CN102414522B - Transcritical thermally activated cooling, heating and refrigerating system - Google Patents
Transcritical thermally activated cooling, heating and refrigerating system Download PDFInfo
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- CN102414522B CN102414522B CN201080018924.4A CN201080018924A CN102414522B CN 102414522 B CN102414522 B CN 102414522B CN 201080018924 A CN201080018924 A CN 201080018924A CN 102414522 B CN102414522 B CN 102414522B
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- heat exchanger
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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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
- F01K17/02—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
- F01K17/04—Using steam or condensate extracted or exhausted from steam engine plant for specific purposes other than heating
-
- 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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
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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
- 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
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
A combined vapor compression and vapor expansion system uses a common refrigerant which enables a supercritical high pressure portion and a sub-critical low pressure portion of the vapor expansion circuit. Provision is made to combine the refrigerant flow from the vapor expander and from the compressor discharge. The outdoor heat exchanger is so sized and designed that the working fluid discharged therefrom is always in a liquid form so as to provide a liquid into the pump inlet. The pump and expander are so sized and designed that the high pressure portion of the vapor expansion circuit is always super-critical. A topping heat exchanger, liquid to suction heat exchanger, and various other design features are provided to further increase the thermodynamic efficiency of the system.
Description
The cross reference of related application
The disclosure relates to the U. S. application 07/18958 of pending trial, and it transfers assignee of the present disclosure.
With reference to submit on April 29th, 2009, name is called the U.S. Provisional Application 61/173776 of " TRANSCRITICAL THERMALLY ACTIVATED COOLING; HEATING AND REFRIGERATING SYSTEM ", the application requires priority and the rights and interests of this U.S. Provisional Application, and the full content of this U.S. Provisional Application is incorporated herein by reference.
Technical field
Disclosure relate generally to vapor compression system, and relate more specifically to the steam compressed and steam expanded system of combination.
Background technology
It is known that vapor compression system and steam expanded (being rankine cycle) system are combined.For example referring to United States Patent (USP) 6962056(, it is transferred to assignee of the present invention) and United States Patent (USP) 5761921.
United States Patent (USP) 5761921 produces power in rankine cycle, and then this power be employed to drive the compressor of vapor-compression cycle, and combined system operates on three stress levels, i.e. ebullator, condenser and evaporator pressure level.Public cold-producing medium R-134 is used in steam compressed and rankine cycle system.This combined system does not allow to use transcritical refrigerant conventionally, because conventionally do not have condenser (and only having gas cooler) across critical system, thereby in the downstream of gas cooler, does not have available liquid refrigerant to pass through Rankine loop for pumping.Expander needs the high pressure that enters, but the temperature of leaving that adds hot fluid that high inlet pressure makes boiling temperature and carries thermal power raises.The temperature of leaving raising reduces the degree that used heat utilizes.For those reasons, described system is not utilized available heat energy fully, thereby has low-level thermodynamic efficiency.In addition, they cannot provide enough performances in available heat sources during lower than 180 ℉.
U.S. Patent application 07/18958 provides respectively the mix flow from the cold-producing medium of two systems at the outlet place of compressor and expander.In addition, provide suction accumulator, liquid refrigerant always can be used for the pump of rankine cycle system, made to carry out across critical operation.Yet the use of this suction accumulator may be less desirable, because need larger pump, and need higher power.Pump power is determined by the product of the specific volume of the pressure differential at pump two ends and the cold-producing medium at pump intake place stream.Although the liquid in suction accumulator has low specific volume, pump still may be in the poor lower work of high pressure.When pressure differential increases the shortcoming bring and surpassed the advantage that flowing fluid ratio volume reduces to bring, being used for the liquid refrigerant of self cooling condenser comes the supply pump to be considered to more favourable than using suction accumulator.
