CN101688725B - Transcritical refrigerant vapor compression system with charge management - Google Patents
Transcritical refrigerant vapor compression system with charge management Download PDFInfo
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- CN101688725B CN101688725B CN2007800534774A CN200780053477A CN101688725B CN 101688725 B CN101688725 B CN 101688725B CN 2007800534774 A CN2007800534774 A CN 2007800534774A CN 200780053477 A CN200780053477 A CN 200780053477A CN 101688725 B CN101688725 B CN 101688725B
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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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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H1/3204—Cooling devices using compression
- B60H1/3228—Cooling devices using compression characterised by refrigerant circuit configurations
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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
- 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
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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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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
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- 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
- F25B2400/23—Separators
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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
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2509—Economiser valves
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1931—Discharge pressures
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/19—Pressures
- F25B2700/193—Pressures of the compressor
- F25B2700/1933—Suction pressures
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
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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
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2115—Temperatures of a compressor or the drive means therefor
- F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor
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- Thermal Sciences (AREA)
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Abstract
A refrigerant vapor compression system includes a refrigerant-to-refrigerant heat exchanger economizer and a flash tank disposed in series refrigerant flow relationship in the refrigerant circuit intermediate a refrigerant heat rejection heat exchanger and a refrigerant heat absorption heat exchanger. A primary expansion valve is interdisposed in the refrigerant circuit upstream of the refrigerant heat absorption heat exchanger and a secondary expansion valve is interdisposed in the refrigerant circuit upstream of the flash tank. The flash tank functions as a refrigerant charge storage reservoir wherein refrigerant expanded from a supercritical pressure to subcritical pressure separates into liquid and vapor phases. A refrigerant vapor bypass line is provided to return refrigerant vapor from the flash tank to the refrigerant circuit downstream of the refrigerant heat absorption heat exchanger. The primary expansion valve and a flow control valve interdisposed in the refrigerant vapor bypass provide refrigerant charge management.
Description
[technical field]
The present invention relates generally to refrigerant vapor compression system, and more specifically, relate to striding the refrigerant charge management in the refrigerant vapor compression system of critical cycle operation.
[background technology]
Refrigerant vapor compression system is known prior art, and it is generally used for regulating the air that will supply to the climate controlling comfort zone in dwelling house, office building, hospital, school, restaurant or other facility.Refrigerant vapor compression system also is used in the air that refrigeration supplies to other perishable/frozen product memory block in showcase, vending machine, refrigerating chamber, refrigerator or the commercial undertaking usually.
Refrigerant vapor compression system also is used in transport refrigeration system usually; be used for the air that refrigeration supplies to the temperature control goods space of truck, trailer, container etc., thereby by truck, railway (rail), ship transportation or the perishable/reefer cargo of intermodal transport ground transportation.Since widely the running load condition and range and widely the outdoor environmental conditions scope (under this outdoor environmental conditions, refrigerant vapor compression system must move, in order to the product in the goods space is remained on the temperature of expectation), so the refrigerant vapor compression system of uniting use with transport refrigeration system generally can suffer more strict service condition.The preferred temperature that goods need to be controlled at this can also change on a large scale according to the character of preserving goods.Refrigerant vapor compression system must not only have the temperature that enough volumes and refrigerant charge are come the product of the fast reducing goods space of packing at ambient temperature, must effectively operation under lower extra refrigerant charge load when during transportation keeping stable product temperature.In addition, transport refrigeration agent steam compression system can suffer vibrations and the mobile impact that static refrigerant vapor compression system can not run into.Like this, store the impact that extra refrigerant liquid will be subjected to rock between moving period at the suction line that is positioned at compressor suction inlet upstream with conventional refrigerant collecting tank, may cause like this refrigerant liquid to be brought into compressor by suction line via the suction inlet on it undesirably.
Traditionally, most of these refrigerant vapor compression systems move under subcritical refrigerant pressure, and typically comprise compressor, condenser, evaporimeter and the expansion gear (normally expansion valve) that is arranged on vaporizer upstream and condenser downstream with respect to cold-producing medium stream.These basic refrigerant system assemblies are interconnected on by refrigerant lines in the refrigerant loop of closing, and arrange according to known refrigerant vapor compression cycle, and move under the subcritical pressure boiler scope of particular refrigerant in use.The refrigerant vapor compression system that moves in subcritical range generally is filled with fluorocarbon refrigerants, such as, but not limited to, fluorochlorohydrocarbon (HCFC) is such as R22, and be filled with more at large HFC compound (HFC), such as R134a, R410A, R404A and R407C.
