CN1839286A - Multizone air-conditioning system with a single frequency compressor - Google Patents

Multizone air-conditioning system with a single frequency compressor Download PDF

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Publication number
CN1839286A
CN1839286A CNA2004800238245A CN200480023824A CN1839286A CN 1839286 A CN1839286 A CN 1839286A CN A2004800238245 A CNA2004800238245 A CN A2004800238245A CN 200480023824 A CN200480023824 A CN 200480023824A CN 1839286 A CN1839286 A CN 1839286A
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China
Prior art keywords
cold
producing medium
bypass
heat exchanger
compressor
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Chinese (zh)
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凯奥尔浩·拜
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Vortex Aircon Inc
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Vortex Aircon Inc
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Publication of CN1839286A publication Critical patent/CN1839286A/en
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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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/04—Desuperheaters
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/22—Disposition of valves, e.g. of on-off valves or flow control valves between evaporator and compressor
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

A variable capacity refrigeration system employing a constant speed compressor that operates continuously irrespective of heat load, and a refrigerant bypass path including a secondary expansion device, two heat exchangers, a pressure differential accomodation device, and a flow control device to divert a portion of the refrigerant exiting the condenser to the bypass path. One heat exchanger is connected so that the refrigerant exiting the condenser passes through a first flow path. At the exit of the first flow path, a portion of the refrigerant is diverted through a secondary expansion device to the bypass path which then passes through a second flow path of the first heat exchanger, whereby the first heat exchanger provides subcooling of the refrigerant exiting the condenser. Refrigerant exiting the compressor passes through a first flow path of the second heat exchanger. The refrigerant exiting the second flow path of the first heat exchanger passes through a second flow path of the second heat exchanger, and then returns to the compressor inlet. The second heat exchanger therefore provides desuperheating of the refrigerant in the primary refrigerant loop.

Description

The multiple domain air-conditioning system that has the single-frequency compressor
The cross reference of priority
It is the priority of the U.S. Provisional Application 60/426,073 on November 11st, 2002 that the application requires the applying date.
Technical field
What present invention relates in general to is the multiple domain air-conditioning system, The present invention be more particularly directed to a kind ofly adopt the single-frequency compressor but be used for the air-conditioning system of variable thermic load.
Background technology
Fig. 1 is conventional refrigeration system 10.This system comprises a compressor 12, condenser 14, a bloating plant 16 and an evaporimeter 18.Thereby each parts couple together by copper pipe 20 and form a closed-loop path, and cold-producing medium such as R12, R22, R134a, R407c, R410a, ammonia, carbon dioxide or natural gas circulate.
This kind of refrigeration cycle mainly comprises following a few step: compressor 12 compressed refrigerants, condenser 14 are discharged into environment with heat from cold-producing medium, and cold-producing medium throttling and cold-producing medium in bloating plant 16 absorb the heat of institute's cooling space in evaporimeter 18.This process, it is called as Vapor Compression Refrigeration Cycle sometimes, be used in make in the living space or means of transport (as automobile, aircraft, train etc.) in air cooling and the air-conditioning system of drying in, in the refrigerator and in the heat pump.
Figure 2 shows that the tephigram of Vapor Compression Refrigeration Cycle among Fig. 1.Wherein cold-producing medium is the superheated vapor (point 1) under the evaporating pressure when leaving evaporimeter 18, is compressed to high pressure by compressor 12 then.The temperature of cold-producing medium is the superheated vapor (point 2) under the condensing pressure when it leaves compressor also along with rising in the compression process.
Common condenser is bent to form parallel spaced apart from each otherly multi coil road by a pipe.Usually be connected with mental-finned or other structure on this bending pipeline and reach maximum with heat exchange between the cold-producing medium that provides heat transfer property to make to flow through condenser and the surrounding air.When of the upstream portion heat release of overheated cold-producing medium at condenser, superheated vapor meeting (at a 2a) becomes saturated vapor, flows through all the other pipelines of condenser 14 then along with it, the further heat release of this cold-producing medium meeting, when cold-producing medium left condenser 14, it was subcooled liquid (point 3).
When having served as cold liquid refrigerant passes through expansion device 16, its pressure descends, and becomes a kind of gas-liquid mixture of approximately being made up of 20% gas and 80% liquid.Also have, when it flows through bloating plant (point 4 among Fig. 2), its temperature drops under the ambient air temperature.
Evaporimeter 18 structurally with the bending pipeline of condenser the spitting image of.Thereby cooled air is exposed to the surface of evaporimeter heat is delivered in the cold-producing medium.When cold-producing medium absorbed heat in evaporimeter 18 after, it can become the superheated vapor under the compressor air suction pressure, and (point 1 place in Fig. 2) thus enter again and finish kind of refrigeration cycle in the compressor.
In the design of air-conditioning or refrigeration system and operation a problem being arranged is that thermic load changes along with the variation of time.This is comprising two kinds of variations.The first, thermic load changes along with the variation of outdoor weather environment.Change for this thermic load, it is that the switch refrigeration system gets final product as required that a kind of processing method is arranged.The lot of energy loss reduced operating efficiency greatly when this system can be because of compressor start when frequent switch.The second, owing to do not need whole house is cooled off, therefore the thermic load of this moment is very low during night.Required cold will be significantly less than the required cold in whole house when the bedroom, and thermic load can reduce more than 60% usually.In other words, in order to raise the efficiency, refrigerating capacity should reduce 60-70%.