Summary of the invention
Briefly, according to an aspect of the present disclosure, a kind of steam pressure of combination and steam expanded system are used public cold-producing medium, it enables supercritical, high pressure part and the subcritical low-pressure section in steam expanded loop, and in the porch of outdoor heat exchanger, combines from expander floss hole with from the cold-producing medium of compressor discharge.The size of outdoor heat exchanger is configured to and is designed such that from the cold-producing medium of its discharge always in liquid form, thereby it can flow directly to the pump in steam expanded loop.The size of pump and expander is configured to and is designed such that the high-pressure section in steam expanded loop is always postcritical.
According to another aspect of the present disclosure, outdoor heat exchanger comprises cooling tower, to guarantee that cold-producing medium is converted into liquid in heat exchanger.
According to another aspect of the present disclosure, between outdoor heat exchanger and pump, provide liquid to aspirating heat exchanger, to improved cold-peace refrigerant density before refrigerant liquid direction of flow pump.
According to another aspect of the present disclosure, in the downstream of expander outlet, provide heat exchange of top part device, so that the enthalpy of this hot-fluid of regenerating.
According to another aspect of the present disclosure, power generation steam expanded loop is used as independently system and produces electric energy, and it can be used as power supply for different objects, comprises driving refrigeration system.
Accompanying drawing explanation
With reference to of the present invention, following describe in detail and read by reference to the accompanying drawings, to further understand these and object of the present invention, in accompanying drawing:
Fig. 1 is only for schematic diagram cooling or hot activation refrigerant system that heat.
Fig. 2 is only for the schematic diagram of warm entropy (T-S) figure of the process of the hot activation refrigerant system of cooling or heating.
Fig. 3 A-3C is some schematic diagrames, respectively the slippage (glide) in more overcritical and subcritical applications.
Fig. 4 is the schematic diagram with the hot activation steam expanded system of multiple expansion.
Fig. 5 is the schematic diagram of warm entropy (T-S) figure of process with the hot activation steam expanded system of multiple expansion.
Fig. 6 is to provide the schematic diagram of the hot activation refrigerant system of air-conditioning and refrigeration.
Fig. 7 is the schematic diagram with the hot activation heat pump of two expansion gears.
Fig. 8 is the schematic diagram with the hot activation heat pump of a two-way expansion gear.
Fig. 9 A and Fig. 9 B are respectively the schematic diagrames that reversal valve and check-valves are arranged.
Figure 10 is the schematic diagram with the hot activation heat pump of two different heat sources.
Figure 11 is the schematic diagram with the hot activation heat pump of multi-stage compression.
Figure 12 has steam to the schematic diagram of the hot activation heat pump of steam displacer.
Figure 13 is the schematic diagram with the hot activation heat pump of two-phase displacer.
Figure 14 is the schematic diagram with the hot activation heat pump of the circulation of saving.
Figure 15 is the schematic diagram with the hot activation heat pump of two-phase expander.
The specific embodiment
Although specifically illustrate and described the disclosure with reference to the preference pattern shown in accompanying drawing, those skilled in the art will be appreciated that, in the situation that do not depart from the disclosure spirit and scope that are defined by the claims, can in the disclosure, realize the various variations in details.
According to Fig. 1, hot activation refrigerant system comprises and shows as the vapor compression circuit 21 of solid line and show the steam expanded loop 22 as dotted line.Vapor compression circuit 21 comprises that compressor 23, condenser 24, liquid are to aspirating heat exchanger 26, expansion gear 27 and evaporimeter 28.Steam expanded loop 22 is by pump 29, heat exchange of top part device 31, heater 32, expander 33 and condenser 24.Refrigerant vapour stream and the vaporous cryogen stream in the exit from expander in the exit from compressor are connected at condenser inlet place, to provide mix flow to pass through condenser 24.As shown in the figure, condensator outlet place or liquid to the refrigerant liquid flow point that aspirates the exit of heat exchanger 26 be cleaved into two streams: one is supplied to pump, and another cycles through the parts of vapor compression circuit.