On current market, " natural " cold-producing medium such as carbon dioxide that substitutes the HFC cold-producing medium to being used in air conditioning and transport refrigeration system shows larger interest.But because carbon dioxide has lower critical-temperature, major part is filled with carbon dioxide and is designed to move striding under the critical pressure state as the refrigerant vapor compression system of cold-producing medium.In the refrigerant vapor compression system with the subcritical cycle operation, condenser and evaporator heat exchanger are both moved under the refrigerant temperature under the critical point of cold-producing medium and pressure.But, in with the refrigerant vapor compression system of striding the critical cycle operation, (this heat rejection heat exchanger is gas cooler to heat rejection heat exchanger, but not condenser) under the refrigerant temperature of the critical point that surpasses cold-producing medium and pressure, move, and evaporimeter in subcritical range refrigerant temperature and pressure under move.Like this, for the refrigerant vapor compression system that moves in striding critical cycle, the refrigerant pressure in the gas cooler and the difference between the refrigerant pressure in the evaporimeter are characteristically substantially greater than the refrigerant pressure in the condenser of the refrigerant vapor compression system that moves with subcritical cycle and the difference between the refrigerant pressure in the evaporimeter.
Incorporating economizer into refrigerant loop, also is usual practice for increasing the capacity of refrigerant vapor compression system.For example, in some system, cold-producing medium-refrigerant heat exchanger is merged in refrigerant loop as economizer.The first's cold-producing medium that leaves condenser passes the first path of heat exchanger and the second portion cold-producing medium heat exchange of passing the heat exchanger alternate path.The second portion cold-producing medium typically consists of the part cold-producing medium that leaves condenser, this part cold-producing medium turns to by expansion gear, and wherein this part cold-producing medium passes steam or the vapor/liquid mixture cold-producing medium that is inflated into lower pressure and lower temperature before the alternate path of economizer cold-producing medium-refrigerant heat exchanger at this second portion cold-producing medium.Behind the alternate path that passes across economizer heat exchanger, the second portion cold-producing medium changes level from the intermediate pressure that this is introduced into compression process.Pass across before entering evaporimeter before the main expansion gear of system, the cold-producing medium in the main refrigerant circuit passes the first path of cold-producing medium-cold-producing medium economizer heat exchanger and therefore is further cooled.The 6th, 058, No. 729 United States Patent (USP) has disclosed a kind of for cold-producing medium-refrigerant heat exchanger being incorporated into refrigerant loop as the subcritical refrigerant vapor compression systems of the transport refrigeration unit of economizer.The 6th, 694, No. 750 United States Patent (USP)s have disclosed a kind of subcritical refrigeration system that is included in the first cold-producing medium of arranging continuously between condenser in the refrigerant loop and the evaporimeter-refrigerant heat exchanger economizer and second refrigerant-refrigerant heat exchanger economizer.
In some system, the flash tank economizer is merged in the refrigerant loop between condenser and the evaporimeter.In this case, the cold-producing medium that leaves condenser expanded by the expansion gear such as thermostatic expansion valve or electric expansion valve before entering flash tank, and the cold-producing medium after wherein expanding is separated into liquid refrigerant component and vapor refrigerant component.The steam component of cold-producing medium is introduced the intermediate pressure stage of compression procedure thus from flash tank.The liquid component of cold-producing medium was guided through the main expansion valve of system from flash tank before entering evaporimeter.The 5th, 174, No. 123 United States Patent (USP)s have disclosed a kind ofly incorporates the flash tank economizer in the refrigerant loop between condenser and the evaporimeter subcritical steam compressibility.The 6th, 385, No. 980 United States Patent (USP) has disclosed a kind of transcritical refrigerant steam compression system of the flash tank economizer being incorporated into the refrigerant loop between gas cooler and the evaporimeter.
[summary of the invention]
A kind of transcritical refrigerant steam compression system with improved refrigerant charge management comprises main refrigerant circuit, comprise compressing apparatus of refrigerant, be used for becoming the refrigerant cools heat exchanger of heat exchanging relation with cold medium so that the cold-producing medium that receives from described compression set under high pressure circulates, be used for so that the cold-producing medium heating heat exchanger that cold-producing medium under low pressure circulates and becomes heat exchanging relation with thermal medium, and the main expansion gear that in main refrigerant circuit, is arranged on described refrigerant cools heat exchanger downstream and described cold-producing medium heating heat exchanger upstream; The economizer circuit refrigerant lines extends to the intermediate pressure stage of described compression set from described main refrigerant circuit in the mode of refrigerant flow communication; Cold-producing medium-refrigerant heat exchanger economizer has the first refrigerant passage and second refrigerant path, described the first refrigerant passage is arranged on described refrigerant cools heat exchanger downstream and described main expansion gear upstream in main refrigerant circuit, described second refrigerant channel setting is in the economizer circuit refrigerant lines; Flash tank, be arranged on the first refrigerant passage downstream of cold-producing medium described in the main refrigerant circuit-refrigerant heat exchanger economizer and the upstream of described main expansion gear, described flash tank limits the separation chamber, wherein liquid refrigerant collecting is in the bottom of described separation chamber, in the part of the described separation chamber of the cold-producing medium of steam state above the cold-producing medium of liquid state; Secondary expansion gear is arranged in the main refrigerant circuit with described flash tank relating operation and is located thereon trip; Evaporator bypass line has been set up refrigerant flow communication between the top of the described separation chamber of described flash tank and the suction pressure portion in the described main refrigerant circuit in described cold-producing medium heating heat exchanger downstream; The economizer circuit expansion gear, described economizer circuit expansion gear is arranged on the upstream with respect to the cold-producing medium stream of the second refrigerant path of described cold-producing medium-refrigerant heat exchanger economizer of described economizer circuit refrigerant lines, the cold-producing medium stream by the second refrigerant path is measured and regulated to the economizer circuit expansion gear, in order in the refrigerant vapour that leaves the second refrigerant path, keep the superheat level of expectation, thereby reduce the wherein existence of liquid; And bypass flow control valve, be arranged in the described evaporator bypass line, described bypass flow control valve has the first open position and the second closed position, wherein refrigerant vapour can be in the first open position by described evaporator bypass line, and refrigerant vapour is prevented from by described evaporator bypass line at place, the second closed position.
