CN101755177A - Economized refrigerant system with flow control - Google Patents
Economized refrigerant system with flow control Download PDFInfo
- Publication number
- CN101755177A CN101755177A CN200780053820A CN200780053820A CN101755177A CN 101755177 A CN101755177 A CN 101755177A CN 200780053820 A CN200780053820 A CN 200780053820A CN 200780053820 A CN200780053820 A CN 200780053820A CN 101755177 A CN101755177 A CN 101755177A
- Authority
- CN
- China
- Prior art keywords
- refrigerant
- cold
- producing medium
- stream
- energy
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- 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
-
- 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
-
- 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
- F25B2600/2513—Expansion valves
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
A refrigerant vapor compression system has a primary refrigerant circuit including a compression device, a refrigerant heat rejection heat exchanger and a refrigerant heat absorption heat exchanger, and an economizer circuit including an economizer refrigerant line. A bypass flow control device controls refrigerant vapor flow through a bypass line extending between the economizer refrigerant line and a suction pressure portion of the primary refrigerant circuit. A flow control apparatus operatively associated with the economizer refrigerant line provides different flow resistance to refrigerant flow through the economizer refrigerant line in a first direction from an intermediate stage of the compression device to the suction portion of the primary refrigerant circuit and in a second direction from the economizer into an intermediate pressure stage of the compression device.
Description
Technical field
The present invention relates generally to refrigerant vapor compression system, relates more specifically to be furnished with the refrigerant vapor compression system of economizer cycle.
Background technology
Refrigerant vapor compression system is well known in the art, is generally used for regulating the air (or other secondary media) in the suitable zone of climate controlled that will be provided in dwelling house, office building, hospital, school, restaurant or other places.Refrigerant vapor compression system also is generally used for transport refrigeration, be supplied to the air of controlled temperature cargo hold of the truck, trailer, container or the like of transportation perishable goods with refrigeration, and be used for commercial refrigeration, suitably to cool off the air in the controlled temperature space that is supplied to cold-room, beverage cooler, dairy products case or refrigerated merchandisers, refrigerated merchandisers is used to show the perishable items goods that is in freezing state.Typically, these refrigerant vapor compression systems comprise: compressor, condenser, evaporimeter; And expansion gear.Usually, expansion gear (typically being fixed orifice, capillary, heating power expansion valve (TXV) or electric expansion valve (EXV)) is arranged in the refrigerant lines, is positioned at the upstream of evaporimeter and the downstream of condenser with respect to cold-producing medium stream.These basic refrigerant vapor compression system assemblies are arranged according to known refrigerant vapor compression cycle by the refrigerant lines interconnected in series in the closed-loop refrigerant circuits.
For the temperature of the performance of improving refrigerant vapor compression system and the refrigerant vapour that control is discharged from the final level of compressor on the operating conditions of wide region, people are known as this system and are furnished with economizer cycle in conjunction with cold-producing medium-cold-producing medium economizer heat exchanger.Economizer heat exchanger generally is arranged in the refrigerant loop between the condenser and evaporimeter.During work, a part is left the cold-producing medium of condenser and is shunted from main refrigerant circuit, is expanded to intermediate pressure, flows through economizer heat exchanger then, constitutes heat exchange relationship with the cold-producing medium major part of leaving condenser.So, any liquid all is evaporated in the cold-producing medium of the energy-conservation expansion stream, and cold-producing medium that then should evaporation is typically by overheated, flows through main refrigerant circuit from condenser and then is further cooled to the cold-producing medium of evaporimeter.Typically, the refrigerant vapour that expands is injected into the intergrade of compression process, one or more injection ports of the intermediate pressure stage of the discharge chambe (or a plurality of discharge chambe) by leading to single compressor, the perhaps refrigerant lines of between the suction inlet of outlet that is infused in the upstream compressor under the situation of multi-compressor system and downstream compressor, extending.
For example, U.S. Pat 6571576 discloses a kind of refrigerant vapor compression system, it is operated in the subcritical cycle and is furnished with economizer heat exchanger, wherein, vapor refrigerant and liquid refrigerant are got back to the intergrade of compression process by one or more economizer injection port that leads to the discharge chambe of scroll compressor.For the refrigerant vapour that injects compressor is provided, part liquid refrigerant is shunted from main refrigerant circuit at the condenser downstream position, expansion gear by means of for example valve is expanded to intermediate pressure and lower temperature, to form the refrigerant liquid/vapour mixture that flows through economizer heat exchanger and refrigerant liquid main flow formation heat exchange relationship subsequently.When passing economizer heat exchanger, this refrigerant liquid/vapour mixture further cools off this liquid from refrigerant liquid main flow draw heat, therefore evaporates any remaining liq component that is in the two-phase mixed state and also typically further heats this steam.The refrigerant vapour that leaves economizer heat exchanger is injected into compressor by the economizer injection port with intermediate pressure (between suction pressure and the discharge pressure) subsequently.In addition, liquid refrigerant is optionally shunted from refrigerant loop in the condenser downstream position, sneak into the refrigerant vapour that flows to compressor from energy-saving appliance, and be injected into the intermediate pressure stage of the discharge chambe of scroll compressor with refrigerant vapour by identical economizer injection port.
U.S. Pat 7114349 discloses a kind of refrigerant vapor compression system, and it has and is arranged in the cold-producing medium-refrigerant heat exchanger that is positioned at the condenser downstream and is positioned at vaporizer upstream with respect to cold-producing medium stream with respect to cold-producing medium stream in the refrigerant loop.By various by-pass lines and the manipulation various ON/OFF magnetic valves related with these by-pass lines, common heat exchangers can be used as economizer heat exchanger or the work of imbibition heat exchanger.When energy-saving appliance work is used as cold-producing medium-refrigerant heat exchanger as by system, cold-producing medium flows through economizer expansion device and flows through cold-producing medium-refrigerant heat exchanger therefrom from main refrigerant circuit, and flows through the residual refrigerant of main refrigerant circuit to evaporimeter from condenser and constitutes heat exchange relationship.Pass after cold-producing medium-refrigerant heat exchanger, the cold-producing medium of expansion is injected into the intermediate pressure stage of compressor, or gets back to main refrigerant circuit at the some place that is positioned at the evaporimeter downstream with respect to cold-producing medium stream and is positioned at the compressor suction upstream.