Hot activation refrigerant system has three stress levels: heated pressure, heat extraction stress level and evaporating pressure.Heated pressure is pump blowdown presssure, and heat extraction pressure is compressor or expander discharge, and evaporating pressure is compressor suction pressure.Heating and heat extraction pressure are high pressure and the low-pressure in steam expanded loop.Heat extraction and evaporating pressure are high pressure and the low-pressures of vapor compression circuit.
A kind of public working fluid is used to steam compressed and steam expanded loop.This working fluid has following characteristics: its high-pressure section for steam expanded loop provides supercritical operation, and provides subcritical operation for the low-pressure section in steam expanded loop.Therefore, the working fluid in the steam expanded loop under high pressure remains gaseous state, but the working fluid in condenser appears in the region in vapor dome left side and is liquefied.The example of this working fluid is CO
2or based on CO
2mixture, CO for example
2and propane, etc.
Operating period under high ambient temperature more, condenser 24 can be supplied with by cooling tower 34, to guarantee the condensation of refrigerant vapour.Another kind of optional mode is to use CO
2with propane etc., to the critical point of fluid is raise fully higher than the level of environment temperature, so that can realize condensation process under heat extraction pressure.
Heated pressure in heater 32 is recently controlled by expander to the capacity of pump, and this Capacity Ratio is determined by expander to the vaporous cryogen state of the rotating ratio of pump, the liquid refrigerant temperature at pump intake place and expander porch.
Liquid is optional to aspirating heat exchanger 26.It is overheated substantially that it makes slightly to cross steam flow cold and that make to flow out from evaporimeter 28 from condenser 24 liquid stream out.Cross the cold pump power that reduced, this is the refrigerant density reduction due to pump intake place.And it has increased the enthalpy difference on evaporimeter 28 and has strengthened evaporimeter effect.Overheatedly reduced the refrigerant density at place, suction port of compressor and reduced compressor mass flowrate and evaporator capacity.Overheating effect is conventionally stronger, thereby total effect is normally disadvantageous.Therefore, liquid only needs at suction port of compressor place necessarily to use when overheated to aspirating heat exchanger 26.
When heat source temperature is high, heat exchange of top part device 31 has improved the thermodynamic efficiency of system substantially.When heat source temperature is low, do not need heat exchange of top part device.
The power producing in expander 33 can drive compression machine 23 and pump 29.All three machines can be placed on same axle.Optional mode is this axle to be connected not only to provide cooling or heating efficiency with power generator 36, and electric energy is provided.Expander 33 can only connect with power generator, and in this case, power generator 36 provides power for compressor 23 and pump 29.In addition, optionally, it can produce supplementary electric energy.
Steam expanded loop can be implemented as separated power generation system.The power producing in power generation system can be used to provide power for heat pump, air-conditioner, refrigerator or any other electric device.
The all parts that are positioned on same axle can be covered by half airtight or airtight housing, to reduce the risk of leakage.
Referring now to Fig. 2,, show the vapor compression circuit 21 of Fig. 1 and the T-S in steam expanded loop 22 figure, in two width figure, interested each point represents with digital 1-12.As will be seen, the temperature that line 9-10 representative occurs when working fluid process heater 32 increases and enthalpy increases.And, should recognize, alternately chain-dotted line 37 represents the T-S figure that adds hot fluid being cooled through heater 32.Like this, desired is not only serviceability temperature at 180 ℉ or higher heat source fluid (as used), and make it possible to serviceability temperature lower than the heat source fluid of this level in conventional system.This passes through from using CO
2" slippage " of the line 37 obtaining as working fluid or slope and become possibility.This will be by being more clearly understood with reference to Fig. 3 A-3C.
Steam expanded loop has been shown in Fig. 3 A, and its relation with serial flow comprises pump 38, heat exchange of top part device 39, heater 41, expander 42 and condenser 43.