Cold-producing medium-refrigerant heat exchanger economizer has the first refrigerant passage and the second bypass, wherein the first refrigerant passage is arranged on refrigerant cools heat exchanger downstream and the main expansion gear upstream in the main refrigerant circuit, the second bypass is arranged in the economizer circuit refrigerant lines, this economizer circuit refrigerant lines from the main refrigerant circuit refrigerant flow communication extend to the intermediate pressure stage of compression set.The economizer circuit expansion gear is arranged on the upstream with respect to the cold-producing medium stream of the second refrigerant path of cold-producing medium-refrigerant heat exchanger economizer in the economizer circuit refrigerant lines.The economizer circuit expansion gear can comprise electric expansion valve or thermostatic expansion valve.
In one embodiment, the by-pass control valve can comprise dibit magnetic valve, pulse width modulation solenoid valve or electric expansion valve.In one embodiment, main expansion valve can comprise electric expansion valve or thermostatic expansion valve.In one embodiment, secondary expansion valve can comprise electric expansion valve or fixing hole expansion valve.
In one embodiment, compression set can be the single compressor with at least the first compression stage and second compression stage.In one embodiment, compression set can be the first compressor and the second compressor, its mode with continuous refrigerant flow communication is arranged in the main refrigerant circuit, and the air exit of described the first compressor becomes refrigerant flow communication with the suction inlet of the second compressor.No matter be at single compressor set or in the twin compressor device, each compressor can be scroll compressor, reciprocating compressor or screw compressor.
[description of drawings]
In order further to understand the present invention, with reference to of the present invention following detailed description the in detail that reads in conjunction with the accompanying drawings, wherein:
Fig. 1 shows the schematic diagram according to an example embodiment of refrigerant vapor compression system of the present invention;
Fig. 2 show be illustrated among Fig. 1, with the chart of the pressure enthalpy relation of the example embodiment of the refrigerant vapor compression system of the present invention of striding critical cycle operation.
Fig. 3 shows to stride the chart of critical cycle pressure enthalpy relation operation, the prior art refrigerant vapor compression system; And
Fig. 4 shows with chart single flash tank economizer, that concern to stride critical cycle pressure enthalpy operation, the prior art refrigerant vapor compression system.
[specific embodiment]
Referring now to Fig. 1, drawn the example embodiment of transcritical refrigerant vapor compression system 10, this transcritical refrigerant vapor compression system is suitable for transport refrigeration system, and this transport refrigeration system refrigeration supplies to the air of the temperature control goods space of the truck, trailer, container of the perishable reefer cargo of transportation etc.Refrigerant vapor compression system 10 also is suitable for regulating the air that will supply to the climate controlling comfort zone in dwelling house, office building, hospital, school, restaurant or other facility.Refrigerant vapor compression system can also be used for the air that refrigeration supplies to other perishable frozen product memory block of showcase, vending machine, refrigerating chamber, refrigerator or commercial undertaking.
