CN102414522A - Transcritical thermally activated cooling, heating and refrigerating system - Google Patents
Transcritical thermally activated cooling, heating and refrigerating system Download PDFInfo
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- CN102414522A CN102414522A CN2010800189244A CN201080018924A CN102414522A CN 102414522 A CN102414522 A CN 102414522A CN 2010800189244 A CN2010800189244 A CN 2010800189244A CN 201080018924 A CN201080018924 A CN 201080018924A CN 102414522 A CN102414522 A CN 102414522A
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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
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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
- 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
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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
- 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 submitted 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 this U.S. Provisional Application No. and rights and interests, 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 the steam compressed and steam expanded system that relates more specifically to make up.
Background technology
It is known that vapor compression system and steam expanded (being rankine cycle) system are made up.For example referring to United States Patent (USP) 6962056 (it is transferred assignee of the present invention) and United States Patent (USP) 5761921.
United States Patent (USP) 5761921 produces power in rankine cycle, this power is employed driving the compressor of vapor-compression cycle then, 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 the rankine cycle system.This combined system does not allow to use transcritical refrigerant usually, does not have condenser (and only having gas cooler) usually because stride critical system, thereby does not have available liquid refrigerant to be used for pumping through the Rankine loop in the downstream of gas cooler.Expander needs high entering pressure, but high inlet pressure makes boiling temperature and the temperature of leaving that adds hot fluid of carrying thermal power raise.The temperature of leaving that raises makes the degree of used heat utilization reduce.For those reasons, said system does not utilize available heat energy fully, thereby has low-level thermodynamic efficiency.In addition, they can't provide enough performances when available heat sources is 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, the suction accumulator is provided, has made liquid refrigerant always can use, made and to stride critical operation for the pump of rankine cycle system.Yet the use of this suction accumulator possibly not expected, because need bigger pump, and needs higher power.Pump power is confirmed by the product of the specific volume of the cold-producing medium stream at the pressure differential at pump two ends and pump intake place.Although the liquid in the suction accumulator has low specific volume, pump still possibly worked under high pressure differential.When pressure differential increased the shortcoming bring and surpassed the advantage that the flowing fluid ratio volume reduces to bring, being used for the liquid refrigerant of self cooling condenser, to come the supply pump to be considered to than to use the suction accumulator more favourable.
Summary of the invention
Briefly; According to an aspect of the present disclosure; A kind of steam pressure of combination and steam expanded system use public cold-producing medium; It enables the supercritical, high pressure part and subcritical low-pressure section in steam expanded loop, and makes up in the porch of outdoor heat exchanger from the 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 discharging always be 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, in heat exchanger, is converted into liquid to guarantee cold-producing medium.
According to another aspect of the present disclosure, between outdoor heat exchanger and pump, provide liquid to aspirating heat exchanger, so that before refrigerant liquid direction of flow pump, improved the cold-peace refrigerant density.
According to another aspect of the present disclosure, in the downstream of expander outlet the heat exchange of top part device is provided, 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 to be used for various objectives, comprises the driving refrigeration system.
Description of drawings
Will be with reference to describing in detail below of the present invention and combine accompanying drawing to read, so that further understand these and purpose of the present invention, in the accompanying drawing:
Fig. 1 only is used to cool off or the sketch map of the hot activation refrigerant system that heats.
Fig. 2 only is used to cool off or the sketch map of warm entropy (T-S) figure of the process of the hot activation refrigerant system that heats.
Fig. 3 A-3C is some sketch mapes, the slippage (glide) in more overcritical respectively and the subcritical applications.
Fig. 4 is the sketch map with hot activation steam expanded system of multiple expansion.
Fig. 5 is the sketch map of warm entropy (T-S) figure of process with hot activation steam expanded system of multiple expansion.
Fig. 6 provides the sketch map of the hot activation refrigerant system of air-conditioning and refrigeration.
Fig. 7 is the sketch map with hot activation heat pump of two expansion gears.
Fig. 8 is the sketch map with hot activation heat pump of a two-way expansion gear.
Fig. 9 A and Fig. 9 B are respectively the sketch mapes that reversal valve and check-valves are arranged.
Figure 10 is the sketch map with hot activation heat pump of two different heat sources.
Figure 11 is the sketch map with hot activation heat pump of multi-stage compression.
Figure 12 is the sketch map with hot activation heat pump of steam to steam displacer.
Figure 13 is the sketch map with hot activation heat pump of two phase displacers.
Figure 14 is the sketch map with hot activation heat pump of economized cycle.