U.S. Pat 6058729 discloses a kind of subcritical refrigerant vapor compression systems that is used for transport refrigeration unit, and this system is attached in the refrigerant loop cold-producing medium-refrigerant heat exchanger as energy-saving appliance.Disclosed system also comprises and is used for the suction modulation valve (SMV) that throttling flows to the cold-producing medium stream of compressor suction, and the intermediate pressure-suction pressure relief circuit that is used for compressor capacity control.
Summary of the invention
Refrigerant vapor compression system of the present invention comprises main refrigerant circuit, energy-saving device circuit, by-pass line, by-pass control device and energy-saving appliance/compressor unloading current-carrying control device.Main refrigerant circuit comprises compressing apparatus of refrigerant, cold-producing medium heat rejection heat exchanger, cold-producing medium endothermic heat exchanger and main expansion gear, main expansion gear is arranged in the main refrigerant circuit, is in cold-producing medium heat rejection heat exchanger downstream and cold-producing medium endothermic heat exchanger upstream.Energy-saving device circuit comprises the energy-saving appliance refrigerant lines, and the energy-saving appliance refrigerant lines becomes cold-producing medium stream to extend communicatively between the intermediate pressure stage of energy-saving appliance and compression set.
By-pass line is positioned at cold-producing medium endothermic heat exchanger downstream position from what the energy-saving appliance refrigerant lines became that cold-producing medium stream extends to main refrigerant circuit communicatively with respect to cold-producing medium stream.The by-pass control device is arranged in the by-pass line.The by-pass control device has first enable possition and second closed position, can flow through by-pass line at the first open position cold-producing medium, and cold-producing medium is prevented from flowing through by-pass line at place, second closed position.In one embodiment, the by-pass control device can comprise the magnetic valve with first enable possition and second closed position.
In addition, the flow control device that is arranged in the energy-saving appliance refrigerant lines provides first stream and second stream, the first direction of first-class curb from the intermediate pressure stage of compression set to by-pass line be by the energy-saving appliance refrigerant lines, second stream along the second direction of the intermediate pressure stage that enters compression set from energy-saving appliance by the energy-saving appliance refrigerant lines.First stream has the first fluid resistance to the cold-producing medium stream by first stream, and second stream has second fluid resistance to the cold-producing medium stream by second stream, and the first fluid resistance is different from second fluid resistance.In one embodiment, the first fluid resistance is relatively low and second fluid resistance is higher relatively.
In one embodiment, flow control device comprises " fluid diode " device, should be arranged between the intermediate pressure stage and by-pass line that is in compression set in the energy-saving appliance refrigerant lines by " fluid diode " device." fluid diode " device has the various flows dynamic resistance of the direction that depends on the stream by " fluid diode ".The check-valves that has two position openings is an embodiment of this " fluid diode " device.This check-valves is used to illustrate this embodiment, and still, other kinds known in the art " fluid diode " will fall within the scope of the present invention.Check-valves has the primary importance and second stream, cold-producing medium can flow through this check-valves along the first direction from the intermediate pressure stage of compression set to by-pass line in primary importance, and this second stream enters the second direction of intermediate pressure stage of compression set by the energy-saving appliance refrigerant lines along second coolant channel from cold-producing medium-refrigerant heat exchanger.
In one embodiment, flow control device comprises that constituting cold-producing medium with the energy-saving appliance refrigerant lines flows the first branched-refrigerant pipeline that is communicated with, constitute the second branched-refrigerant pipeline that cold-producing medium stream is communicated with and is arranged to be parallel to the first branched-refrigerant pipeline with the energy-saving appliance refrigerant lines, and be arranged in check-valves in the first branched-refrigerant pipeline, check-valves has the primary importance and the second place, can flow through the first branched-refrigerant pipeline at primary importance place cold-producing medium, the cold-producing medium stream that flows through the first branched-refrigerant pipeline at second place place is prevented from and cold-producing medium can flow through the second branched-refrigerant pipeline.
Energy-saving appliance can be heat exchanger energy-saving appliance or flash tank energy-saving appliance.In one embodiment, energy-saving appliance comprises cold-producing medium-refrigerant heat exchanger, and cold-producing medium-refrigerant heat exchanger comprises first coolant channel and is arranged to constitute with described first coolant channel second coolant channel of heat exchange relationship.First refrigerant pass arrangement is in main refrigerant circuit, and second refrigerant pass arrangement is in the energy-saving appliance refrigerant lines.The energy-saving appliance refrigerant lines becomes fluid to extend to the intermediate pressure stage of compression set communicatively by second coolant channel from main refrigerant circuit.In this embodiment, economizer expansion device is arranged in the energy-saving appliance refrigerant lines, is positioned at the upstream of second coolant channel of cold-producing medium-refrigerant heat exchanger with respect to cold-producing medium stream.
The present invention also can be used for flash tank type energy conserving system equally.In this system, the control of by-pass and energy-saving appliance vapor stream realizes with similar type by the stream of cold-producing medium economizer line by control.In such embodiments, the flash tank energy-saving appliance is arranged in the main refrigerant circuit, is positioned at the downstream of cold-producing medium heat rejection heat exchanger and is positioned at the upstream of main expansion gear with respect to cold-producing medium stream with respect to cold-producing medium stream.The energy-saving appliance refrigerant lines becomes refrigerant vapour stream to extend to the intermediate pressure stage of compression set communicatively from the flash tank energy-saving appliance, and economizer expansion device is arranged in the main refrigerant circuit, is positioned at flash tank energy-saving appliance upstream with respect to cold-producing medium stream.
Description of drawings
In order further to understand the present invention, will be with reference to the specific embodiment of the invention hereinafter, and connection with figures understands, wherein:
Fig. 1 is for showing the schematic diagram according to the exemplary embodiment of refrigerant vapor compression system of the present invention; And
Fig. 2 is for showing the schematic diagram according to another exemplary embodiment of refrigerant vapor compression system of the present invention.
The specific embodiment
Further describe the present invention in this exemplary embodiment with reference to the refrigerant vapor compression system 20 that Fig. 1-2 described.As in the legacy system, refrigerant vapor compression system 20 comprises compression set 22, heat rejection heat exchanger 24, evaporator expansion device 26 and evaporimeter 28, various refrigerant lines 3,5 and 7 interconnection that these parts are communicated with by the formation serial refrigerant flow in traditional kind of refrigeration cycle of main refrigerant circuit.This refrigerant vapor compression system 20 is suitable for being used in the transport refrigeration system, air or other gaseous environments in the controlled temperature cargo space of the truck that is used to transport perishable/reefer cargo of being used to freeze, trailer, container etc.Refrigerant vapor compression system 20 also is applicable to the air of regulating the suitable zone of climate controlled that is supplied in dwelling house, office building, hospital, school, restaurant or other places.Refrigerant vapor compression system 20 also can be used for freezing and is supplied to the air of other perishable/frozen product storage areas in showcase, vending machine, freezing cabinet, refrigerating chamber or the commercial location.