Transcritical refrigerant steam compression system 10 comprises that multi-stage compression device 20, cold-producing medium heat rejection heat exchanger 40 (being also referred to as in this article gas cooler), cold-producing medium heating heat exchanger 50 (being also referred to as in this article evaporimeter) and main expansion gear 55 are (such as for example, electric expansion valve or thermostatic expansion valve with evaporimeter 50 co-operations (operativelyassociated with)) and the various refrigerant lines 2,4 and 6 that are connected the aforementioned components in the main refrigerant circuit.Compression set 20 is used for compressed refrigerant also so that cold-producing medium circulates in main refrigerant circuit, as discussing in more detail hereinafter.Compression set 20 can comprise single, multi-stage refrigerating agent compressor, for example, reciprocating compressor, it has the first compression stage 20a and second level 20b, perhaps single compressor, for example, scroll compressor or screw compressor, it is applicable in the usual way with the intermediate pressure point of cold-producing medium by inlet injection compressor compresses chamber, by this, the first compression stage 20a is positioned at the upstream of intermediate pressure point, and the second compression stage 20b is positioned at the downstream of intermediate pressure point.The cold-producing medium that the first compression stage 20a and the second compression stage 20b arrange and leave the first compression stage directly to pass to the second compression stage is the relation of continuous cooling agent stream, is used for further compression.Compression set 20 also can comprise a pair of compressor 20a and 20b, and it is connected in the main refrigerant circuit by the relation that the refrigerant lines of the air exit of the first compressor 20a of the suction inlet refrigerant flow communication of connection and the second compressor 20b flows with continuous cooling.Compressor 20a and 20b can be the combinations of compressor or any this class compressor of scroll compressor, screw compressor, reciprocating compressor, Rotary Compressor or other any type.
Cold-producing medium heat rejection heat exchanger 40 can comprise finned tube exchanger 42, and the warm refrigerant of high pressure is to pass through this finned tube exchanger 42 with the relation of cold medium (modal by the surrounding air of condenser fan 44 by heat exchanger 42 suctions) heat exchange.Finned tube exchanger 42 can comprise for example fin round tube heat exchange coil or the dull and stereotyped microchannel of fin tubular type heat exchanger.
In addition, refrigerant vapor compression system 10 of the present invention comprises cold-producing medium-refrigerant heat exchanger economizer 60 and flash tank 70, and its relation with continuous cooling agent stream is arranged on the downstream of the gas cooler 40 in the refrigerant line 4 of main refrigerant circuit and is arranged on the upstream of evaporimeter 50 with respect to cold-producing medium stream with respect to cold-producing medium stream.Cold-producing medium-refrigerant heat exchanger economizer 60 be arranged in the refrigerant lines 4 of main refrigerant circuit with respect to the downstream of the cold-producing medium stream of gas cooler 40 with respect to the upstream of the cold-producing medium stream of flash tank 70.In addition, be provided with secondary expansion gear 75 in the main refrigerant circuit between cold-producing medium-refrigerant heat exchanger economizer 60 and flash tank 70, such as for example, electric expansion valve or fixed restriction aperture apparatus.
Cold-producing medium-refrigerant heat exchanger economizer 60 comprises the first refrigerant passage 62 and the second refrigerant path 64 of arranging with heat transfer relation.The first refrigerant passage 62 is arranged in the refrigerant lines 4 and the forming section main refrigerant circuit.Second refrigerant path 64 is not put in refrigerant lines 12 and the forming section economizer circuit.Economizer circuit refrigerant lines 12 is connected with the intermediate pressure stage refrigerant flow communication ground of compression process.In the exemplary embodiment of figure 1, economizer circuit refrigerant lines 12 is connected to and is positioned at respect to the refrigerant lines 4 of the main refrigerant circuit of the upstream of the first path 62 cold-producing mediums of cold-producing medium-cold-producing medium heat exchange economizer 60 stream and sets up cold-producing medium stream.Perhaps, the economizer circuit refrigerant lines can be connected to the refrigerant lines 4 that is positioned at respect to the major loop in the downstream of the first path 62 cold-producing mediums of cold-producing medium-cold-producing medium heat exchange economizer 60 stream.The first refrigerant passage 62 of cold-producing medium-refrigerant heat exchanger economizer 60 and second refrigerant path 64 can optionally be arranged by laminar heat transfer relation (in parallel flow heat exchangerelationship) or heat convection relation.Cold-producing medium-refrigerant heat exchanger 60 can be brazing plate type heat exchanger, interior pipe heat exchanger (tube-in-tube heat exchanger), upper pipe heat exchanger (tube-on-tubeheat exchanger) or shell-and-tube heat exchanger (shell-and-tube heat exchanger).