For fear of switching manipulation continually, it is to use frequency-changeable compressor as shown in Figure 3 that a kind of method is arranged.The system of the 10A of this system and Fig. 1 is basic identical, and its main difference is that compressor 12A is a variable speed compressor.Be different from compressor 12A and circulate between Push And Release, the frequency of this compressor can change according to required thermic load.Yet frequency-changeable compressor can not solve second above-mentioned problem, because it can not handle the situation of thermic load decline 60-70%.
Figure 4 and 5 are depicted as heat and the relation curve of frequency and the relation curve of EER (Energy Efficiency Ratio) and frequency that evaporimeter absorbs.(those skilled in the art know that EER is a refrigerating capacity and the ratio of compressor power consumption.) as can be seen from Figure 4, the advantage of frequency conversion class compressor be when frequency when 60Hz brings up to 80Hz, refrigerating capacity can improve 17%.Yet, when frequency when 60Hz drops to 30Hz, refrigerating capacity descends 40%.This performance is very good with respect to the variation of thermic load.
Yet bring extra 17% refrigerating capacity that cost is arranged when 80Hz: its efficient is subjected to severe impairment.As shown in Figure 5, when frequency when 60Hz brings up to 80Hz, EER descends 18%.In addition, the cost of frequency-changeable compressor can account for 1/3rd of whole air-conditioning system or refrigeration system usually, and this point is very high as room conditioning for many application scenarios.
Also have, frequency-changeable compressor can not be worked under very low frequency, therefore can't make refrigerating capacity decline 60-70%.Therefore, need a kind of method here, it can avoid solving the time dependent problem of thermic load under the situation of the cost problem of frequency conversion compression and other shortcoming.
Figure 6 shows that a kind of air-conditioning system 10B that becomes crack screw compressor 12B that adopted.Those skilled in the art are clear, and compressor 12B has adopted two complete concentric scrolls, and one of them is inserted in another the inside.A scroll is static, and another then curls up its rotation.The motion of this scroll was pressed the formed little space that constantly diminishes of scroll rotation with gas, reached maximum pressure up to this gas at the center of compression chamber, the exhaust outlet discharge of this Compressed Gas from fixing scroll then.
In order to reduce the refrigerating capacity of air-conditioning system 10B, the load of compressor is reduced along with the reduction of refrigerating capacity thereby static scroll departs from the scroll that curls up slightly.Yet the cost of this compressor is a limiting factor: the cost of space-changeable type screw compressor is much higher than single-frequency compressor (near four times).Therefore, the space-changeable type screw compressor changes the refrigerating capacity of air-conditioning system unsatisfactorily.
In addition, Hwang, Choe, Kim and Chung go up in the Purdue compressor engineering of the West Lafayette IN2002 of Purdue university and refrigeration and air-conditioning conference (Purdue CompressorEngineering and Refrigeration and Air Conditioning Conference) and proposed a kind of high efficiency air conditioner that has two different capabilities compressors in The Development of High Efficiency Air Condition with TwoCompressor of Different Capacities.This double compressor system can be referring to the 10C among Fig. 7.
System 10C is different from system 10,10A and 10B, because the 10C of system adopts two compressor 12C-1 and 12C-2 and two check-valves 13C-3 and 13C-2.Compressor 12C-1 is the high power capacity compressor, and compressor 12C-2 is the low capacity compressor.Two compressors move together to satisfy the needs of whole refrigeration duty.When night, refrigeration duty obviously descended, big compressor 12C-1 is turned off, only keep little compressor 12C-2 and work on.
The problem of this method is that oil content is joined inequality.For the inequality that prevents that oil content is joined between two compressors, need one shared 15.Another shortcoming of system 10C has been to use two compressors to add two check-valves, therefore compares the cost of the air-conditioning system that heightened (being twice at least) with single compressor system.
U.S. Pat 6662576 on December 16th, 2003, that name is called " Refrigeration System WithDe-Superheating Bypass " discloses a kind of compartmentalization air-conditioning system, the document is incorporated the application into here by reference in full, has the Reference numeral 90 referring to Fig. 8.
Refrigeration system 90 comprises a main refrigerating circuit 91 and a refrigerant bypassing 92.Major loop 91 comprises compressor 12, condenser 14, main bloating plant 16 and multizone evaporator sub-system 96, and all these parts all are parts routine or required type that those skilled in the art will know that.Flow control valve 100a and 100b that evaporator sub-system 96 comprises the evaporation element of a plurality of parallel connections and links with it respectively, two evaporation elements shown in it are respectively 98a and 98b, it is arranged in the space of being cooled off as required, and these two evaporation elements link to each other with main bloating plant 16 by flow control valve.These parts equally also are parts conventional or required type.
Bypass 92 comprises one second bloating plant 94 and a heat exchanger 97, the former is connected to the outlet of condenser 14 by an adjustable throttle control valve 95, the latter has one first stream and one second stream, wherein first stream links to each other the outlet of compressor 12 with the inlet of condenser 14, and second stream then is connected to the outlet of second bloating plant 94.Pressure reduction conditioning equipment (PDAD) 38 is used for making the cold-producing medium of major loop 91 and bypass 92 to turn back to compressor 12 together.Use pressure reduction conditioning equipment 38 to be because the cold-producing medium in the bypass 92 at the pressure of heat exchanger 97 outlets pressure greater than evaporator unit 98a and the shared outlet of 98b 104 places.