In compression set 22, the suction pressure of refrigerant vapour when this refrigerant vapour enters the inhalation port of compression set 22 is compressed into discharge pressure, and discharge pressure is significantly higher than suction pressure.Heat, high pressure refrigerant vapor flow to heat rejection heat exchanger 24 from the discharge port of compression set 22 refrigerant lines 3 by main refrigerant circuit, and by heat rejection heat exchanger 24.In heat rejection heat exchanger 24, heat, high-pressure refrigerant and cooling media formation heat exchange relationship and cooling off, and in subcritical cycle this refrigerant vapour of condensation.Heat rejection heat exchanger 24 can comprise for example fin-tube heat exchanger, for example be fin and pipe heat-exchangers of the plate type, perhaps fin and micro-channel flat heat exchanger, wherein, cold-producing medium flows through heat exchanger tube and environment (typically being the open air) air constitutes heat exchange relationship, this surrounding air was inhaled fin-tube heat exchanger by air moving device, and air moving device for example is one or more and fan (not shown)s heat rejection heat exchanger 24 operative association.
The cold-producing medium that leaves heat rejection heat exchanger 24 flows through the refrigerant lines 5 of main refrigerant circuit to evaporimeter 28.In this case, cold-producing medium pass the evaporator expansion device 26 that is arranged in the refrigerant lines 5 and before entering evaporimeter 28, be expanded to low temperature more, more low-pressure liquid refrigerant or more common be liquid/vapor refrigerant mixture.Evaporator expansion device 26 can be the throttle-type expansion gear, for example capillary or fixed head throttle orifice, heating power expansion valve or electric expansion valve.Evaporimeter 28 constitutes the cold-producing medium endothermic heat exchanger, and liquid or liquid/vapor refrigerant mixture constitute heat exchange relationship by cold-producing medium endothermic heat exchanger and a secondary fluid that will be cooled, typically be dehumidified and be delivered in the air conditioner surroundings.Cold-producing medium is heated at this, and the evaporating liquid component is also typically crossed the steam that heating obtains.A secondary fluid typically is the air that is provided to climate controlled environment, is in the state that is conditioned, is cooled and typically dehumidified.In one embodiment, evaporimeter 28 can comprise fin-tube heat exchanger, cold-producing medium constitutes heat exchange relationship by fin-tube heat exchanger and air, and this air can be extracted and send back to out climate controlled environment by the fan (not shown) of one or more and evaporimeter 28 operative association from climate controlled environment.Fin-tube heat exchanger can comprise for example fin and pipe heat-exchangers of the plate type, or fin and micro-channel flat heat exchanger.The refrigerant vapour that leaves evaporimeter 28 passes the refrigerant lines 7 of main refrigerant circuit, and the inhalation port by compression set enters compression set 22 once more.
Refrigerant vapor compression system 20 further comprises energy-saving device circuit, and energy-saving device circuit comprises energy-saving appliance refrigerant lines 9, economizer heat exchanger 30 and is arranged in related economizer expansion device 32 in the energy-saving appliance refrigerant lines 9.Economizer heat exchanger 30 comprises cold-producing medium-refrigerant heat exchanger, and this heat exchanger has first coolant channel 31 and second coolant channel 33 that is arranged as the formation heat exchange relationship.First coolant channel 31 is arranged in the refrigerant lines 5 of main refrigerant circuit, is positioned at the downstream of heat rejection heat exchanger 24 with respect to cold-producing medium stream, and is positioned at the upstream of evaporator expansion device 26 with respect to cold-producing medium stream.Second coolant channel 33 is arranged in the energy-saving appliance refrigerant lines 9, is positioned at the downstream of economizer expansion device 32 with respect to cold-producing medium stream.The cold-producing medium that passes the refrigerant lines 5 of main refrigerant circuit flows through first coolant channel 31 of economizer heat exchanger 30, and enters the cold-producing medium stream of energy-saving appliance refrigerant lines 9 with second coolant channel 33 that passes economizer heat exchanger 30 from refrigerant lines 5 shunting and constitutes heat exchange relationship.
Energy-saving appliance refrigerant lines 9 is set up cold-producing medium stream and is communicated with between the intermediate pressure stage of the refrigerant lines 5 of main refrigerant circuit and compression process.Describe as Fig. 1, energy-saving appliance refrigerant lines 9 can shunted part of refrigerant with respect to cold-producing medium stream at first coolant channel, 31 upstream positions of economizer heat exchanger 30 from refrigerant lines 5, perhaps describe, shunting part of refrigerant in first coolant channel, 31 downstream position of economizer heat exchanger 30 with respect to cold-producing medium stream as Fig. 2.If the compression set of refrigerant vapor compression system 20 22 is single compressor, scroll compressor for example shown in Figure 1, energy-saving appliance refrigerant lines 9 constitutes the connection of cold-producing medium stream via the injection port 25 of the intermediate pressure stage of the discharge chambe that leads to compressor 22 so.If the compression set of refrigerant vapor compression system 20 22 is a pair of compressor 22A and 22B, as shown in Figure 2, energy-saving appliance refrigerant lines 9 constitutes the connection of cold-producing medium stream with the refrigerant lines 11 of the import of the outlet that is connected the first compressor 22A and the second compressor 22B.