Economizer circuit expansion gear 65 is arranged on the economizer circuit refrigerant lines 12 that is positioned at respect to the upstream of the cold-producing medium stream of the alternate path 64 of cold-producing medium-refrigerant heat exchanger economizer 60.Economizer circuit expansion gear 65 metering with the relation of the cold-producing medium heat exchange of the first path by the heat exchanger economizer 60 cold-producing medium stream by the alternate path 64 of refrigerant lines 12 and cold-producing medium-refrigerant heat exchanger economizer 60, in order in the refrigerant vapour of the alternate path 64 that leaves heat exchanger economizer 60, keep the superheat level of expectation, thereby guarantee wherein not have liquid.Expansion valve 65 can be electric expansion valve, and for example, as shown in Figure 1-Figure 3, in this case expansion valve 65 responses come the signal of self-controller 100 to come the metrology refrigerant flow, in order to keep refrigerant temperature or the pressure of expectation in refrigerant lines 12.Expansion gear 65 can also be thermostatic expansion valve, in this case expansion valve 65 response is by the refrigerant temperature of sensing device (not shown) sensing or pressure indicating signal and the metrology refrigerant flow, described sensing device can be conventional temperature-sensitive element, for example is mounted to bulb or the thermocouple of the refrigerant lines 12 in the alternate path downstream that is positioned at heat exchanger economizer 60.Refrigerant vapour by economizer circuit refrigerant lines 12 is injected into compression set 20 at the intermediate pressure end of compression process.For example, if compression set 20 is multistage reciprocating compressors, then refrigerant lines 12 is directly introduced intermediate pressure stage between this reciprocating compressor the first compression stage 20a and the second compression stage 20b with refrigerant vapour.If compression set 20 is single scroll compressor or single screw compressor, then refrigerant lines 12 is introduced refrigerant vapour at the intermediate pressure place of compression process the inlet of opening to the compression set of the discharge chambe of this compression set.If compression set 20 is compressor 20a of a pair of continuous connection, 20b (for example, a pair of scroll-type compression or screw compressor or reciprocating compressor), or single reciprocating compressor with the first cylinder group and second cylinder group, the second economizer circuit refrigerant lines 12 is introduced refrigerant lines with refrigerant vapour, this refrigerant lines so that the air exit of the first compressor 20a be connected with the suction inlet refrigerant flow communication ground of the second compressor 20b.
Flash tank 70 is arranged on that the cold-producing medium that is arranged in respect to the first path 62 of cold-producing medium-refrigerant heat exchanger economizer 60 flows down trip and with respect to the refrigerant lines 4 of the main refrigerant circuit of the cold-producing medium stream upstream of evaporimeter 50, in order to receive the cold-producing medium that flows through refrigerant lines 4.Secondary expansion gear 75 is arranged on that the cold-producing medium that is arranged in respect to the first refrigerant passage 62 of cold-producing medium-refrigerant heat exchanger economizer 60 flows down trip and with respect to the refrigerant lines 4 of the main refrigerant circuit of the cold-producing medium stream upstream of flash tank 70 entrances.Along with it crosses secondary expansion gear 75, the high pressure refrigerant vapor by refrigerant lines 4 was expanded to subcritical pressure boiler and temperature before cold-producing medium passes into flash tank 70.Secondary expansion gear 75 can be electric expansion valve, as shown in Figure 1, in this case, 75 responses of secondary expansion valve come the signal of self-controller 100 and the metrology refrigerant flow, in order to keep the refrigerant pressure of expectation in the refrigerant lines 4 that is being arranged in respect to the cold-producing medium stream upstream of secondary expansion gear 75.Secondary expansion gear 75 can also only be fixed orifice expansion device, in this case, the refrigerant pressure that is arranged in respect to the refrigerant lines 4 of the cold-producing medium of secondary expansion gear 75 stream upstream will fluctuate according to environmental condition, and cold-producing medium stream will fundamentally be measured according to the magnitude of the pressure differential of passing fixed orifice.
Flash tank 70 limits separation chamber 72, the cold-producing medium that expands flows to this separation chamber 72 under subcritical pressure boiler, and the vapor portion that is separated into the liquid refrigerant part that is collected in flash tank 70 bottoms and is collected in flash tank 70 tops of top, flash tank 70 interior fluid level.Like this, flash tank 70 is as receiver, the whenever storage of liquids cold-producing medium that is used for turning round under this refrigerant vapor compression system is not needing the capacity of the full filling quantity of cold-producing medium of this system.
In addition, this refrigerant vapor compression system comprises refrigerant lines 14, and this refrigerant lines 14 is being positioned at respect to the downstream of the cold-producing medium stream of evaporimeter 50 outlets with respect to the some place of the upstream of the cold-producing medium stream of compression set 20 suction inlets having set up refrigerant flow communication between the flash tank 70 of main refrigerant circuit and refrigerant lines 6.
The refrigerant vapour that is collected in the part of flash tank 70 of top, fluid level wherein passes refrigerant lines 14 from flash tank 70, entering main refrigerant circuit, thereby gets back to compression set 20.Bypass flow control valve 85 is arranged in the refrigerant lines 14, with by the flowing of refrigerant lines 14 restriction refrigerant vapours, in order to where necessary the separation chamber 72 of flash tank 70 is remained on the refrigerant pressure that is higher than suction pressure.In one embodiment, bypass flow control valve 85 comprises the magnetic valve with the first open position and second closed position, for example such as, but not limited to, pulse width modulation solenoid valve.In one embodiment, bypass flow control valve 85 can comprise electric expansion valve.