Figure 15 is the sketch map with hot activation heat pump of two phase expanders.
The specific embodiment
Though specifically illustrate and described the disclosure with reference to the preference pattern shown in the accompanying drawing; Those skilled in the art will be appreciated that; Under the situation that does not depart from the disclosure spirit that is defined by the claims and scope, can in the disclosure, realize the various variations on the details.
According to Fig. 1, the hot activation refrigerant system comprise show as the vapor compression circuit of solid line 21 with show 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.Being connected at the condenser inlet place,, mix flow passes through condenser 24 so that being provided from the refrigerant vapour stream in the exit of compressor and at vaporous cryogen stream from the exit of expander.As shown in the figure, the perhaps refrigerant liquid flow point in liquid to the exit of aspirating heat exchanger 26 at condensator outlet place is cleaved into two streams: one supplies to pump, and another cycles through the parts of vapor compression circuit.
The hot activation refrigerant system has three stress levels: heated pressure, heat extraction stress level and evaporating pressure.Heated pressure is the pump blowdown presssure, and heat extraction pressure is compressor or expander discharging, and evaporating pressure is a compressor suction pressure.Heating and heat extraction pressure are the high pressure and the low-pressure in steam expanded loop.Heat extraction and evaporating pressure are the high pressure and the low-pressures of vapor compression circuit.
A kind of public working fluid is used to steam compressed and the steam expanded loop.This working fluid has following characteristic: it provides supercritical operation for the high-pressure section in steam expanded loop, and subcritical operation is provided for the low-pressure section in steam expanded loop.Therefore, the working fluid in the steam expanded loop under the high pressure remains gaseous state, but the working fluid in the condenser appears in the zone 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, or the like.
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., so that raise the critical point of fluid to such an extent that fully be higher than the level of environment temperature, so that can under heat extraction pressure, realize condensation process.
Heated pressure in the heater 32 is recently controlled by the capacity of expander to pump, and this Capacity Ratio is confirmed by the rotating ratio of expander to pump, the liquid refrigerant temperature at pump intake place and the vaporous cryogen state of expander porch.
Liquid is chosen wantonly to aspirating heat exchanger 26.It is overheated substantially that its feasible flow of liquid of coming out from condenser 24 is crossed cold and feasible steam flow from evaporimeter 28 outflows slightly.Cross the cold pump power that reduced, this is because the refrigerant density at pump intake place reduces.And it has increased the enthalpy difference on the evaporimeter 28 and has strengthened the evaporimeter effect.Overheatedly reduced the refrigerant density at place, suction port of compressor and reduced compressor mass flowrate and evaporator capacity.Overheating effect is stronger usually, thereby total effect is normally disadvantageous.Therefore, liquid only needs at the place, suction port of compressor necessarily to use when overheated to aspirating heat exchanger 26.
When heat source temperature was high, heat exchange of top part device 31 had improved the thermodynamic efficiency of system substantially.When heat source temperature is low, do not need the heat exchange of top part device.
But the power Driven Compressor 23 and the pump 29 that produce in the expander 33.All three machines can be placed on the same axle.Optional mode is this axle to be connected with power generator 36 not only to provide cool off or the heating efficiency, and electric energy is provided.Expander 33 can only connect with power generator, and in this situation, power generator 36 provides power for compressor 23 and pump 29.In addition, randomly, it can produce additional electric energy.
The steam expanded loop can be implemented as the power generation systems of separation.The power that produces in the power generation systems can be used for heat pump, air-conditioner, refrigerator or any other electric device power is provided.
All parts that are positioned on the same axle can be covered by half airtight or airtight housing, to reduce the risk of leaking.
Referring now to Fig. 2,, show the vapor compression circuit 21 of Fig. 1 and the T-S figure in steam expanded loop 22, in two width of cloth figure, interested each point is represented with digital 1-12.As will see, the temperature that line 9-10 representative takes place when working fluid process heater 32 increases and enthalpy increases.And, should recognize that alternately chain-dotted line 37 expressions are through the T-S figure that adds hot fluid that is cooled of heater 32.Like this, desired is not only serviceability temperature and make it possible to the heat source fluid that serviceability temperature is lower than this level at 180 ℉ or higher heat source fluid (as using in the conventional system).This passes through from using CO
2" slippage " of the line 37 that obtains as working fluid or slope and become possibility.This will be through more being expressly understood with reference to Fig. 3 A-3C.