Refrigerant vapor compression system 20 also comprises compressor unloading loop and flow control device, the compressor unloading loop comprises by-pass line 17, by-pass line 17 is set up cold-producing medium stream and is communicated with between the suction refrigerant lines 7 of energy-saving appliance refrigerant lines 9 and main refrigerant circuit, flow control device is for example for being arranged in the valve 50 in the by-pass line 17.Flow control device 50 has at least the first enable possition and second closed position.In one embodiment, flow control device can comprise the dibit magnetic valve with first enable possition and second closed position.Import department at by-pass line, by-pass line 17 taps into energy-saving appliance refrigerant lines 9, tap into the position and be positioned at the downstream of second coolant channel 33 of economizer heat exchanger 30, and be positioned at the upstream of terminal point of energy-saving appliance refrigerant lines 9 at the intermediate pressure stage place of compression set 22 with respect to cold-producing medium stream with respect to cold-producing medium stream.The port of export in refrigerant bypass line, refrigerant bypass line 17 taps into the refrigerant suction pipe line 7 of main refrigerant circuit, tap into the position and be positioned at the downstream of evaporimeter 28 outlets, and be positioned at the upstream of the inhalation port of compression set 22 with respect to cold-producing medium stream with respect to cold-producing medium stream.So, by-pass line 17 provides refrigerant flow path, and intermediate pressure refrigerant can the intermediate pressure stage from compression process enter main refrigerant circuit by this refrigerant flow path, and cold-producing medium is in suction pressure with the unloading compressor in the refrigerant flow path zone.As used in this, refer to the part that energy-saving appliance refrigerant lines 9 is extended about the term " downstream part " of energy-saving appliance refrigerant lines 9 between the terminal point of the energy-saving appliance refrigerant lines 9 at the intergrade place of the intersection point of by-pass line 17 and energy-saving appliance refrigerant lines 9 and compression set 22, refer to the part that energy-saving appliance refrigerant lines 9 is extended between the intersection point of the refrigerant lines 5 of main refrigerant circuit and by-pass line 17 and energy-saving appliance refrigerant lines 9 about the term " upstream portion " of energy-saving appliance refrigerant lines 9.
Refrigerant vapor compression system 20 further comprises check-valves 40, and check-valves is arranged in the downstream part of energy-saving appliance refrigerant lines 9.Check-valves 40 has the primary importance and the second place, wherein, open allowing refrigerant vapour to flow through the downstream part of energy-saving appliance refrigerant lines 9 at primary importance place check-valves, flow through the downstream part of energy-saving appliance refrigerant lines 9 along the direction that enters the compression process intergrade in the compression set 22 from energy-saving appliance refrigerant lines 9 upstream portion at second place place check-valves 40 restriction cold-producing mediums streams along direction from the compression process intergrade of compression set 22.
Referring now to Fig. 1, in the exemplary embodiment of the refrigerant vapor compression system 20 that this Fig. 1 described, flow metering device 42 is arranged to arrange with 40 one-tenth PARALLEL FLOW of check-valves.For example, describe ground as Fig. 1, flow metering device 42 and check-valves 40 can be arranged among the parallel branch 9a and 9b of energy-saving appliance refrigerant lines 9 downstream parts.In this embodiment, when refrigerant vapor compression system 20 is operated in energy saver mode and does not have compressor unloading, flow control device 50 in the by-pass line 17 is closed, the cold-producing medium stream that enters the downstream part of energy-saving appliance refrigerant lines 9 from the upstream portion of energy-saving appliance refrigerant lines 9 makes the check-valves 40 the take-off line 9b be in the second place, and this closes check-valves fully in this embodiment.When check-valves 40 cuts out fully, flow through flow metering device 42 9b of branch of downstream part of energy-saving appliance refrigerant lines 9 from the upstream portion of refrigerant lines 9, enter the intermediate pressure stage of the compression process of compression set 22 from the cold-producing medium of energy-saving appliance.Flow metering device 42 can include but not limited to fixed flow area throttle orifice.For example, in one embodiment, the desirable flowmeter amount of power save mode of operation function can be provided by the size of suitable design take-off line 9a, take-off line 9a self provides the flow restriction of hope thus, thereby need not the other forms of flow metering device 42 among fixed-area throttle orifice or the take-off line 9a.
But, when refrigerant vapor compression system 20 work zone compressor unloadings, by-pass control valve 50 in the by-pass line 17 is opened, refrigerant vapour flows through the 9a of branch of energy-saving appliance refrigerant lines 9 downstream parts from the intergrade of the compression process of compression set 22 thus, make check-valves 40 be in the enable possition, and flow into and flow through by-pass line 17 and flow into and flow through the refrigerant lines 7 of main refrigerant circuit therefrom, the inhalation port by compression set enters compression set 22 once more.If refrigerant vapor compression system 20 is operated in energy saver mode when compressor unloading, the cold-producing medium that passes energy-saving appliance refrigerant lines 9 upstream portion so enters bypass 17, and entering the refrigerant lines 7 of main refrigerant circuit by bypass 17, the inhalation port by compression set enters compression set 22 once more.
Referring now to Fig. 2, in the exemplary embodiment of the refrigerant vapor compression system 20 that Fig. 2 described, the check-valves 40 that is arranged in energy-saving appliance refrigerant lines 9 downstream parts has first full open position and second portion enable possition.In this embodiment, when refrigerant vapor compression system 20 is operated in energy saver mode and does not have compressor unloading, flow control device 50 in the by-pass line 17 is closed, the cold-producing medium stream that enters energy-saving appliance refrigerant lines 9 downstream parts from energy-saving appliance refrigerant lines 9 upstream portion makes check-valves 40 be in the second portion enable possition, and flow control device 50 measurement flow are crossed the cold-producing medium stream of its compression process intermediate pressure stage that enters compression set 22 in this embodiment.But, in this embodiment, when refrigerant vapor compression system 20 band compressor unloading work, by-pass control device 50 in the by-pass line 17 is opened, refrigerant vapour flows through the downstream part of energy-saving appliance refrigerant lines 9 from the compression process intergrade of compression set 22 thus, make check-valves 40 be in its first full open position, cold-producing medium flows into the refrigerant lines 7 that also flows through by-pass line 17 and therefore flow through main refrigerant circuit, and the inhalation port by compression set enters compression set 22 once more.Equally, if refrigerant vapor compression system 20 is operated under the energy saver mode when compressor unloading, the cold-producing medium that passes energy-saving appliance refrigerant lines 9 upstream portion flows into by-pass line 17, and also flowing through the refrigerant lines 7 that by-pass line 17 enters main refrigerant circuit, the inhalation port by compression set enters compression set 22 once more.
In arbitrary embodiment of the present invention, do not having under the power save mode of operation of bypass, the cold-producing medium that has passed second coolant channel 33 of economizer heat exchanger 30 partly flows through energy-saving appliance refrigerant lines 9, gets back to compression set 22 with the intermediate pressure state of compression process.If compression set is single coolant compressor 22, scroll compressor as shown in Figure 1 for example, or the reciprocating compressor of screw compressor or multi cylinder group, at least one injection port of opening under the intermediate pressure state of cold-producing medium by compression process in compressor 22 of second coolant channel 33 of economizer heat exchanger 30 enters compressor 22 so.If as described in Figure 2, compression set is a pair of compressor 20A and the 20B that connects with series relationship with respect to cold-producing medium stream, the cold-producing medium that has so passed second coolant channel 33 of economizer heat exchanger 30 is injected into refrigerant lines 11, and refrigerant lines 11 connects and composes cold-producing medium stream with the discharge port of first order compressor 20A and the inhalation port of high stage compressor 20B and is communicated with.