Fig. 3 B shows Fig. 3 A loop when operating in overcritical pattern (for example, with CO
2for cold-producing medium) time T-S figure.Digital 1-8 in Fig. 3 B is corresponding to the position 1-8 in the figure of Fig. 3 A.As will be seen, CO is worked as in the representative of the line 3-4 in Fig. 3 B
2temperature during through heater 41 increases and enthalpy increases, and alternately chain-dotted line 44 represents the T-S figure that adds hot fluid being cooled.Will appreciate that, " slippage " of this line or slope are very considerable.
On the contrary, Fig. 3 C illustrates Fig. 3 A loop and (for example uses and be different from CO when operating in sub-critical mode
2cold-producing medium) time T-S figure.Here, will recognize, the slippage/slope of line 46 is significantly less than the slippage/slope of the line 44 in Fig. 3 B.Article two, the used heat that line 44 and 46 vertical component (as shown in arrow line 47 and 48) show respectively two kinds of alternative of Fig. 3 B and Fig. 3 C utilizes degree.As will be seen, line 47 obtains farther to downward-extension than line 48, this so that represent that the thermal source (state 7) under lower temperature may be utilized, as long as the temperature in state 8 is lower than the temperature in state 7.Therefore,, lower than the temperature of 180 ℉, for example the temperature of 150 ℉, may be suitable.
Referring now to Fig. 4,, show another embodiment, wherein, be different from the single-stage expansion device 33 shown in Fig. 1, double expansion device 49 and secondary heater 51 are provided.Secondary heater 51 receives and adds hot fluid along circuit 52, and by circuit 53, is back to the point of heater 32.The temperature that adds hot fluid in heater 51 should equal the temperature of the attached point of circuit 53 in heater 32.In operation, cold-producing medium flows to the first order of double expansion device 49 from heater 32, then pass through secondary heater 51, the second level of its process double expansion device 49 after this, and then flow to heat exchange of top part device 31.Other parts in loop as described above.The T-S of Fig. 5 illustrates the effect of using double expansion device 49 and secondary heater 51, in Fig. 5, and the position of indication in numeral (1-14) presentation graphs 4.Known, there is the method for the multiple expansion of heating again and improved expander efficiency, and reduced needed pump power, thus the use that makes it possible to use less pump and reduce pump power, thus the overall efficiency of improvement system.
Fig. 6 shows another embodiment, wherein, provides concurrently the second vapor compression circuit 54 with vapor compression circuit 21.This makes system that air-conditioning (for example, by the second vapor compression circuit 54) and refrigeration (for example, by vapor compression circuit 21) can be provided.
The second vapor compression circuit 54 comprises the second expansion gear 56, the second evaporimeter or indoor unit 57 and the second compressor 58.For the cold-producing medium stream in this loop, be derived from the upstream of expansion gear 27, and from the discharge stream of the second compressor 58 and cold-producing medium stream combination from heat exchange of top part device 31, then said composition is combined with the stream of floss hole from compressor 23.Therefore, each vapor compression circuit 21 and 54 has compressor and the evaporator unit of himself, and all other parts are shared between two loops.As will be seen, two compressors provide power by expander 33.
If condenser 24 is that outdoor unit and evaporimeter 28 are indoor units, hot activation refrigerant system produces cooling.If condenser is indoor unit and evaporimeter is outdoor unit, hot activation refrigerant system produces heating.In order to switch, can as shown in Fig. 7-15, provide one or more reversal valves or check-valves between two kinds of operator schemes.
For permission system is operable to heat pump, a pair of reversal valve 59 and 61 are provided as shown in Figure 7.Further, except can being operable to the expansion gear 27 for refrigerating mode, also provide the second expansion gear 62 for heating mode.Each expansion gear 27 and 62 comprises respectively by-passing valve, i.e. valve 63 and 64 operates respectively allowing in cooling and heating mode.Expansion gear 27 and 62 is unidirectional expansion devices.In order to switch between cooling and heating mode, reversal valve 59 and 61 and by-passing valve 63 and 64 be all simultaneously operated.
Can provide suction accumulator 66, to meet cooling and refrigerant charge requirement heating operation.And suction accumulator 66 provides filling management and volume controlled, the amount of redundancy of savings liquid refrigerant.