The steam expanded loop has been shown among 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
2Be cold-producing medium) time T-S figure.Digital 1-8 among Fig. 3 B is corresponding to the position 1-8 among the figure of Fig. 3 A.As will see, CO is worked as in the line 3-4 representative among Fig. 3 B
2Temperature during through heater 41 increases and enthalpy increases, and replaces the T-S figure that adds hot fluid that chain-dotted line 44 expressions are 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 that the slippage/slope of line 46 is significantly less than the slippage/slope of the line among Fig. 3 B 44.Article two, line 44 and 46 vertical component (shown in arrow line 47 and the 48) used heat that shows two kinds of alternative of Fig. 3 B and Fig. 3 C respectively utilizes degree.As will see that to extending below fartherly, this and then expression lower temperature thermal source (state 7) down may be utilized line 47 than line 48, the temperature that needs only in the state 8 is lower than the temperature in the state 7.Therefore, be lower than the temperature of 180 ℉, for example the temperature of 150 ℉ possibly be suitable.
Referring now to Fig. 4,, show another embodiment, wherein, be different from single-stage expansion device 33 shown in Figure 1, double expansion device 49 and secondary heater 51 are provided.Secondary heater 51 receives along circuit 52 and adds hot fluid, and through circuit 53 it is back to the point of heater 32.The temperature that adds hot fluid in the heater 51 should equal in the heater 32 circuit 53 the temperature of attached point.In operation, cold-producing medium flows to the first order of double expansion device 49 from heater 32, passes through secondary heater 51 then, and it and flows to heat exchange of top part device 31 then through the second level of double expansion device 49 after this.Other part in the loop such as top as described in.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, have again the method for the multiple expansion of heating and improved expander efficient, and reduced needed pump power, thus the use that makes it possible to use littler pump and reduce pump power, thus the overall efficiency of improvement system.
Fig. 6 shows another embodiment, wherein, with vapor compression circuit 21 second vapor compression circuit 54 is provided concurrently.This system that makes can provide air-conditioning (for example through second vapor compression circuit 54) and refrigeration (for example through vapor compression circuit 21).
Second vapor compression circuit 54 comprises second expansion gear 56, second evaporimeter or the indoor unit 57 and second compressor 58.The cold-producing medium stream that is used for this loop is derived from the upper reaches of expansion gear 27, and from the discharge stream of second compressor 58 and cold-producing medium stream combination from heat exchange of top part device 31, and said composition is combined with the stream from the floss hole of compressor 23 then.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 see, two compressors provide power by expander 33.
If condenser 24 is that outdoor unit and evaporimeter 28 are indoor units, then the hot activation refrigerant system produces cooling.If condenser is indoor unit and evaporimeter is outdoor unit, then the hot activation refrigerant system produces heating.In order between two kinds of operator schemes, to switch, one or more reversal valves or check-valves can be provided shown in Fig. 7-15.
System is operable to heat pump for permission, a pair of reversal valve 59 and 61 of providing as shown in Figure 7.Further, except can being operable to the expansion gear 27 that is used for refrigerating mode, also provide second expansion gear 62 to be used for heating mode.Each expansion gear 27 and 62 comprises by-passing valve respectively, and promptly valve 63 and 64 is operated in cooling and heating mode respectively with permission.Expansion gear 27 and 62 is unidirectional expansion devices.For the cooling and heating mode between switch, reversal valve 59 and 61 and by-passing valve 63 and 64 all be simultaneously operated.
In addition, can provide liquid to aspirating heat exchanger 67 like indicated.
The variant of Fig. 7 system is shown in Fig. 8, and wherein, two expansion gears are replaced by single expansion gear 68, and this single expansion device 68 is designed to two-way use.Therefore, when between cooling and heating mode, switching, single expansion device and reversal valve 59 and 61 are all switched simultaneously.
In Fig. 9 A, show the position separately of the reversal valve 59 that cooling or heating operation are provided.Therefore, when cooling, cold-producing medium through heat exchanger 67, expansion gear 27, flows to indoor unit from reversal valve 59 then.When heating, cold-producing medium through heat exchanger 67, expansion gear 27, flows to outdoor unit from reversal valve 59 then.
As will in Fig. 9 B, see, be different from and use reversal valve mentioned above, can replace and use check-valves to 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 flows to outdoor unit then through check-valves 74, heat exchanger 67, expansion gear 27 and check-valves 72.
Figure 10 representative is worked as two thermals source (high temperature and cold temperature source) but the situation of time spent.Secondary heater 74 adopts high temperature source.Heater 32 adopts cold temperature source.