The location of by-pass control device 50 can be by controlling with the controller 80 of refrigerant vapor compression system 20 operative association.In one embodiment, as conventional practice, controller 80 can constitute main system controller, and can receive operating data about the different system operating parameter, for example (be used for illustration purpose but be not limited to) discharge the refrigerant temperature and/or the pressure of port, compressor inhalation port, evaporator outlet and other positions at compressor, operating data can be provided by the sensor (not shown) of suitable layout according to hope.If main expansion gear 26 is an electric expansion valve, controller 80 also can be controlled the operation of main expansion gear in response to selected operating parameter so.Similarly, if economizer expansion device 32 is an electric expansion valve, controller 80 also can be controlled the operation of economizer expansion device in response to selected operating parameter so.
In the prior art, refrigerant vapor compression system uses the common sparing of energy-saving appliance refrigerant lines, in energy saver mode operating period, cold-producing medium flows through the common sparing of energy-saving appliance refrigerant lines along the first direction that enters the compression set intermediate pressure stage from economizer heat exchanger, but in unloading mode operating period, the common sparing that cold-producing medium flows through the energy-saving appliance refrigerant lines along the second direction from the intermediate pressure stage of compression set is got back to the inhalation port of compression set.In this refrigerant vapor compression system, can't carry out the optimal design of refrigerant lines size for each current control shape dress condition.Typically, be used to unload the best flow area of refrigerant lines of compression set much larger than the best flow area of refrigerant lines that is used for cold-producing medium is injected the intermediate pressure stage of compression set, a for example big order of magnitude.
But, in refrigerant vapor compression system 20 of the present invention, flow control device is provided with first stream and second stream, the first direction of first-class curb from the intermediate pressure stage of compression set to by-pass line passes the energy-saving appliance refrigerant lines, and second stream passes the energy-saving appliance refrigerant lines along the second direction that second coolant channel from cold-producing medium-cold-producing medium economizer heat exchanger enters the intermediate pressure stage of compression set.The cold-producing medium stream that first stream is crossed in the first stream convection current has the first fluid resistance, and second stream has second fluid resistance to the cold-producing medium stream that flows through second stream, and the first fluid resistance is different from second fluid resistance.In one embodiment, the first fluid resistance is relatively low, and second fluid resistance is higher relatively.Therefore, can be each flow area size of flow-optimized these streams of the refrigerant vapour that flows through these streams, this can improve 10% compressor efficiency.
In the exemplary embodiment that Fig. 1 described, the cold-producing medium stream that the refrigerant lines 9b of branch is crossed in check-valves 40 convection current that are in the enable possition provides relatively low fluid resistance, and flow controller 42 convection current are crossed the cold-producing medium stream of the refrigerant lines 9a of branch higher relatively fluid resistance is provided.In the exemplary embodiment that Fig. 2 described, 40 pairs on check-valves provides relatively low fluid resistance along the cold-producing medium stream that the flow path direction from the intermediate pressure stage of compression set 22 to by-pass line 17 flows through energy-saving appliance refrigerant lines 9, and provides higher relatively fluid resistance to the cold-producing medium stream that flows through energy-saving appliance refrigerant lines 9 along the flow path direction that enters the port 25 that leads to compression set 22 intergrades from energy-saving appliance 30.
The present invention can be used for flash tank type energy conserving system equally.In this system, the stream that the control of by-pass and energy-saving appliance vapor stream is flow through the cold-producing medium economizer line by control is realized in a similar manner.In such embodiments, the flash tank energy-saving appliance is arranged in the main refrigerant circuit, is positioned at the downstream of cold-producing medium heat rejection heat exchanger with respect to cold-producing medium stream, and is positioned at the upstream of main expansion gear with respect to cold-producing medium stream.The energy-saving appliance refrigerant lines is communicated with the intermediate pressure stage that extends to compression set from the flash tank energy-saving appliance with refrigerant vapour stream, and economizer expansion device is arranged in the main refrigerant circuit, is positioned at the upstream of flash tank energy-saving appliance with respect to cold-producing medium stream.
Although partly show with reference to accompanying drawing example shown embodiment and described the present invention, it will be understood to those of skill in the art that not break away from the spirit and scope of the present invention that claim limits and make various details and change.For example, the check-valves 40 of Fig. 2 embodiment can be with respect to the shell of compression set 22 and is placed on outside or inside.Also have, check-valves 40 is replaceable be the magnetic valve that will be controlled by controller 80.
Claims (21)
1. refrigerant vapor compression system comprises:
Main refrigerant circuit, it comprises compressing apparatus of refrigerant, cold-producing medium heat rejection heat exchanger, cold-producing medium endothermic heat exchanger and main expansion gear, described main expansion gear is arranged in the described main refrigerant circuit, is in the downstream of described cold-producing medium heat rejection heat exchanger and is in the upstream of described cold-producing medium endothermic heat exchanger;
Energy-saving device circuit comprises energy-saving appliance and energy-saving appliance refrigerant lines, and described energy-saving appliance refrigerant lines constitutes refrigerant vapour stream and is communicated with between the intermediate pressure stage of described energy-saving appliance and described compression set;
By-pass line, it is in the described energy-saving appliance refrigerant lines that is in position between described energy-saving appliance and the described compression set intergrade and be in respect to cold-producing medium stream and constitute cold-producing medium stream between the described main refrigerant circuit of described cold-producing medium endothermic heat exchanger downstream position and be communicated with;
The by-pass control device, it is arranged in the described by-pass line, described by-pass control device has first enable possition and second closed position, can flow through described by-pass line at the first open position cold-producing medium, and cold-producing medium is prevented from flowing through described by-pass line at place, second closed position; And
Flow control device, it is arranged in the described energy-saving appliance refrigerant lines, have first stream and second stream, the first direction of described first-class curb from the described intermediate pressure stage of described compression set to described by-pass line passes described energy-saving appliance refrigerant lines, described second stream passes the energy-saving appliance refrigerant lines along the second direction that enters the described intermediate pressure stage of described compression set from described energy-saving appliance, the cold-producing medium stream that described first stream is crossed in the described first stream convection current has the first fluid resistance, described second stream has second fluid resistance to the cold-producing medium stream that flows through described second stream, the described first and second fluid resistance differences.
2. refrigerant vapor compression system according to claim 1 is characterized in that, described by-pass control device comprises the magnetic valve with first enable possition and second closed position.