In addition, can provide as indicated liquid to aspirating heat exchanger 67.
The variant of Fig. 7 system is shown in Figure 8, and wherein, two expansion gears are replaced by single expansion device 68, and this single expansion device 68 is designed to two-way use.Therefore,, when switching between cooling and heating mode, single expansion device and reversal valve 59 and 61 are all switched simultaneously.
In Fig. 9 A, show the position separately that the reversal valve of cooling or heating operation 59 is provided.Therefore,, when cooling, cold-producing medium through heat exchanger 67, expansion gear 27, then flows to indoor unit from reversal valve 59.When heating, cold-producing medium through heat exchanger 67, expansion gear 27, then flows to outdoor unit from reversal valve 59.
As seen in Fig. 9 B, be different from and use reversal valve mentioned above, can replace with check-valves and realize same function.Therefore, be different from reversal valve, four check- valves 71,72,73 and 74 are provided.In refrigerating mode, cold-producing medium process check-valves 71, heat exchanger 67, expansion gear 27 and check-valves 73, thus come indoor unit, check- valves 72 and 74 cuts out.In the operation of heating mode, check- valves 71 and 73 cuts out, and cold-producing medium is through check-valves 74, heat exchanger 67, expansion gear 27 and check-valves 72, then flows to outdoor unit.
The situation of Figure 10 representative when two thermals source (high temperature and cold temperature source) are available.Secondary heater 74 adopts high temperature source.Heater 32 adopts cold temperature source.
Figure 11 shows further embodiment, wherein, provides compound compressor 76.After the first order, cold-producing medium, through gas cooler 77, then passes through the second level of two-stage compressor 76, then flows to reversal valve 61 and condenser 24.Like this, reduce total compressor horsepower, improved thus the thermodynamic efficiency of compression circuit, and therefore improved the thermodynamic efficiency of overall system.
The embodiment of Figure 12 provides displacer 78, for advancing refrigerant vapour to flow to suction accumulator 66, has improved thus the thermodynamic efficiency of vapor compression circuit, and has therefore improved the thermodynamic efficiency of overall system.Displacer 78 is by along circuit 79 or drive from the high-pressure spray of circuit 81 or 82 alternatively.In this specific embodiment, liquid is critical pieces to aspirating heat exchanger 67.Heat exchanger 67 makes partly to complete evaporation from the liquid of displacer 78 cold-producing medium stream out.
The embodiment of Figure 13 shows the heat pump with displacer 83, and displacer 83 is by from circuit 84 or drive from the high-pressure refrigerant of circuit 86 alternatively.Two-way expansion gear 87 can be substituted by two unidirectional expansion devices, and one for indoor unit and another is for outdoor unit, as shown in Fig. 7 above.
Known, displacer has improved the Performance Characteristics of vapor-compression cycle.Steam compressed and the steam expanded of combination circulates in the situation of better vapor-compression cycle and is improved.
Figure 14 shows alternate embodiment, and it comprises economizer cycle, and this economizer cycle comprises the economizer port 91 of saving heat exchanger 88, economizer expansion device 89 and leading to the intergrade of compressor 23.Further alternative can be to have the cooling compound compressor of intermediate vapor.Known, save the Performance Characteristics that circulation has improved vapor-compression cycle.Steam compressed and the steam expanded of combination circulates in the situation of better vapor-compression cycle and is improved.
The embodiment of Figure 15 provides two-phase expander 92, and it is fluidly interconnected between the entrance and reversal valve 59 of pump 29, as shown in the figure.Its use trends towards increasing cooling effect, and recovers other power to drive this circulation simultaneously.This so reduced required pump size and pump power.
Although specifically illustrate and described the disclosure with reference to the preferred embodiment shown in accompanying drawing, those skilled in the art will be appreciated that, in the situation that do not depart from the disclosure spirit and scope that are defined by the claims, can realize the various variations in details to the disclosure.
