WO2001067011A1 - Systeme frigorifique haute efficacite - Google Patents

Systeme frigorifique haute efficacite Download PDF

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Publication number
WO2001067011A1
WO2001067011A1 PCT/US2001/006551 US0106551W WO0167011A1 WO 2001067011 A1 WO2001067011 A1 WO 2001067011A1 US 0106551 W US0106551 W US 0106551W WO 0167011 A1 WO0167011 A1 WO 0167011A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
vortex tube
evaporator
vapor
compressor
Prior art date
Application number
PCT/US2001/006551
Other languages
English (en)
Inventor
Young I. Cho
Cheolho Bai
Original Assignee
Vai Holdings, Llc
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from US09/517,922 external-priority patent/US6250086B1/en
Application filed by Vai Holdings, Llc filed Critical Vai Holdings, Llc
Priority to AU2001239966A priority Critical patent/AU2001239966A1/en
Publication of WO2001067011A1 publication Critical patent/WO2001067011A1/fr

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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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0011—Ejectors with the cooled primary flow at reduced or low pressure
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0012—Ejectors with the cooled primary flow at high pressure
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0014—Ejectors with a high pressure hot primary flow from a compressor discharge
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0015—Ejectors not being used as compression device using two or more ejectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/02—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using Joule-Thompson effect; using vortex effect
    • F25B9/04—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using Joule-Thompson effect; using vortex effect using vortex effect