The liquid refrigerant that is collected in the bottom of flash tank economizer 70 passes from here refrigerant lines 4 and crosses main refrigerant circuit expansion valve 55, this main refrigerant circuit expansion valve 55 can be electric expansion valve or conventional thermostatic expansion valve, and it is arranged on the refrigerant lines 4 that is arranged in respect to the cold-producing medium stream upstream of evaporimeter 50.Along with this liquid refrigerant crosses the first expansion gear 55, it is expanded to lower pressure and temperature before entering evaporimeter 50.Along with liquid refrigerant passes evaporimeter 50, this liquid refrigerant becomes heat exchanging relation ground to flow through with thermal medium, and by this, this liquid refrigerant is vaporized and typically by superheat, and this thermal medium is cooled.In one embodiment, evaporimeter 50 consists of finned tube coil heat exchanger 52, such as, the dull and stereotyped microchannel of fin round tube heat exchanger or fin tubular type heat exchanger.The hot fluid that becomes heat exchanging relation ground to flow through with cold-producing medium in the evaporimeter 50 can be air, described air is aspirated from the climate controlling environment by the fan 54 that links, such as relevant with transport refrigeration unit perishable/food of reefer cargo memory block or commercial undertaking shows or the memory block, perhaps relevant with air handling system, the building comfort zone that will lower the temperature and usually also will dehumidify, and the air that aspirates turns back to the climate controlling environment thus.The low pressure refrigerant vapor of leaving evaporimeter 50 turns back to the suction inlet of compression set 20 by refrigerant lines 6.
In conventional practice, main expansion valve 55 meterings are by the cold-producing medium stream of refrigerant lines 4, leaving evaporimeter 50 and to pass the heat of crossing that keeps aspiration level in the refrigerant vapour of refrigerant lines 6, there is not liquid thereby guarantee to leave in the cold-producing medium of evaporimeter.As noted above, main expansion valve 55 can be electric expansion valve, in this case, expansion valve 55 response comes the signal of self-controller 100 and the metrology refrigerant flow, to keep inlet temperature or the suction pressure of expectation in the refrigerant lines 6 on the suction side of compression set 20.Main expansion gear 55 can also be thermostatic expansion valve, in this case, expansion valve 55 responds the metrology refrigerant flow by the index signal of the refrigerant temperature of sensing device sensing or pressure, sensing device can be conventional temperature-sensitive element, for example is installed near bulb or the thermocouple of the refrigerant lines 6 evaporator outlet.
In the example embodiment of refrigerant vapor compression system shown in Figure 1 10, the running of refrigerant vapor compression system is controlled by control system, described control system comprises controller 100, this controller 100 be arranged on the bypass flow control valve 85 in the refrigerant lines 14 and be arranged on economizer circuit expansion gear 65 relating operations in the refrigerant lines 12.Controller 100 can also be controlled the operation of electric expansion valve 55 and 65, compression set 20 and fan 44 and 54.By convention, except the monitoring environment condition, controller 100 can also be by with controller 100 relating operations and be arranged on the various operational factors of various Sensor monitorings of the select location of whole system.For example, in the exemplary embodiment of figure 1, pressure sensor 102 can arrange with flash tank 70 relating operation ground, with the pressure in the sensing flash tank 70, temperature sensor 103 and pressure sensor 104 can be configured to respectively sensing cold-producing medium inlet temperature and pressure, and temperature sensor 105 and pressure sensor 106 can dispose respectively sensing cold-producing medium exhaust temperature and pressure.Pressure sensor 102,104,106 can be conventional pressure sensor, such as for example, pressure transducer, and temperature sensor 103 and 105 can be conventional temperature sensor, such as for example, thermoelectricity is thermistor occasionally.
Refrigerant vapor compression system of the present invention is particularly suited for using the low critical point cold-producing medium such as carbon dioxide to move to stride critical cycle, but also can move with subcritical cycle with the higher critical point cold-producing medium of routine.When refrigerant vapor compression system 10 moves under economic model, controller 100 command economy device circuit expansion device 65 are measured from the flow of refrigerant lines 4 by the refrigerant vapour of economizer circuit refrigerant lines 12 with responding system service condition and capacity requirement.When system moved under the non-economy pattern, controller 100 cut out economizer circuit expansion valve 65, thereby all can pass secondary expansion gear 75 and enter thus flash tank 70 from the cold-producing medium that gas cooler 40 passes refrigerant lines 4.In economy or non-economy pattern, controller 100 control main expansion valves 55, the correct amount of the refrigerant liquid of flash tank 70 is left in metering with the system operational parameters (for example, compressor discharge temperature) of response sensing, thus the refrigerant charge demand of matching system.