Claims (32)
1. a hot activation cooling system, comprising:
Vapor compression circuit, it comprises compressor, First Heat Exchanger, expansion gear and the second heat exchanger with serial flow relation;
Steam expanded loop, it comprises liquid refrigerant pump, heater, expander and described First Heat Exchanger with serial flow relation;
Described vapor compression circuit and described steam expanded loop have separately public cold-producing medium and therefrom cycle through as working fluid, wherein, described cold-producing medium provides supercritical operation for the high-pressure section in described steam expanded loop, and provides subcritical operation for the low-pressure section in described steam expanded loop;
Described compressor has suction entrance and exhaust outlet, and described expander has entrance and exit, and further wherein, described expander outlet fluid is connected to described exhaust outlet so that mix flow to be provided, for making a part for described working fluid cycle through described First Heat Exchanger and flow to described liquid refrigerant pump, wherein, the size of described First Heat Exchanger is configured to and is designed such that from the working fluid of its discharge always in liquid form; And
The size of described liquid refrigerant pump and described expander is configured to and is designed such that the high-pressure section in described steam expanded loop is always postcritical.
2. hot activation cooling system as claimed in claim 1, wherein, described public cold-producing medium is CO
2.
3. hot activation cooling system as claimed in claim 1, wherein, described public cold-producing medium is CO
2mixture with propane.
4. hot activation cooling system as claimed in claim 1, and comprise heat exchange of top part device, for causing heat to flow to the stream of heater from expander discharge stream.
5. hot activation cooling system as claimed in claim 1, and comprise that liquid is to aspirating heat exchanger, for causing heat to flow to described the second heat exchanger discharge stream from described First Heat Exchanger discharge stream.
6. hot activation cooling system as claimed in claim 1, wherein, described expander is double expansion device, and further wherein, secondary heater is arranged between the two-stage of described double expansion device.
7. hot activation cooling system as claimed in claim 1, and comprise second vapor compression circuit parallel with described vapor compression circuit, described the second vapor compression circuit has expansion gear, evaporimeter and the compressor of the fluid interconnection of himself, to play a role together with described First Heat Exchanger.
8. hot activation cooling system as claimed in claim 1, and comprise a plurality of valves, for optionally causing described vapor compression circuit to be used as heat pump.
9. hot activation cooling system as claimed in claim 8, wherein, described a plurality of valves comprise two expansion gears, one for described First Heat Exchanger, and another is for described the second heat exchanger.
10. hot activation cooling system as claimed in claim 8, wherein, described a plurality of valves comprise single two-way expansion gear, it optionally operates cold-producing medium stream to be transmitted to the described first or second heat exchanger.
11. hot activation cooling systems as claimed in claim 8, wherein, described a plurality of valves comprise a plurality of check-valves, it optionally operates cold-producing medium stream to be transmitted to the described first or second heat exchanger.
12. hot activation cooling systems as claimed in claim 1, and comprise secondary heater, it is connected with serial flow relation with described heater.
13. hot activation cooling systems as claimed in claim 1, wherein, described compressor comprises compound compressor, and further comprises the gas cooler being operatively coupled between described compound compressor multistage.
14. hot activation cooling systems as claimed in claim 1, wherein, described vapor compression circuit comprises displacer, for advancing described cold-producing medium to flow to described compressor.
15. hot activation cooling systems as claimed in claim 14, and comprise that liquid is to aspirating heat exchanger, for causing heat to flow to described the second heat exchanger discharge stream from described First Heat Exchanger discharge stream,
Wherein, cold-producing medium stream for cooling performance is split into two parts, the part that described displacer is flowed by described cold-producing medium provides power and discharges another part of described cold-producing medium stream, another part of described cold-producing medium stream described the second heat exchanger and then at described liquid to processed in aspirating heat exchanger.
16. hot activation cooling systems as claimed in claim 14, wherein, described vapor compression circuit comprises suction accumulator, for the cold-producing medium stream of cooling performance, provide power for described displacer, discharge the liquid part of described cold-producing medium stream, it is collected in described suction accumulator and is processed in described the second heat exchanger.
