ meuzen extracted thermal energy by the heat pump system can be at least partially be prepared for further use by the heat pump system be ⁇ .
• a power plant according to the invention comprises a heat pump system according to the invention.
• the thermal energy of a plurality of different waste heat sources of Kraftkraft- kes at least partially recovered and provided ⁇ the.
• the efficiency of the power plant, in particular a combined cycle power plant improved.

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• Engineering & Computer Science (AREA)
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• Mechanical Engineering (AREA)
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• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Engine Equipment That Uses Special Cycles (AREA)
• Heat-Pump Type And Storage Water Heaters (AREA)

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• 2017
  • 2017-02-13 DE DE102017202227.2A patent/DE102017202227A1/de not_active Withdrawn
• 2018
  • 2018-01-22 WO PCT/EP2018/051417 patent/WO2018145884A1/de active Search and Examination
  • 2018-01-22 CN CN201880011413.6A patent/CN110291347A/zh active Pending
  • 2018-01-22 EP EP18705319.4A patent/EP3563098A1/de not_active Withdrawn
  • 2018-01-22 JP JP2019543329A patent/JP2020507733A/ja active Pending
  • 2018-01-22 KR KR1020197021617A patent/KR20190105019A/ko not_active Application Discontinuation

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