PDAD 38 or be the vortex generator of a vacuum generating equipment shown in United States Patent (USP) 6250086, the document is incorporated the application in full with the form of reference here, be other any required or suitable equipment such as Venturi tube of utilizing physical dimension and fluid dynamic to form vacuum, it can make steam mix before turning back to the suction port of compressor and reach pressure balance.Also can adopt pressure drop equipment such as capillary, metering hole, valve or porous plug as selecting.Obviously, no matter adopt the PDAD of which kind of type, it all can make pressure of cold-producing medium stream of bypass outlet descend and be complementary with the pressure of evaporator outlet.
In operation, when needs cooled off two zones, valve 100a and 100b all opened, and cold-producing medium flows through two evaporator unit 98a and 98b.Thereby thereby refrigerating capacity and the highest efficient that reaches maximum in the bypass 92 assigned to 10% to 15% cold-producing medium in the condenser 14 by control valve 95.
Another feature of system 90 is, if only need the employed zone of evaporator unit 98a is cooled off, so valve 100a is opened, 100b closes with valve, thereby this moment, control valve 95 was diverted to cold-producing medium and those cold-producing mediums that are used for desuperheat that those will flow through evaporimeter 98b originally in the bypass 92.In order to change the mass flow of cold-producing medium in the bypass, thus can be continuously or the valve in the adjusted stepwise bypass 92 95 cold-producing medium of required different flow is provided.For example, shunt 10% o'clock cold-producing medium maximum, shunting 20%, 30% and 40% o'clock refrigerating capacity reduce successively.
Submitted to November 12, application number be PCT/US03/36424, name is called among the PCT application WO2004/044503 of " Refrigeration System With Bypass Subcooling and Component SizeOptimization " and discloses another kind of compartmentalization air-conditioning system, referring to 110 among Fig. 9, this application is incorporated the application in full with the form of reference here.Native system is similar to the system 90 among Fig. 8, and it is different from the configuration difference of bypass 92A wherein.
More particularly, but adjusting control valve 95A is arranged in the downstream of first stream that passes heat exchanger 97A, and the second bloating plant 94A directly links to each other the outlet of condenser 24 with the inlet of heat exchanger 97A first stream.Second stream of heat exchanger 97A is arranged between the inlet of the outlet of condenser 24 and bloating plant 16, rather than between compressor and condenser.
In operating process, if be used for cooling off dwelling house, when maximum cooling capacity appears at daytime whole room is cooled off so such as Fig. 8 and multizone air-conditioning system shown in Figure 9.At night, refrigerating capacity reduces along with the increase in the room that need not cool off in the whole house, has only this moment the bedroom to need less cold.Therefore, as previously mentioned, can make refrigeration duty reduce 60-70% with respect to the maximum cold load like this, the mass flow of bypass should be at 60-70%.
The method of above-mentioned bypass can not solve so high bypass flow, because all liquid refrigerants that do not have enough heats to evaporate here to flow through in the bypass.And cold-producing medium must be gasified totally before entering compressor flowing through bypass, this be because if the end of bypass a little drop all can cause the damage of compressor.Although above-mentioned these systems are the known best system that variable refrigerating capacity can be provided in multizone system, they still can not so many liquid refrigerants.Therefore, still need a method and apparatus here, it can avoid liquid refrigerant to enter a large amount of cold-producing medium (60-70% of total mass flow rate) of bypass under the condition of compressor.
Summary of the invention
One object of the present invention is to provide a kind of improved, multizone air-conditioning system that refrigerating capacity is variable.
Another object of the present invention provides air-conditioning system a kind of multizone, that refrigerating capacity is variable, and it adopts a single-frequency compressor, and no matter how all runnings continuously of this compressor of required refrigerating capacity.
Another object of the present invention provides a kind of air-conditioning system that adopts conventional single speed compressor, this air-conditioning system can provide available technology adopting frequency-changeable compressor, become the variable refrigerating capacity that the air-conditioning system of crack screw compressor or a plurality of compressors just can provide, avoided the shortcoming of existing system simultaneously again.
The purpose that the present invention is more general provides a kind of air-conditioning system, and it adopts the single speed compressor of a routine, and no matter how all runnings continuously of this compressor of refrigeration duty.
A general objects of the present invention provides the variable refrigeration system of a kind of refrigerating capacity, and it does not rely on expensive frequency-changeable compressor or becomes crack screw compressor or a plurality of compressor.
Another object of the present invention provides the air-conditioning system of varying capacity, and it comprises a refrigerant bypassing, and this bypass can realize the cold-peace cooling selectively.
Another object of the present invention provides a kind of method of operating air conditioning system, and air-conditioning system wherein has a single speed compressor, and this system can provide variable refrigerating capacity under the condition of the shortcoming of avoiding existing variable refrigerating capacity system; And
Another object of the present invention provides a kind of method of operating the multizone air-conditioning system, in this system, though single speed compressor running continuously can provide variable refrigerating capacity.
Above-mentioned purpose is realized that by air-conditioning system of the present invention this system has a main refrigerating circuit and a bypass, and bypass wherein comprises two heat exchangers, and one was used for coldly, and another is used for desuperheat.Principle of the present invention both had been applicable to single district system such as room air conditioner, was applicable to the multizone system of cooling large space again.