17. hot activation cooling systems as claimed in claim 1, wherein, described vapor compression circuit comprises the saver being operably connected with it.
18. hot activation cooling systems as claimed in claim 1, and comprise two-phase expander, it is fluidly interconnected between described First Heat Exchanger and described the second heat exchanger.
19. hot activation cooling systems as claimed in claim 1, wherein, described expander, described liquid refrigerant pump and described compressor have public axle.
20. hot activation cooling systems as claimed in claim 1, wherein, power generator and described expander have public axle, and described power generator provides power for described liquid refrigerant pump and described compressor.
21. hot activation cooling systems as claimed in claim 1, wherein, power generator, described expander and described liquid refrigerant pump have public axle, and described power generator provides power for described compressor.
22. hot activation cooling systems as claimed in claim 1, wherein, power generator, described expander and described compressor have public axle, and described power generator is supplied with described liquid refrigerant pump.
23. hot activation cooling systems as claimed in claim 18, wherein, described expander, described liquid refrigerant pump and described compressor have public airtight housing.
24. 1 kinds of power generation steam expanded loops, it comprises power generator and liquid refrigerant pump, heater, expander and heat exchanger in serial flow relation;
Cold-producing medium therefrom cycles through as working fluid, and wherein, described cold-producing medium provides supercritical operation for the high-pressure section in described steam expanded loop, and provides subcritical operation for the low-pressure section in described steam expanded loop;
The size of described heat exchanger is configured to and is designed such that from the working fluid of its discharge always in liquid form; And
The size of described liquid refrigerant pump and described expander is configured to and is designed such that the high-pressure section in described steam expanded loop is always postcritical.
25. power generation steam expanded as claimed in claim 24 loops, wherein, described cold-producing medium is CO
2.
26. power generation steam expanded as claimed in claim 24 loops, wherein, described cold-producing medium is CO
2mixture with propane.
27. power generation steam expanded as claimed in claim 24 loops, and comprise heat exchange of top part device, for causing heat to flow to the stream of heater from expander discharge stream.
28. power generation steam expanded as claimed in claim 24 loops, wherein, described expander is double expansion device, and further wherein, secondary heater is arranged between the two-stage of described double expansion device.
29. power generation steam expanded as claimed in claim 24 loops, and comprise secondary heater, it is connected with serial flow relation with described heater.
30. power generation steam expanded as claimed in claim 24 loops, wherein, described power generator, described expander and described liquid refrigerant pump have public axle.
31. power generation steam expanded as claimed in claim 24 loops, wherein, described power generator, described expander and described liquid refrigerant pump have public airtight housing.
32. power generation steam expanded as claimed in claim 24 loops, wherein, described power generator provides power for refrigeration system.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US17377609P | 2009-04-29 | 2009-04-29 | |
| US61/173776 | 2009-04-29 | ||
| PCT/US2010/032726 WO2010126980A2 (en) | 2009-04-29 | 2010-04-28 | Transcritical thermally activated cooling, heating and refrigerating system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102414522A CN102414522A (en) | 2012-04-11 |
| CN102414522B true CN102414522B (en) | 2014-03-05 |
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| CN201080018924.4A Expired - Fee Related CN102414522B (en) | 2009-04-29 | 2010-04-28 | Transcritical thermally activated cooling, heating and refrigerating system |
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|---|---|
| US (1) | US20120036854A1 (en) |
| EP (1) | EP2425189A2 (en) |
| CN (1) | CN102414522B (en) |
| WO (1) | WO2010126980A2 (en) |
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Also Published As
| Publication number | Publication date |
|---|---|
| WO2010126980A3 (en) | 2011-03-03 |
| CN102414522A (en) | 2012-04-11 |
| WO2010126980A2 (en) | 2010-11-04 |
| US20120036854A1 (en) | 2012-02-16 |
| EP2425189A2 (en) | 2012-03-07 |
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