Figure 11 shows further embodiment, wherein, compound compressor 76 is provided.After the process first order, cold-producing medium passes through the second level of two-stage compressor 76 then through gas cooler 77, flows to reversal valve 61 and condenser 24 then.Like this, reduce total compressor horsepower, improved the thermodynamic efficiency of compression circuit thus, and therefore improved the thermodynamic efficiency of overall system.
The embodiment of Figure 12 provides displacer 78, is used to advance refrigerant vapour to flow to suction accumulator 66, has improved the thermodynamic efficiency of vapor compression circuit thus, and has therefore improved the thermodynamic efficiency of overall system.Displacer 78 is perhaps driven from the high-pressure spray of circuit 81 or 82 along circuit 79 substitutingly.In this specific embodiment, liquid is critical pieces to aspirating heat exchanger 67.The liquid that the heat exchanger 67 feasible cold-producing mediums that come out from displacer 78 flow is partly accomplished evaporation.
The embodiment of Figure 13 shows the heat pump with displacer 83, and displacer 83 is driven from circuit 84 or substituting high-pressure refrigerant from circuit 86.Two-way expansion gear 87 can be substituted by two unidirectional expansion devices, and promptly one is used for indoor unit and another is used for outdoor unit, as top shown in Figure 7.
Known, displacer has improved the Performance Characteristics of vapor-compression cycle.Steam compressed and the steam expanded of combination circulates under 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 practicing thrift heat exchanger 88, economizer expansion device 89 and leading to the intergrade of compressor 23.Further alternative can be the compound compressor with intermediate vapor cooling.Known, economized cycle has been improved the Performance Characteristics of vapor-compression cycle.Steam compressed and the steam expanded of combination circulates under the situation of better vapor-compression cycle and is improved.
The embodiment of Figure 15 provides two phase expanders 92, is interconnected between the inlet and reversal valve 59 of pump 29 its fluid, and is as shown in the figure.Its use trends towards increasing cooling effect, and recovers other power simultaneously to drive this circulation.This so reduced required pump size and pump power.
Though specifically illustrate and described the disclosure with reference to the preferred embodiment shown in the accompanying drawing; Those skilled in the art will be appreciated that; Under the situation that does not depart from the disclosure spirit that is defined by the claims and scope, can realize the various variations on the details to the disclosure.
Claims (32)
1. hot activation cooling system comprises:
Vapor compression circuit, it comprises compressor, first heat exchanger, expansion gear and second heat exchanger with the serial flow relation;
The steam expanded loop, it comprises liquid refrigerant pump, heater, expander and said first heat exchanger with the serial flow relation;
Said vapor compression circuit and said steam expanded loop have public cold-producing medium separately and therefrom cycle through as working fluid, and wherein, said cold-producing medium enables the supercritical, high pressure part and the subcritical low-pressure section of said vapor compression circuit;
Said compressor has suction inlet and exhaust outlet; And said expander has entrance and exit; And further wherein, said expander outlet fluid is connected to said compressor outlet so that mix flow to be provided, and is used to make the part of said working fluid to cycle through said first heat exchanger and flow to said pump; Wherein, the size of said first heat exchanger is configured to and is designed such that from the working fluid of its discharging always be in liquid form; And
The size of said pump and said expander is configured to and is designed such that the high-pressure section in said steam expanded loop is always postcritical.
2. hot activation cooling system as claimed in claim 1, wherein, said public cold-producing medium is CO
2
3. hot activation cooling system as claimed in claim 1, wherein, said public cold-producing medium is CO
2Mixture with propane.
4. hot activation cooling system as claimed in claim 1, and comprise the heat exchange of top part device, be used to cause heat to flow to the stream of heater from the expander discharge stream.
5. hot activation cooling system as claimed in claim 1, and comprise liquid to aspirating heat exchanger, be used to cause heat to flow to the evaporimeter discharge stream from the condenser discharge stream.
6. hot activation cooling system as claimed in claim 1, wherein, said expander is the double expansion device, and further wherein, secondary heater is set between the two-stage.
7. hot activation cooling system as claimed in claim 1; And comprise second vapor compression circuit parallel with said first vapor compression circuit; Said second vapor compression circuit has expansion gear, evaporimeter and the compressor of the fluid interconnection of himself, to play a role with said first heat exchanger.
8. hot activation cooling system as claimed in claim 1, and comprise a plurality of valves, be used for optionally causing said vapor compression system to be used as heat pump.