In addition, controller 100 controls are arranged on the location of the bypass flow control valve 85 in the refrigerant lines 14, limit the flow from the refrigerant vapour of flash tank 70 with the pressure in separation chamber's flash tank 70 of response sensing, thereby keep the subcritical flash tank pressure of expectation.To depend on subcritical pressure boiler level in the separation chamber because appear at the ratio of refrigerant liquid in the flash tank and refrigerant vapour, thereby flash tank pressure can be controlled the refrigerant quality that generation is selected when expanding with box lunch by location bypass flow control valve 85.If bypass flow control valve 85 is closed continuously, then the pressure in the flash tank will rise to the upper limit of gas cooler pressure.If bypass flow control valve 85 is opened continuously, then the pressure in the flash tank 70 will be down to lower pressure, but on suction pressure.When the bypass flow control valve was opened fully, the pressure in the flash tank and the actual pressure between the suction pressure are poor will be by the size Control of the throttle orifice in the specific bypass flow control valve that uses.Refrigerant vapour is disposed to suction pressure from flash tank 70 by refrigerant lines 14 with controlling, and low-pressure is necessary in the flash tank to keeping.Therefore, controller 100 can also be continuously so that bypass flow control valve 85 circulate opening and closing between the position, optionally to control flash tank pressure.This manipulation of main expansion valve 55 and bypass flow control valve 85 provides in the effective ability of management and control refrigerant charge (even refrigerant vapor compression system 10 is when striding the critical conduction mode operation) between the service condition scope widely for controller 100.In addition, cold-producing medium is separated into liquid phase and vapour phase and only liquid refrigerant is transmitted by evaporimeter in flash tank 70, and vapor refrigerant is diverted to the some place in evaporimeter downstream, improved like this heat exchange efficiency in the evaporimeter.
Arbitrary pressure enthalpy of pressure enthalpy (the pressure to enthalpy) relation that the feature of the refrigerant vapor compression system 10 of representative graph 1 shown in Figure 2 is pressed the enthalpy relation and Fig. 3 or the conventional refrigerant vapor compression system of representative shown in Figure 4 concerns has relatively explained the capacity improvements relevant with refrigerant vapor compression system of the present invention.Fig. 3 show have single cold-producing medium-feature of the conventional prior art transcritical refrigerant both vapor compression of cold-producing medium heat exchange economizer presses the enthalpy relation.Fig. 4 shows the feature of the conventional prior art transcritical refrigerant both vapor compression with single flash tank economizer and presses the enthalpy relation.Among each figure of Fig. 2-Fig. 4, AB represents the gas heat extraction process in the gas cooler 40, and DE represents the gas endothermic process in the evaporimeter 50.Among Fig. 2, KG represents the process in cold-producing medium-cold-producing medium heat exchange economizer circuit, and MN represents the process in flash tank-suction evaporimeter bypass circulation.Among Fig. 3, KG represents the process in cold-producing medium-cold-producing medium heat exchange economizer circuit.Among Fig. 4, JL represents the process in the flash tank economizer circuit.Evaporimeter pipeline DE among Fig. 1 is longer than each refrigerant lines relevant with the single economizer system of arbitrary prior art, shows the evaporator effectiveness relevant with refrigerant vapor compression system of the present invention that increases.
Person of skill in the art will appreciate that and to carry out many changes to the particular exemplary embodiment that describes herein.Although the present invention is specifically shown with reference to example embodiment shown in the drawings and is described, do not deviating from the situation of the spirit and scope of the present invention defined by the claims, it should be appreciated by those skilled in the art that various trickle changes are effective here.
Claims (18)
1. refrigerant vapor compression system comprises:
Main refrigerant circuit, comprise compressing apparatus of refrigerant, be used for becoming the refrigerant cools heat exchanger of heat exchanging relation with cold medium so that the cold-producing medium that receives from described compression set under high pressure circulates, be used for so that the cold-producing medium heating heat exchanger that cold-producing medium under low pressure circulates and becomes heat exchanging relation with thermal medium, and the main expansion gear that in main refrigerant circuit, is arranged on described refrigerant cools heat exchanger downstream and described cold-producing medium heating heat exchanger upstream; The economizer circuit refrigerant lines extends to the intermediate pressure stage of described compression set from described main refrigerant circuit in the mode of refrigerant flow communication;
Cold-producing medium-refrigerant heat exchanger economizer has the first refrigerant passage and second refrigerant path, described the first refrigerant passage is arranged on described refrigerant cools heat exchanger downstream and described main expansion gear upstream in main refrigerant circuit, described second refrigerant channel setting is in the economizer circuit refrigerant lines;
Flash tank, be arranged on the first refrigerant passage downstream of cold-producing medium described in the main refrigerant circuit-refrigerant heat exchanger economizer and the upstream of described main expansion gear, described flash tank limits the separation chamber, wherein liquid refrigerant collecting is in the bottom of described separation chamber, in the part of the described separation chamber of the cold-producing medium of steam state above the cold-producing medium of liquid state;
Secondary expansion gear is arranged in the main refrigerant circuit with described flash tank relating operation and is located thereon trip;
Evaporator bypass line has been set up refrigerant flow communication between the top of the described separation chamber of described flash tank and the suction pressure portion in the described main refrigerant circuit in described cold-producing medium heating heat exchanger downstream;
The economizer circuit expansion gear, described economizer circuit expansion gear is arranged on the upstream with respect to the cold-producing medium stream of the second refrigerant path of described cold-producing medium-refrigerant heat exchanger economizer of described economizer circuit refrigerant lines, the cold-producing medium stream by the second refrigerant path is measured and regulated to the economizer circuit expansion gear, in order in the refrigerant vapour that leaves the second refrigerant path, keep the superheat level of expectation, thereby reduce the wherein existence of liquid; And
The bypass flow control valve, be arranged in the described evaporator bypass line, described bypass flow control valve has the first open position and the second closed position, wherein refrigerant vapour can be in the first open position by described evaporator bypass line, and refrigerant vapour is prevented from by described evaporator bypass line at place, the second closed position.