A first aspect of the present invention provides a kind of varying capacity refrigeration system, it has condensing unit, expansion gear, vaporising device and a compressing apparatus of refrigerant, when system starts, no matter how refrigeration duty changes, this compression set all continuously operates with fixed speed, and refrigerant bypassing comprises second expansion gear, first and second heat-exchange devices and volume control device.When refrigeration duty was lower than the threshold value of predetermined high refrigeration duty, volume control device made the part of refrigerant of leaving condensing unit flow through the bypass path to first and second heat-exchange devices, thereby made two heat-exchange devices as additional vaporising device.When refrigeration duty was not less than the limit value of predetermined high refrigeration duty, volume control device was used for preventing to leave the cold-producing medium of condensing unit by by-pass overcompression device.
A second aspect of the present invention provides a kind of varying capacity refrigeration system, it has a condenser, a bloating plant, an evaporimeter and a compressor, when system starts, no matter how refrigeration duty changes, this compressor all continuously operates with fixed speed, and refrigerant bypassing comprises one second bloating plant, first and second heat-exchange devices and a flow control appliance.When refrigeration duty is higher than the threshold value of predetermined high refrigeration duty,, flow-control equipment provides high refrigerating capacity to flowing of bypass thereby cutting off cold-producing medium in operation.
As selection, thereby whenever the cold-producing medium of minimum mass flow can both be assigned to the operating efficiency that improves system in the bypass.In the time of under refrigeration duty is fallen selected high refrigeration duty threshold value, the cold-producing medium in the bypass can increase gradually from minimum discharge.When system operates in this way,,, also there is the cold-producing medium of 5% to 15% mass flow to be diverted in the bypass even when maximum heating load as preferably.When refrigeration duty does not surpass selected threshold value, more cold-producing medium can be diverted in the bypass to reduce refrigerating capacity.
A third aspect of the present invention provides a kind of multizone system, and it has a main refrigerant circuit and a refrigerant bypassing; Wherein main refrigerant circuit adopts conventional design or designs as required, and it comprises the evaporator units that are arranged in parallel that spatially separate, a plurality of, and these evaporator units can be connected to the outlet of expansion valve selectively; Refrigerant bypassing wherein is used for making refrigerating capacity to reduce and realized the cold-peace desuperheat so that improve overall system efficiency, and guarantees that the cold-producing medium that flows through bypass was gasified totally before returning compressor.Can prevent that like this compressor from damaging because of the inflow of liquid refrigerant.
In a preferred embodiment, the part of refrigerant that condenser is come out is shunted away refrigerating capacity is reduced.The outlet of condenser is connected to the inlet of the first heat exchanger high temperature stream.In the outlet of this stream, there is a control valve that the cold-producing medium of required flow is diverted in the bypass, thereby and flows through second bloating plant thus and reduce its pressure and temperature.The outlet of second bloating plant links to each other with the inlet of the first heat exchanger low temperature stream.Thus formed heat transfer can make main refrigerant circuit further cold excessively.
The high temperature stream of second heat exchanger is connected between the inlet of the outlet of compressor and condenser, and the cold-producing medium that leaves the first heat exchanger low temperature stream simultaneously flows through the low temperature stream of second heat exchanger.Heat transfer in second heat exchanger just makes the temperature of main refrigerant circuit descend thus.Then, the cold-producing medium that leaves the second heat exchanger low temperature stream turns back to the inlet of compressor with the cold-producing medium that leaves evaporator system.Pass in the bypass total amount of heat of cold-producing medium and be enough to realize gasification completely.
Also have, when heat exchanger made refrigerating capacity reduce in operation, because liquid refrigerant does not have complete expansion in second bloating plant, so the refrigerant pressure in the heat exchanger can remain on one with respect on the higher pressure of pressure in the main evaporator.At this moment, an available pressure reduction conditioning equipment (PDAD) reduces the pressure of the cold-producing medium that leaves bypass.This PDAD can be a vacuum generator such as vortex generator, also a Venturi tube or a current limiter such as capillary.If system does not have pressure reduction between main evaporator and the heat exchanger when operation, just do not need PDAD.
As a distortion of the foregoing description, in second preferred embodiment of the present invention, the upstream extremity of bypass is furnished with a liquid trap.As the simplest a kind of form, this liquid trap can be used for forming an enlarged diameter in the connecting line of bypass part.
The cold-producing medium that circulates in system can be made of a kind of composition, as selection, and its also a kind of mixed type cold-producing medium, it comprises multiple composition, these compositions should be able to provide required thermal performance and flammable performance when selecting.
Also with reference to following explanation, other features and advantages of the present invention will be more readily apparent from conjunction with the accompanying drawings.
Description of drawings
Fig. 1 is the flow chart of conventional air-conditioning system.
Fig. 2 is the temperature entropy curve of conventional air-conditioning shown in Figure 1 system.
Fig. 3 is the flow chart that has the air-conditioning system of conventional frequency-changeable compressor.
Fig. 4 is the heat absorption of conventional frequency-changeable compressor and the performance curve between the frequency.
Fig. 5 is the EER of conventional frequency-changeable compressor and the performance curve between the frequency.
Fig. 6 is the flow chart that has the air-conditioning system that becomes the crack screw compressor.
Fig. 7 is the flow chart of an air-conditioning system, and this system has two compressors and two check-valves, and a shared liquid trap.
Fig. 8 is the flow chart of a subregion cooling system when adding bypass.
Fig. 9 is the another kind of flow chart of a subregion cooling system when adding bypass.