3. refrigerant vapor compression system according to claim 1, it is characterized in that, described flow control device comprises the fluid diode apparatus, described fluid diode apparatus is arranged in the described energy-saving appliance refrigerant lines, be in the position between the described intermediate pressure stage of described by-pass line and described compression set, described fluid diode apparatus is provided with first stream and second stream, the first direction of described first-class curb from the intermediate pressure stage of described compression set to described by-pass line passes described energy-saving appliance refrigerant lines, the described first stream convection current has relatively low first fluid resistance through cold-producing medium stream wherein, described second stream passes described energy-saving appliance refrigerant lines along the second direction that enters the intermediate pressure stage of described compression set from described energy-saving appliance, and described second stream has the second higher relatively fluid resistance to the cold-producing medium stream of flowing through wherein.
4. refrigerant vapor compression system according to claim 3, it is characterized in that, described fluid diode apparatus comprises check-valves, described check-valves is arranged in the described energy-saving appliance refrigerant lines, be in the intermediate pressure stage of described compression set and the position between the described by-pass line, described check-valves has the primary importance and the second place, the first direction that can pass described first stream at primary importance place cold-producing medium along intermediate pressure stage to the described by-pass line from described compression set flows through described check-valves, can flow through described energy-saving appliance refrigerant lines along the second direction that enters the intermediate pressure stage of described compression set from described energy-saving appliance at second place place cold-producing medium and flow through described check-valves along second direction.
5. refrigerant vapor compression system according to claim 1, it is characterized in that, described flow control device comprises the first branched-refrigerant pipeline, second branched-refrigerant pipeline and the check-valves, the described first branched-refrigerant pipeline constitutes cold-producing medium stream with described first stream that passes described energy-saving appliance refrigerant lines and is communicated with, the described second branched-refrigerant pipeline and described second stream that passes described energy-saving appliance refrigerant lines constitute cold-producing medium stream and are communicated with and are arranged to be parallel to the described first branched-refrigerant pipeline, described check-valves is arranged in the described first branched-refrigerant pipeline, described check-valves has the primary importance and the second place, can flow through described first branched-refrigerant pipeline and described first stream at primary importance place cold-producing medium, flow through the described first branched-refrigerant pipeline at second place place cold-producing medium, and described first stream is blocked.
6. refrigerant vapor compression system according to claim 5, it is characterized in that, the described first branched-refrigerant pipeline has relatively low fluid resistance to the cold-producing medium stream of flowing through wherein, and the described second branched-refrigerant pipeline has higher relatively fluid resistance to the cold-producing medium stream of flowing through wherein.
7. refrigerant vapor compression system according to claim 5 further comprises the fixed restriction control device, and described fixed restriction control device is arranged in the described second branched-refrigerant pipeline.
8. refrigerant vapor compression system according to claim 7, it is characterized in that, the described check-valves that is in primary importance provides relatively low fluid resistance to the cold-producing medium stream of the described first branched-refrigerant pipeline of flowing through, and described fixed restriction control device provides higher relatively fluid resistance to the cold-producing medium stream of the described second branched-refrigerant pipeline of flowing through.
9. refrigerant vapor compression system according to claim 1, it is characterized in that, described flow control device comprises the first branched-refrigerant pipeline, second branched-refrigerant pipeline and the magnetic valve, the described first branched-refrigerant pipeline constitutes cold-producing medium stream with described first stream that passes described energy-saving appliance refrigerant lines and is communicated with, the described second branched-refrigerant pipeline and described second stream that passes described energy-saving appliance refrigerant lines constitute cold-producing medium stream and are communicated with and are arranged to be parallel to the described first branched-refrigerant pipeline, magnetic valve is arranged in the described first branched-refrigerant pipeline, described magnetic valve has the primary importance and the second place, can flow through the described first branched-refrigerant pipeline at primary importance place cold-producing medium, at second place place, the cold-producing medium stream that flows through the described first branched-refrigerant pipeline is blocked, and cold-producing medium only can flow through the described second branched-refrigerant pipeline.
10. refrigerant vapor compression system according to claim 9 further comprises the fixed restriction control device, and described fixed restriction control device is arranged in the described second branched-refrigerant pipeline.
11. refrigerant vapor compression system according to claim 1 is characterized in that, described energy-saving appliance comprises cold-producing medium-refrigerant heat exchanger.
12. refrigerant vapor compression system according to claim 1, it is characterized in that, described cold-producing medium-refrigerant heat exchanger comprises first coolant channel and second coolant channel, second refrigerant pass arrangement becomes with described first coolant channel to constitute heat exchange relationship, described first refrigerant pass arrangement is in described main refrigerant circuit, described second refrigerant pass arrangement is in described energy-saving appliance refrigerant lines, and described energy-saving appliance refrigerant lines becomes to flow and passes the intermediate pressure stage that described second coolant channel extends to described compression set from described main refrigerant circuit communicatively.
13. refrigerant vapor compression system according to claim 12, further comprise economizer expansion device, economizer expansion device is arranged in the described energy-saving appliance refrigerant lines, is positioned at the upstream of second coolant channel of described cold-producing medium-refrigerant heat exchanger with respect to cold-producing medium stream.
14. refrigerant vapor compression system according to claim 13 is characterized in that, described economizer expansion device comprises and is selected from following group expansion gear: electric expansion valve, heating power expansion valve and fixed orifice throttling arrangement.
15. refrigerant vapor compression system according to claim 1, it is characterized in that, described economizer heat exchanger is a flash tank, described flash tank is arranged in the described main refrigerant circuit, is positioned at the downstream of described cold-producing medium heat rejection heat exchanger and is positioned at the upstream of described main expansion gear with respect to cold-producing medium stream with respect to cold-producing medium stream.
16. refrigerant vapor compression system according to claim 15 further comprises economizer expansion device, described economizer expansion device is arranged in the described main refrigerant circuit, is positioned at the upstream of described flash tank with respect to cold-producing medium stream.
17. refrigerant vapor compression system according to claim 16 is characterized in that, described economizer expansion device comprises and is selected from following group expansion gear: electric expansion valve, heating power expansion valve and fixed orifice throttling arrangement.
18. refrigerant vapor compression system according to claim 1 is characterized in that, described main expansion gear comprises and is selected from following group expansion gear: electric expansion valve, heating power expansion valve and fixed orifice throttling arrangement.
19. refrigerant vapor compression system according to claim 1 is characterized in that, described compression set comprises the single compressor with at least two compression stages.