9. hot activation cooling system as claimed in claim 8, wherein, said a plurality of valves comprise two expansion gears, one is used for said first heat exchanger, and another is used for said second heat exchanger.
10. hot activation cooling system as claimed in claim 8, wherein, said a plurality of valves comprise single two-way expansion gear, it is optionally operated so that cold-producing medium stream is transmitted to said first or second heat exchanger.
11. hot activation cooling system as claimed in claim 8, wherein, said a plurality of valves comprise a plurality of check-valves, and it is optionally operated so that cold-producing medium stream is transmitted to said first or second heat exchanger.
12. hot activation cooling system as claimed in claim 1, and comprise secondary heater, it is connected with the serial flow relation with said heater.
13. hot activation cooling system as claimed in claim 1, wherein, said compressor comprises compound compressor, and further comprises and be operatively coupled on said gas cooler between multistage.
14. hot activation cooling system as claimed in claim 1, wherein, said compression circuit comprises displacer, is used to advance said cold-producing medium to flow to said compressor.
15. hot activation cooling system as claimed in claim 14; Wherein, The cold-producing medium stream that is used for cooling performance is split into two parts; Said displacer is provided power by a part of said cold-producing medium stream and discharges another part of said cold-producing medium stream, and it also is processed to aspirating in the heat exchanger at said liquid at said evaporimeter then.
16. hot activation cooling system as claimed in claim 14; Wherein, Said compression circuit comprises the suction accumulator; The cold-producing medium stream that is used for cooling performance provides power for said displacer, discharges the liquid part of said stream, and it is collected in the said suction accumulator and in said evaporimeter and is processed.
17. hot activation cooling system as claimed in claim 1, wherein, said vapor compression circuit comprises the saver that is operably connected with it.
18. hot activation cooling system as claimed in claim 1, and comprise and two phase expanders be interconnected between said condenser and the said evaporimeter its fluid.
19. hot activation cooling system as claimed in claim 1, wherein, said expander, said pump and said compressor have public axle.
20. hot activation cooling system as claimed in claim 1, wherein, power generator and said expander have public axle, and said power generator is that said pump and said compressor provide power.
21. hot activation cooling system as claimed in claim 1, wherein, power generator, said expander and said pump have public axle, and said power generator is that said compressor provides power.
22. hot activation cooling system as claimed in claim 1, wherein, power generator, said expander and said compressor have public axle, and said power generator is supplied with said pump.
23. hot activation cooling system as claimed in claim 18, wherein, said expander, said pump and said compressor have public airtight housing.
24. a power generation steam expanded loop, liquid refrigerant pump, heater, expander and heat exchanger that it comprises power generator and is in the serial flow relation;
Cold-producing medium therefrom cycles through as working fluid, and wherein, said cold-producing medium enables the supercritical, high pressure part and the subcritical low-pressure section in said steam expanded loop;
The size of said first heat exchanger is configured to and is designed such that from the working fluid of its discharging always be in liquid form; And
The size of said pump and said expander is configured to and is designed such that the high-pressure section in said steam expanded loop is always postcritical.
25. power generation steam expanded as claimed in claim 24 loop, wherein, said cold-producing medium is CO
2
26. hot activation cooling system as claimed in claim 24, wherein, said public cold-producing medium is CO
2Mixture with propane.
27. power generation steam expanded as claimed in claim 24 loop, and comprise the heat exchange of top part device, be used to cause heat to flow to the stream of heater from the expander discharge stream.
28. power generation steam expanded as claimed in claim 24 loop, wherein, said expander is the double expansion device, and further wherein, secondary heater is set between the two-stage.
29. power generation steam expanded as claimed in claim 24 loop, and comprise secondary heater, it is connected with the serial flow relation with said heater.
30. power generation steam expanded as claimed in claim 24 loop, wherein, said power generator, said expander and said pump have public axle.
31. power generation steam expanded as claimed in claim 24 loop, wherein, said power generator, said expander and said pump have public airtight housing.
32. power generation steam expanded as claimed in claim 24 loop, wherein, said power generator is that refrigeration system provides power.
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 true CN102414522A (en) | 2012-04-11 |
| CN102414522B 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 |
Country Status (4)
| Country | Link |
|---|---|
| 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 |
|---|---|
| US20120036854A1 (en) | 2012-02-16 |
| CN102414522B (en) | 2014-03-05 |
| WO2010126980A3 (en) | 2011-03-03 |
| WO2010126980A2 (en) | 2010-11-04 |
| EP2425189A2 (en) | 2012-03-07 |
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