Figure 10 is applied to the flow chart of subregion cooling system for the present invention, and it has used two heat exchangers in bypass.
Figure 11 is applied to the flow chart of multizone cooling system for the present invention, its with a part of bypass as embedded liquid trap.
In all accompanying drawings, identical parts adopt identical Reference numeral.
Preferred embodiment
Figure 10 shows that the first embodiment of the present invention 130, it has used two heat exchangers in bypass.Similar to system 90 shown in Figure 8, system's 130 main refrigerating circuit 132 and refrigerant bypassings 133.Major loop 132 comprises a compressor 134, a condenser 136, one main bloating plant 138 and a multizone evaporator sub-system 140, and all these parts all can adopt type this area routine or required.The cold-producing medium that circulates in system can be made of a kind of composition, as selection, and its also a kind of mixed type cold-producing medium, it comprises multiple composition, these compositions should be able to provide required thermal performance and flammable performance in the choice.
Evaporator sub-system 140 comprises the evaporator unit of a plurality of parallel connections, wherein two are 144A and the 144B among the figure, and the flow control valve 146A and the 146B that link with evaporator unit, evaporator unit wherein is arranged in the space of required cooling on demand, and links to each other with main bloating plant 138 by flow controlling unit.Also have, these parts also all are conventional or required type.
Bypass 133 comprises one second bloating plant 148, first heat exchanger 150 and second heat exchanger 152 and a flow control valve 154. Heat exchanger 150 and 152 is depicted as a shell-tube type heat exchange unit, obviously also can adopt other conventional type or designs as required.
The tube side stream 162 of heat exchanger 150 is as high temperature conduit, and it is connected between the inlet of the outlet of condenser 136 and main bloating plant 138.Shell flow path 164 is as cryogenic pipe, and it links to each other with the outlet of tube side stream 162 by second bloating plant 148, thereby makes the part of refrigerant of leaving condenser 136 shunt out, flows to after flowing through heat exchanger in the bypass 133.
The port of export of shell flow path 164 is by the arrival end 166 of flow control valve 154 connections second heat exchanger 152 shell flow path, and the shell flow path of this second heat exchanger 152 is as cryogenic pipe.The port of export 169 of heat exchanger 152 shell flow path links to each other with the high pressure entry of PDAD142.The tube side stream 168 of heat exchanger 152 is as high temperature conduit, between the outlet of its connection compressor 134 and the inlet of condenser 136.
Because the pressure of shared outlet 160 place's cold-producing mediums is lower than the pressure in the bypass 133 in the evaporator sub-system 140, therefore exports 160 and link to each other with the low-pressure inlet of PDAD 142.The structure of this PDAD 142 can be identical with the PDAD38 among top Fig. 8.Obviously, if there is not pressure reduction here, then do not need PDAD 142.
Structure shown in Figure 10 can be by regulating cold-producing medium to the control of refrigerant mass fluxes in the evaporator sub-system 140 and making it and the thermic load that constantly changes is complementary.Obviously, a kind of method that reduces refrigerating capacity is arranged here, promptly close main bloating plant 138 as much as possible.Yet,, just must make the cold-producing medium that leaves condenser 136 reach enough cold excessively in order to close main bloating plant 138.If can not reach enough cold excessively, so just there is gas-liquid mixture to enter into main bloating plant 138, system will no longer cool off this moment.
Yet in the present invention, heat exchanger 150 provides coldly excessively is enough to make the cold-producing medium that enters main bloating plant 138 to liquefy fully, though therefore when main expansion valve is closed as far as possible system also highly stable.
The a part of liquid refrigerant that leaves first heat exchanger is diverted to second bloating plant 148 just can make heat exchanger 150 provide necessary cold excessively.Because by throttling, so it can become the refrigerant mixture of low-pressure low-temperature to liquid refrigerant when flowing through second expansion valve 148.Second bloating plant 148 should be able to make the pressure of the cold-producing medium in the bypass remain on the numerical value of an a little higher than evaporator pressure in the choice.
As previously mentioned, when required refrigerating capacity reached minimum, nearly the refrigerating capacity of 70% mass flow need be diverted in the bypass 133.Yet, when the mass flow of the cold-producing medium of being shunted in the multizone variable capacity system surpasses 50%,, need very large heat exchange amount to convert the liquid refrigerant in the bypass to superheated vapor for the consideration of compressor safety.This point is very difficult for the system of routine, or even impossible.
In the present invention, this problem solves by adopting two heat exchangers.Cold-producing medium in the bypass is throttling in second bloating plant 148 at first, and the mixture of Xing Chenging (it mainly is made of liquid refrigerant) enters into first heat exchanger thus.In first heat exchanger, liquid parts is constantly reduced thereby the cold-producing medium in the bypass absorbs heat.First heat exchanger is arranged between the inlet of the outlet of condenser and main bloating plant, and it is used for making the liquid refrigerant in the major loop cold excessively.Cross cold advantage in above-mentioned patent documentation WO2004/044503 and the applying date be that February 25, application number in 2004 are that PCT/US04/05721, name are called in the patent documentation of " Refrigeration System Havingan Integrated Bypass Device " and have provided description, this patent is incorporated the application in full with the form of reference here.
The refrigerant mixture that leaves heat exchanger 150 flows through heat exchanger 152, and absorbs heat from the high-temperature exhaust air that leaves compressor here.Thus, the refrigerant mixture in the bypass 133 just becomes superheated refrigerant after flowing through second heat exchanger.So just can guarantee that this cold-producing medium is gasified totally, thereby in the protection compressor, reduce the temperature of cold-producing medium before condenser 136 that compressor is discharged.