20. refrigerant vapor compression system according to claim 1 is characterized in that, described compression set comprises at least two compressors, and described at least two compressors are arranged in the described main refrigerant circuit and constitute series relationship with respect to cold-producing medium stream.
21. refrigerant vapor compression system according to claim 1, it is characterized in that described compression set comprises at least one compressor that is selected from following compressor bank: scroll compressor, reciprocating compressor, screw compressor, centrifugal compressor and rotary compressor.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/US2007/011797 WO2008143611A1 (en) | 2007-05-17 | 2007-05-17 | Economized refrigerant system with flow control |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101755177A true CN101755177A (en) | 2010-06-23 |
Family
ID=40032179
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200780053820A Pending CN101755177A (en) | 2007-05-17 | 2007-05-17 | Economized refrigerant system with flow control |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US20100251750A1 (en) |
| CN (1) | CN101755177A (en) |
| WO (1) | WO2008143611A1 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103322717A (en) * | 2013-06-17 | 2013-09-25 | 江苏科立德制冷设备有限公司 | Low-temperature vortex parallel compression condensing unit with enhanced vapor injection |
| CN103673145A (en) * | 2012-09-05 | 2014-03-26 | 苏州必信空调有限公司 | Compact type water chilling unit and air conditioning system of high-rise building |
| CN104896813A (en) * | 2015-06-29 | 2015-09-09 | 广东美的暖通设备有限公司 | Air conditioner online system |
| CN107429952A (en) * | 2014-12-11 | 2017-12-01 | 安吉拉通力测试技术有限公司简称Att有限公司 | Refrigeration plant |
| CN112730277A (en) * | 2019-10-28 | 2021-04-30 | 佳能医疗系统株式会社 | Automatic analyzer and reagent library thereof |
| CN115038869A (en) * | 2020-01-10 | 2022-09-09 | 江森自控泰科知识产权控股有限责任合伙公司 | Economizer control system and method |
Families Citing this family (29)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US10107536B2 (en) | 2009-12-18 | 2018-10-23 | Carrier Corporation | Transport refrigeration system and methods for same to address dynamic conditions |
| JP2012137207A (en) * | 2010-12-24 | 2012-07-19 | Mitsubishi Electric Corp | Refrigerating cycle apparatus |
| JP2012233676A (en) * | 2011-04-21 | 2012-11-29 | Denso Corp | Heat pump cycle |
| JP5708421B2 (en) * | 2011-09-30 | 2015-04-30 | ダイキン工業株式会社 | Refrigeration equipment |
| DE102012102163A1 (en) * | 2012-03-14 | 2013-09-19 | Kist Europe-Korea Institute of Science and Technologie Europe Forschungsgesellschaft mbh | System and method for superheating and / or supercooling of liquids and use of the system and / or method |
| KR20140022619A (en) * | 2012-08-14 | 2014-02-25 | 삼성전자주식회사 | Air conditioner and thereof control process |
| JP5819006B2 (en) * | 2012-10-22 | 2015-11-18 | 三菱電機株式会社 | Refrigeration equipment |
| JP6005255B2 (en) * | 2013-03-12 | 2016-10-12 | 三菱電機株式会社 | Air conditioner |
| US10168068B2 (en) | 2013-03-12 | 2019-01-01 | Mitsubishi Electric Corporation | Air-conditioning apparatus |
| ITVI20130257A1 (en) * | 2013-10-18 | 2015-04-19 | Carel Ind Spa | METHOD OF DRIVING A REFRIGERATED MACHINE EQUIPPED WITH AN ECONOMISER SYSTEM |
| WO2015105845A1 (en) | 2014-01-08 | 2015-07-16 | Carrier Corporation | Adaptive control of multi-compartment transport refrigeration system |
| US10119738B2 (en) | 2014-09-26 | 2018-11-06 | Waterfurnace International Inc. | Air conditioning system with vapor injection compressor |
| KR101702736B1 (en) * | 2015-01-12 | 2017-02-03 | 엘지전자 주식회사 | An air conditioner |
| CN106766441A (en) | 2015-11-25 | 2017-05-31 | 开利公司 | Refrigeration system and its throttling control method |
| US10539350B2 (en) | 2016-02-26 | 2020-01-21 | Daikin Applied Americas Inc. | Economizer used in chiller system |
| US10871314B2 (en) | 2016-07-08 | 2020-12-22 | Climate Master, Inc. | Heat pump and water heater |
| US10724546B2 (en) | 2016-08-05 | 2020-07-28 | Daikin Applied Americas Inc. | Centrifugal compressor having a casing with an adjustable clearance and connections for a variable flow rate cooling medium, impeller clearance control apparatus for centrifugal compressor, and impeller clearance control method for centrifugal compressor |
| US20180073779A1 (en) | 2016-09-15 | 2018-03-15 | Daikin Applied Americas Inc. | Centrifugal compressor |
| US10866002B2 (en) | 2016-11-09 | 2020-12-15 | Climate Master, Inc. | Hybrid heat pump with improved dehumidification |
| US11535425B2 (en) | 2016-11-22 | 2022-12-27 | Dometic Sweden Ab | Cooler |
| USD933449S1 (en) | 2016-11-22 | 2021-10-19 | Dometic Sweden Ab | Latch |
| CN108662799A (en) | 2017-03-31 | 2018-10-16 | 开利公司 | Multistage refrigerating plant and its control method |
| USD836993S1 (en) | 2017-05-17 | 2019-01-01 | Dometic Sweden Ab | Cooler |
| USD836994S1 (en) | 2017-05-17 | 2019-01-01 | Dometic Sweden Ab | Cooler |
| EP3635304B1 (en) | 2017-06-08 | 2022-03-23 | Carrier Corporation | Method of control for economizer of transport refrigeration units |
| US10935260B2 (en) | 2017-12-12 | 2021-03-02 | Climate Master, Inc. | Heat pump with dehumidification |
| US11592215B2 (en) | 2018-08-29 | 2023-02-28 | Waterfurnace International, Inc. | Integrated demand water heating using a capacity modulated heat pump with desuperheater |
| CA3081986A1 (en) | 2019-07-15 | 2021-01-15 | Climate Master, Inc. | Air conditioning system with capacity control and controlled hot water generation |
| CA3221677A1 (en) * | 2021-06-16 | 2022-12-22 | Todd M. Bandhauer | Air source heat pump system and method of use for industrial steam generation |
Family Cites Families (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4144717A (en) * | 1977-08-29 | 1979-03-20 | Carrier Corporation | Dual flash economizer refrigeration system |
| US4141708A (en) * | 1977-08-29 | 1979-02-27 | Carrier Corporation | Dual flash and thermal economized refrigeration system |