2. refrigerant vapor compression system as claimed in claim 1, wherein, described bypass flow control valve comprises the magnetic valve with the first open position and second closed position.
3. refrigerant vapor compression system as claimed in claim 1, wherein, described bypass flow control valve comprises pulse width modulation solenoid valve.
4. refrigerant vapor compression system as claimed in claim 1, wherein, described bypass flow control valve comprises electric expansion valve.
5. refrigerant vapor compression system as claimed in claim 1, wherein, described main expansion gear comprises electric expansion valve.
6. refrigerant vapor compression system as claimed in claim 1, wherein, described main expansion gear comprises thermostatic expansion valve.
7. refrigerant vapor compression system as claimed in claim 1, wherein, described secondary expansion gear comprises electric expansion valve.
8. refrigerant vapor compression system as claimed in claim 1, wherein, described secondary expansion gear comprises the fixing hole expansion valve.
9. refrigerant vapor compression system as claimed in claim 1, wherein, described economizer circuit expansion gear comprises electric expansion valve.
10. refrigerant vapor compression system as claimed in claim 1, wherein, described economizer circuit expansion gear comprises thermostatic expansion valve.
11. refrigerant vapor compression system as claimed in claim 1, wherein, described compression set comprises the single compressor with at least two compression stages.
12. refrigerant vapor compression system as claimed in claim 1, wherein, described compression set comprises with respect to cold-producing medium stream and is arranged at least two compressors in the main refrigerant circuit with serial relation.
13. refrigerant vapor compression system as claimed in claim 1, wherein, described compression set comprises scroll compressor.
14. refrigerant vapor compression system as claimed in claim 1, wherein, described compression set comprises reciprocating compressor.
15. refrigerant vapor compression system as claimed in claim 1, wherein, described compression set comprises screw compressor.
16. refrigerant vapor compression system as claimed in claim 1, wherein, described refrigerant vapor compression system is incorporated in the transport refrigeration system, is used for regulating the goods memory block of temperature control.
17. refrigerant vapor compression system as claimed in claim 16, wherein, described refrigerant vapor compression system is to stride the critical cycle operation.
18. refrigerant vapor compression system as claimed in claim 17, wherein, described cold-producing medium comprises carbon dioxide.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/US2007/010066 WO2008130358A1 (en) | 2007-04-24 | 2007-04-24 | Transcritical refrigerant vapor compression system with charge management |
Publications (2)
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| CN101688725A CN101688725A (en) | 2010-03-31 |
| CN101688725B true CN101688725B (en) | 2013-03-27 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2007800534774A Expired - Fee Related CN101688725B (en) | 2007-04-24 | 2007-04-24 | Transcritical refrigerant vapor compression system with charge management |
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| US (1) | US20100132399A1 (en) |
| EP (1) | EP2147269A4 (en) |
| JP (1) | JP5196452B2 (en) |
| CN (1) | CN101688725B (en) |
| WO (1) | WO2008130358A1 (en) |
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- 2007-04-24 US US12/596,885 patent/US20100132399A1/en not_active Abandoned
- 2007-04-24 EP EP07756034.0A patent/EP2147269A4/en not_active Withdrawn
- 2007-04-24 JP JP2010506153A patent/JP5196452B2/en not_active Expired - Fee Related
- 2007-04-24 CN CN2007800534774A patent/CN101688725B/en not_active Expired - Fee Related
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Also Published As
| Publication number | Publication date |
|---|---|
| EP2147269A4 (en) | 2014-05-28 |
| WO2008130358A1 (en) | 2008-10-30 |
| JP2010525293A (en) | 2010-07-22 |
| CN101688725A (en) | 2010-03-31 |
| EP2147269A1 (en) | 2010-01-27 |
| JP5196452B2 (en) | 2013-05-15 |
| US20100132399A1 (en) | 2010-06-03 |
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