The delivery temperature that reduces compressor can improve the performance of whole system.In addition, because the temperature of compressor 134 exhausts is much higher than the temperature of the refrigerant mixture in the bypass 133, so can form heat exchange fully in the heat exchanger 152, thereby make the termination of bypass form superheated vapor.
In the present invention, because the cold-producing medium in the bypass will flow through two heat exchangers of series connection, therefore can absorb enough heats, and form superheated vapor in the terminal of bypass, this point is a required condition of multizone varying capacity application system that has bypass.
As the various documents of being quoted here were described, bypass also had many advantages for high heat load.For example, the refrigeration system among Figure 10 can not have the cold-producing medium of shunting in the bypass when maximum heating load.As selection, flow control valve 154 in the bypass 133 also can be used to when the very high refrigerating capacity of thermic load is maximum the cold-producing medium of 5% to 15% mass flow is diverted in the bypass, and along with the minimizing of thermic load can be diverted to maximum about 60% even 70% cold-producing medium in the bypass.
Figure 11 shows that an alternative embodiment of the invention 130A.This embodiment is similar to the embodiment of Figure 10, except being provided with of the upstream extremity of bypass 133A different.For more succinct, different places is only described here.
As shown in figure 11, the upstream extremity of bypass 133A is formed by one section thicker pipe of diameter, and it is preferably 3 times (as 2.54cm) of all the other pipeline diameters in the system.It is as the memory space (liquid trap) on the pipe of bypass work schedule cryogen.When multizone system need reach maximum cooling capacity, thus the valve in the bypass 194 close and prevent that cold-producing medium is diverted among the bypass 133A, make 100% cold-producing medium flow through evaporator sub-system 140 and condenser 136 in the major loop 132 thus.
In the time of under refrigeration duty drops to a certain predetermined value, for example this predetermined value descends 50% corresponding to required refrigerating capacity, enters among the bypass 133A thereby valve 95A opens the cold-producing medium that makes above 50%.Yet when these cold-producing mediums flow through bypass, the most of cold-producing medium in the bypass all was kept in the liquid trap 190.The amount of being preserved preferably is at least 50%, and more preferably 70% of institute's diverted mass flow.All the other cold-producing mediums of being shunted flow through second bloating plant 148 and flow to heat exchanger 152, thereby 152 provided the cold-peace desuperheat as previously mentioned.
The advantage of structure shown in Figure 11 is: the feed tube of second bloating plant has been used as liquid trap, and it has preserved a part of liquid refrigerant when required refrigerating capacity descends.
In a further advantageous embodiment, the identical mode of plane system 130 (Figure 10) is operated before the 130A of system.Thus, when thermic load is 100%, thereby thereby valve 95A and 194 work make the cold-producing medium of about 5-10% flow through the advantage that bypass has bypass.When thermic load drops under the predetermined threshold, in the time of as under the 70-80% time or under the design maximum, thereby control valve work improves the refrigerating capacity that the mass flow of bypass reduces whole system.
In explanation of the present invention, for the sake of clarity, employing be specific technology.Yet the present invention is not limited to specific description term, and each particular term includes all technology of similar functions and similar operations.
Equally, it also is exemplary describing the embodiment that shows here, and other modification, variation or embodiment within the scope of the present invention all is conspicuous to those skilled in the art.Therefore, scope of the present invention is only determined by claims rather than specification.

Claims (39)

1, a kind of varying capacity refrigeration system, it comprises:
One main refrigerant circuit and a refrigerant bypassing;
Wherein main refrigerant circuit comprises:
Compression set, its no matter thermic load how to change all with constant speed work so that the cold-producing medium in the compression major loop;
Condensing unit, it is used for making compression back cold-producing medium to emit heat;
Main expansion gear, it is used for making the cold-producing medium decompression of leaving condensing unit; And
Vaporising device, it is used for making the space that is cooled to emit heat;
Wherein refrigerant bypassing comprises:
Second expansion gear;
First and second heat-exchange devices, it is connected with main refrigerant circuit so that make cold-producing medium wherein emit heat; And
Volume control device, it is operated according to thermic load, is used in the upstream of main expansion gear the part of refrigerant in the main refrigerant circuit being flow through above-mentioned heat exchanger and flows to an inlet of compression set;
Provided the cold-peace desuperheat thereby this heat-exchange device is connected with main refrigerant circuit, thereby no matter how its mass flow all can absorb enough heats to the cold-producing medium wherein in the bypass that the cold-producing medium of being shunted was gasified totally before turning back to the suction port of compressor.
2, refrigeration system as claimed in claim 1, it further comprises differential pressure adjusting device, it is used for the outlet of vaporising device is linked to each other with an inlet of compression set with bypass.
3, refrigeration system as claimed in claim 1, vaporising device wherein comprises:
A plurality of evaporation elements, it is arranged in the select location place in the space that is cooled;
The device that the inlet of each evaporation element is linked to each other with the outlet of main expansion gear selectively; And
Be used for the outlet of evaporation element is connected to the device that compression set enters the mouth jointly.
4, refrigeration system as claimed in claim 3, jockey wherein comprises differential pressure adjusting device, it is used for the outlet of vaporising device is linked to each other with the inlet of compression set with bypass.