| US4207749A (en) * | 1977-08-29 | 1980-06-17 | Carrier Corporation | Thermal economized refrigeration system |
| US5431026A (en) * | 1994-03-03 | 1995-07-11 | General Electric Company | Refrigerant flow rate control based on liquid level in dual evaporator two-stage refrigeration cycles |
| US5553457A (en) * | 1994-09-29 | 1996-09-10 | Reznikov; Lev | Cooling device |
| JP2000046420A (en) * | 1998-07-31 | 2000-02-18 | Zexel Corp | Refrigeration cycle |
| US6202438B1 (en) * | 1999-11-23 | 2001-03-20 | Scroll Technologies | Compressor economizer circuit with check valve |
| US6276148B1 (en) * | 2000-02-16 | 2001-08-21 | David N. Shaw | Boosted air source heat pump |
| US6385980B1 (en) * | 2000-11-15 | 2002-05-14 | Carrier Corporation | High pressure regulation in economized vapor compression cycles |
| US6718781B2 (en) * | 2001-07-11 | 2004-04-13 | Thermo King Corporation | Refrigeration unit apparatus and method |
| KR100437805B1 (en) * | 2002-06-12 | 2004-06-30 | 엘지전자 주식회사 | Multi-type air conditioner for cooling/heating the same time and method for controlling the same |
| US6658867B1 (en) * | 2002-07-12 | 2003-12-09 | Carrier Corporation | Performance enhancement of vapor compression system |
| US6938438B2 (en) * | 2003-04-21 | 2005-09-06 | Carrier Corporation | Vapor compression system with bypass/economizer circuits |
| US7000423B2 (en) * | 2003-10-24 | 2006-02-21 | Carrier Corporation | Dual economizer heat exchangers for heat pump |
| US6883341B1 (en) * | 2003-11-10 | 2005-04-26 | Carrier Corporation | Compressor with unloader valve between economizer line and evaporator inlet |
| US6955058B2 (en) * | 2004-01-30 | 2005-10-18 | Carrier Corporation | Refrigerant cycle with tandem economized and conventional compressors |
| US7137270B2 (en) * | 2004-07-14 | 2006-11-21 | Carrier Corporation | Flash tank for heat pump in heating and cooling modes of operation |
| US7325411B2 (en) * | 2004-08-20 | 2008-02-05 | Carrier Corporation | Compressor loading control |
| US7114349B2 (en) * | 2004-12-10 | 2006-10-03 | Carrier Corporation | Refrigerant system with common economizer and liquid-suction heat exchanger |
| DK2147264T3 (en) * | 2007-04-24 | 2019-03-04 | Carrier Corp | Refrigerant vapor compression system |
-
2007
- 2007-05-17 CN CN200780053820A patent/CN101755177A/en active Pending
- 2007-05-17 US US12/599,888 patent/US20100251750A1/en not_active Abandoned
- 2007-05-17 WO PCT/US2007/011797 patent/WO2008143611A1/en active Application Filing
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103673145A (en) * | 2012-09-05 | 2014-03-26 | 苏州必信空调有限公司 | Compact type water chilling unit and air conditioning system of high-rise building |
| CN103673145B (en) * | 2012-09-05 | 2016-03-23 | 苏州必信空调有限公司 | The air-conditioning system of compact handpiece Water Chilling Units and skyscraper |
| CN103322717A (en) * | 2013-06-17 | 2013-09-25 | 江苏科立德制冷设备有限公司 | Low-temperature vortex parallel compression condensing unit with enhanced vapor injection |
| CN107429952A (en) * | 2014-12-11 | 2017-12-01 | 安吉拉通力测试技术有限公司简称Att有限公司 | Refrigeration plant |
| CN104896813A (en) * | 2015-06-29 | 2015-09-09 | 广东美的暖通设备有限公司 | Air conditioner online system |
| CN112730277A (en) * | 2019-10-28 | 2021-04-30 | 佳能医疗系统株式会社 | Automatic analyzer and reagent library thereof |
| CN115038869A (en) * | 2020-01-10 | 2022-09-09 | 江森自控泰科知识产权控股有限责任合伙公司 | Economizer control system and method |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2008143611A1 (en) | 2008-11-27 |
| US20100251750A1 (en) | 2010-10-07 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101755177A (en) | Economized refrigerant system with flow control | |
| US7997092B2 (en) | Refrigerant vapor compression system operating at or near zero load | |
| CN101946137B (en) | Refrigerant vapor compression system | |
| CN101568776B (en) | Economized refrigeration cycle with expander | |
| CN101688698B (en) | Refrigerant vapor compression system with flash tank economizer | |
| CN101688725B (en) | Transcritical refrigerant vapor compression system with charge management | |
| CN102388279B (en) | Refrigerant vapor compression system with hot gas bypass | |
| EP2147264B1 (en) | Refrigerant vapor compression system | |
| CN105228842B (en) | Refrigerant vapor compression system and the cold storage container used in transporting perishable items | |
| CN105008820B (en) | Air-conditioning device | |
| US20140150489A1 (en) | Startup Logic For Refrigeration System | |
| AU2004237783A2 (en) | Heat pump and heat pump system | |
| CN108131860B (en) | Ultralow temperature air source heat pump based on single-machine double-stage compressor | |
| CN107816818A (en) | A kind of folding type cooling system of freezer with hot gas defrosting | |
| CN100507401C (en) | Capacity adjustable vortex compressor refrigeration system with mediate loop installed with ejector | |
| CN101907371B (en) | Air-condition freezing and refrigeration system device | |
| CN1321298C (en) | Refrigerating machine | |
| CN201724461U (en) | Refrigeration and cold storage system device for air conditioner | |
| WO2018051409A1 (en) | Refrigeration cycle apparatus | |
| JP2021529923A (en) | Refrigerant vapor compression system | |
| US20230160610A1 (en) | Heat Pump with Ejector | |
| WO2019189748A1 (en) | Refrigeration device | |
| CN115597247A (en) | Air energy heating system and heating method thereof | |
| CN118328573A (en) | Ultralow temperature refrigeration system and control method thereof |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| REG | Reference to a national code |
Ref country code: HK Ref legal event code: DE Ref document number: 1144836 Country of ref document: HK |
|
| C12 | Rejection of a patent application after its publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20100623 |
|
| REG | Reference to a national code |
Ref country code: HK Ref legal event code: WD Ref document number: 1144836 Country of ref document: HK |