5, refrigeration system as claimed in claim 1, it further comprises in bypass and is used for device that the part of refrigerant that is diverted to bypass is stored.
6, a kind of refrigeration system, it comprises:
One main refrigerant circuit, it comprises:
One compressor, no matter how thermic load changes all with constant speed work for it;
One condenser;
One main bloating plant; And
One evaporimeter; And
One refrigerant bypassing, it links to each other major loop with an inlet of compressor, and this bypass comprises:
One second bloating plant;
First and second heat exchangers; And a flow control appliance, it is operated according to thermic load, thereby makes the part of refrigerant of leaving condenser flow through second bloating plant, and flows to the inlet of compressor through above-mentioned heat exchanger;
Thereby being connected with main refrigerant circuit, this heat-exchange device make a heat exchanger provide cold, another heat exchanger provides desuperheat, thereby no matter how its mass flow all can absorb enough heats to the cold-producing medium wherein in the bypass was gasified totally before turning back to the suction port of compressor.
7, refrigeration system as claimed in claim 6, it further comprises the pressure reduction conditioning equipment, it is used for the outlet of evaporimeter is linked to each other with the inlet of compressor with bypass.
8, refrigeration system as claimed in claim 6, evaporimeter wherein comprises:
A plurality of evaporation elements, it is arranged in the select location place in the space that is cooled;
The outlet of evaporation element is connected to the inlet of compressor jointly; And
Control valve, it links to each other each inlet of evaporation element in operation selectively with the outlet of main bloating plant.
9, refrigeration system as claimed in claim 8, wherein
The outlet of evaporation element is connected to an inlet of a pressure reduction conditioning equipment jointly;
The outlet of bypass is connected to another inlet of pressure reduction conditioning equipment;
The outlet of pressure reduction conditioning equipment is connected to the inlet of compressor.
10, refrigeration system as claimed in claim 6, it further comprises a liquid trap, stores so that will be diverted to the part of refrigerant of bypass.
11, refrigeration system as claimed in claim 6, wherein:
Bypass comprises, arranged in series, second bloating plant, first stream of first heat exchanger and second stream of second heat exchanger;
Second stream of first heat exchanger is connected between the inlet of the outlet of condenser and main bloating plant;
Second stream of second heat exchanger is connected between the inlet of the outlet of compressor and condenser; And the inlet of bypass is arranged between the inlet of the outlet of first heat exchanger, first stream and main bloating plant.
12, as the refrigeration system of claim 11, flow-control equipment wherein is used for improving the mass flow of cold-producing medium in the bypass when thermic load descends in operation; And when rising, thermic load is used for reducing the mass flow of cold-producing medium in the bypass.
13, as the refrigeration system of claim 11, it further comprises a liquid trap, and this liquid trap is used for the part of refrigerant that is diverted to bypass is stored.
14, as the refrigeration system of claim 13, liquid trap wherein is made of the part of one section enlarged diameter of the second bloating plant upstream bypass duct.
15, refrigeration system as claimed in claim 6, bypass wherein are connected to the major loop exit in the first heat exchanger downstream.
16, refrigeration system as claimed in claim 6, wherein
Evaporimeter is made of the evaporation element of a plurality of parallel connections, and these evaporation elements are arranged in the various piece of native system institute cooling space; And native system further comprises a plurality of control valves, it is connected to main bloating plant on these evaporation elements respectively, when a certain ad-hoc location of a certain moment need not cool off, these control valves made corresponding evaporation component idle by cutting off corresponding cold-producing medium in operation; And
Flow control valve in the bypass, it is used for controlling the refrigerant flow of bypass in operation, unwanted cold-producing medium flows in the bypass in the main refrigerant flow path thereby make when a specific evaporation component is idle.
17, as the refrigeration system of claim 16, wherein thereby the flow control valve in the bypass is all worked at all evapn parts in operation and about cold-producing medium of 5% to 15% is diverted in the bypass when making required refrigerating capacity reach maximum, thereby and does not work at some evaporation component and the highest about 70% cold-producing medium to be diverted to bypass when making the thermic load minimizing.
18, refrigeration system as claimed in claim 6, wherein the flow control valve in the bypass is diverted to about cold-producing medium of 5% to 15% in the bypass when the very high required refrigerating capacity of thermic load reaches maximum in operation, and the highest about 70% cold-producing medium can be diverted to bypass when thermic load reduces.
19, refrigeration system as claimed in claim 6, wherein the cold-producing medium that circulates in the system is made of a composition.
20, refrigeration system as claimed in claim 6, wherein the cold-producing medium that circulates in the system is a kind of mixed type cold-producing medium, and it comprises multiple composition, and these compositions should be able to provide required thermal performance and flammable performance when selecting.
21, refrigeration system as claimed in claim 6, wherein
The cold-producing medium that leaves condenser flows through a stream of first heat exchanger; And the part of refrigerant of leaving first heat exchanger, first stream is connected on one second stream of first heat exchanger through second bloating plant, thereby makes the cold-producing medium heat release of cold-producing medium in bypass of leaving condenser, and provides cold thus.
22, as the refrigeration system of claim 21, wherein
The cold-producing medium that leaves compressor flows through a stream of second heat exchanger; And
The outlet of first heat exchanger, second stream is connected with one second stream of second heat exchanger, thereby the cold-producing medium of cold-producing medium in bypass that leaves compressor conducted heat, and desuperheat is provided thus.
23, as the refrigeration system of claim 22, it further comprises a liquid trap, and this liquid trap is arranged between the outlet and second bloating plant of first heat exchanger, first stream.
24, refrigeration system as claimed in claim 6, wherein
The cold-producing medium that is diverted to bypass flows through first stream of first heat exchanger and absorbs heat from leaving the cold-producing medium that condenser flows through first heat exchanger, second stream;
The cold-producing medium that leaves first heat exchanger, first stream flows through first stream of second heat exchanger, and from leaving the cold-producing medium absorption heat that compressor flows through second heat exchanger, one second stream; And
The cold-producing medium that leaves second heat exchanger, first stream flows to the inlet of compressor, is delivered to from main circuit refrigerant that the heat of cold-producing medium is enough to make the cold-producing medium in the bypass to be gasified totally before reaching the suction port of compressor the bypass.
25, as the varying capacity refrigeration system of claim 24, wherein the flow-control equipment in the bypass is in operation, when thermic load descends, be used for improving the mass flow of cold-producing medium in the bypass, and when thermic load rises, be used for reducing the mass flow of cold-producing medium in the bypass.
26, a kind of method that is used for improving varying capacity refrigeration system efficient, refrigeration system wherein comprises a main refrigerant circuit, this loop comprises a compressor, a condenser, a main bloating plant and an evaporimeter, they couple together and form a closed-loop path, and cold-producing medium circulates therein, and this method may further comprise the steps:
The part of refrigerant of leaving condenser is diverted in second refrigerant flow path, this second refrigerant flow path comprises second bloating plant and two heat exchangers, one of them heat exchanger connects to the main refrigerant flow path heat between the main bloating plant inlet with condensator outlet, and another heat exchanger connects to the heat of the main refrigerant flow path between the condenser inlet with compressor outlet simultaneously;
Thereby making the cold-producing medium of being shunted flow through above-mentioned heat exchanger makes the cold-producing medium that flows in the main refrigerant flow path emit heat; And
Make cold-producing medium that leaves bypass and the cold-producing medium that leaves evaporimeter turn back to an inlet of compressor.
27, as the method for claim 26, the cold-producing medium that wherein leaves the cold-producing medium of bypass and leave evaporimeter turns back to the inlet of compressor by a pressure reduction conditioning equipment, and this pressure reduction conditioning equipment is used for mixing two strands of steams of different pressures.
28, as the method for claim 26, cold-producing medium wherein is diverted in the bypass in a position in heat exchanger downstream.
29, as the method for claim 26, it further may further comprise the steps:
Thereby the amount of condenser cold-producing medium that flow out, that be diverted to bypass controlled according to thermic load regulate refrigerating capacity; And
Regardless of thermic load, compressor turns round continuously with constant rate of speed basically.
30, as the method for claim 29, wherein under the maximum heating load condition, about 5% to 15% the cold-producing medium that flows out from condenser is diverted to the bypass, and hour best result is flowed about 70% in thermic load.
31, as the method for claim 26, wherein
Main refrigeration stream comprises a plurality of evaporator units, and it is arranged in the position of being cooled off respectively; And this method further may further comprise the steps:
Needing maximum cooling capacity to cool off all local time, the cold-producing medium of predetermined minimum amount is being diverted in the bypass; And
Make the amount raising of the cold-producing medium that is diverted to bypass along with the decline of thermic load.
32, as the method for claim 31, it further may further comprise the steps:
By stopping to flow of cold-producing medium those are left unused in the specific evaporator unit that given time does not need to cool off the place;
Those cold-producing mediums that under normal circumstances are transported to the specific evaporator unit are diverted in the bypass.
33, as the method for claim 26, wherein the cold-producing medium that circulates in the system is made of a kind of composition.
34, as the method for claim 26, wherein the cold-producing medium that circulates in the system is a kind of mixed type cold-producing medium, and it comprises multiple composition, and these compositions should be able to provide required thermal performance and flammable performance when selecting.
35, as the method for claim 26, it further may further comprise the steps: the part of refrigerant that will be diverted to bypass is stored in the liquid trap.
36, as the method for claim 26, it further comprises by following operation makes the cold excessively step of cold-producing medium of leaving condenser:
Make the cold-producing medium that leaves compressor flow through one first stream of first heat exchanger; And
The part of refrigerant of leaving first heat exchanger, first stream is diverted to one second stream of first heat exchanger through second bloating plant, and the cold-producing medium that leaves condenser thus is just with the cold-producing medium in the heat transferred bypass.
37, as the method for claim 26, it further comprises the step that makes the cold-producing medium desuperheat that leaves compressor by following operation:
Make the cold-producing medium that leaves compressor flow through one first stream of second heat exchanger; And
Make the cold-producing medium that leaves first heat exchanger, second stream flow through second stream of second heat exchanger, thereby make the cold-producing medium that leaves compressor the cold-producing medium in the heat transferred bypass.
38, as the method for claim 37, it further may further comprise the steps: the cold-producing medium that will be diverted to bypass from the outlet of first heat exchanger, first stream stores the liquid trap.
39,, be delivered to from main circuit refrigerant wherein that the heat of cold-producing medium is enough to make the cold-producing medium in the bypass to be gasified totally the bypass before being transported to the suction port of compressor as the method for claim 37.
CNA2004800238245A 2003-08-18 2004-08-18 Multizone air-conditioning system with a single frequency compressor Pending CN1839286A (en)

Applications Claiming Priority (2)

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