Definitions

  • the present invention relates generally to a high efficiency refrigeration system and, more specifically, to a refrigeration system utilizing one or more vortex tubes for increasing the overall efficiency of a refrigeration system.
  • a refrigeration system typically consists of four major components connected together via a conduit (preferably copper tubing) to form a closed loop system.
  • the four major components are a compressor, a condenser, an expansion device and an evaporator.
  • a refrigerant will have its pressure either increased or decreased and its temperature either increased or decreased by the four components as it circulates therethrough.
  • the refrigerant is continuously cycled through the refrigeration system.
  • the main steps in the refrigeration cycle are compression of the refrigerant by the compressor, heat rejection of the refrigerant in the condenser, throttling of the refrigerant in the expansion device, and heat absorption of the refrigerant in the evaporator.
  • the compressor provides the energy to keep the refrigerant moving within the conduits and through the major components This process is sometimes referred to as a vapor-compression refrigeration cycle.
  • the vapor-compression ref ⁇ geration cycle is used in air conditioning systems, which cool and dehumidify air in a living space, in a moving vehicle (e g , automobile, airplane, train, etc ), ref ⁇ gerators and heat pumps
  • the refrigerant enters the compressor as saturated vapor and is compressed to a very high pressure
  • the temperature of the ref ⁇ gerant increases during this compression step
  • the refrigerant leaves the compressor as superheated vapor and enters the condenser
  • a typical condenser comp ⁇ ses a single conduit formed into a serpentine-like shape so that a plurality of rows of conduit is formed parallel to each other Metal fins or other aids are usually attached to the serpentine conduit in order to increase the transfer of heat between the refrigerant passing through the condenser and the ambient air Heat is rejected from the superheated vapor as it passes through the condenser and the refrigerant exits the condenser as saturated liquid
  • the expansion device reduces the pressure of the saturated liquid thereby turning it into a saturated liquid-vapor mixture, which is throttled to the evaporator
  • the temperature of the refrigerant drops below the temperature of the ambient air as it goes through the expansion device
  • the refrigerant enters the evaporator as a low quality saturated mixture comprised of approximately 20% vapor and 80% liquid ("Quality" is defined as the mass fraction of vapor in the liquid-vapor mixture )
  • the evaporator physically resembles the serpentine-shaped conduit of the condenser Ideally, the ref ⁇ gerant completely evaporates by absorbing heat from the refrigerated space and leaves the evaporator as saturated vapor at the suction pressure of the compressor and reenters the compressor thereby completing the cycle
  • EER energy- efficiency ratio
  • the ref ⁇ geration cycle has an EER of approximately 30 (kw/kw)
  • the present invention is designed to increase the efficiency of a refrigeration, air conditioning or heat pump system by increasing the efficiency of the ref ⁇ geration cycle
  • the increase in the efficiency is achieved by assisting in the conversion of the refrigerant from vapor to liquid at specific points in the refrigeration cycle
  • a first vortex tube is placed between the expansion device and the evaporator in order to increase the percentage of refrigerant entering the evaporator as a liquid
  • a second vortex tube is placed between the evaporator and the compressor in order to increase the percentage of refrigerant entering the compressor as a vapor Since the heat absorption from the evaporator occurs through the evaporation of the liquid refrigerant, the increase in the percentage of the liquid refrigerant entering the evaporator increases the efficiency of the refrigeration cycle and reduces the size of the evaporator
  • the present invention increases the efficiency of the refrigeration cycle is by placing a vortex tube in the serpentine tubing of the condenser
  • the vortex tube is placed approximately one-quarter of the way in from the inlet of the condenser where desuperheating is completed
  • the vortex tube produces liquid refrigerant and further increases the temperature of the vapor refrigerant thereby reducing the size of the condenser and decreasing the head pressure of the compressor
  • the compression ratio decreases, and the work required by the compressor is reduced, thus increasing the efficiency of the refrigeration cycle
  • FIG. 1 is a block diagram of a typical refrigeration system
  • Figure 2 shows a temperature entropy diagram of the refrigeration system illustrated in Figure 1 ,
  • FIG. 3 is a block diagram of a refrigeration system in accordance with the present invention utilizing a vortex tube proximate the evaporator,
  • Figure 4A illustrates a side cut-away view of a conventional vortex tube
  • Figure 4B is a top cut-away view of the vortex tube shown in Figure 4A
  • FIG. 5 is a block diagram of a refrigeration system in accordance with the present invention utilizing a vortex tube in the condenser
  • Figure 6 is a picto ⁇ al representation of the phase change in the refrigerant in a condenser and vortex tube of the type used in the refrigeration system of Figure 5,
  • FIG. 7 is a block diagram of another embodiment of ref ⁇ geration system in accordance with the present invention which utilizes two vortex tubes,
  • Figure 8 is a block diagram of the refrigeration system of Figure 7 in which the refrigerant vapor bypasses the evaporator and the liquid refrigerant bypasses the condenser,
  • FIG. 9 is a block diagram of another embodiment of a ref ⁇ geration system in accordance with the present invention which utilizes a liquid/vapor separator and/or a third vortex tube,
  • FIG. 10A is a block diagram of another embodiment of a refrigeration system in accordance with the present invention which utilizes two vortex tubes, one before the evaporator and one after the evaporator,
  • Figure 10B is a va ⁇ ation of the embodiment illustrated in Figure 10A in which the liquid and vapor components from the first vortex tube is directed to the evaporator, and
  • Figure 10C is a variation of the embodiment illustrated in Figure 10B in which the central outlet is connected to the inlet of the compressor ⁇ FT ⁇ II F ⁇ DFS ⁇ RIPTIQN OF THF PRFFFRRF ⁇ FMRODIMFNT
  • spe ⁇ fic terminology will be selected for the sake of clarity However, the invention is not intended to be limited to the specific terms so selected, and it is to be understood that each spe ⁇ fic term includes all technical equivalents that operate in a similar manner to accomplish a similar purpose
  • FIG. 1 A typical refrigeration system is illustrated in Figure 1
  • the ref ⁇ geration system includes a compressor 12, a condenser 14, an expansion device 16 and an evaporator 18
  • the various components are connected together via copper tubing 19
  • the ref ⁇ geration system is a closed loop system that circulates a refrigerant through the va ⁇ ous elements
  • refrigerant include R-12, R- 22, R-134A, R-410A, ammonia, carbon dioxide and natural gas
  • a refrigerant is continuously cycled through the ref ⁇ geration system
  • the main steps in the ref ⁇ geration cycle are compression of the ref ⁇ gerant by the compressor, heat rejection of the ref ⁇ gerant in the condenser, throttling of the ref ⁇ gerant in the expansion device, and heat absorption of the refrigerant in the evaporator
  • this process is referred to as the vapor compression ref ⁇ geration cycle
  • the temperature entropy curve of a typical refrigeration cycle is illustrated is Figure 2 Point 2 is where the refrigerant exists as a superheated vapor As the superheated vapor cools inside the condenser, the superheated vapor becomes a saturated vapor (point 2a) As heat transfer to the ambient air continues in the condenser, the ref ⁇
  • the effi ⁇ ency of a ref ⁇ geration cycle depends primarily on the heat absorption from the evaporator and the efficiency of the compressor
  • the former depends on the percentage of liquid in the liquid-vapor ref ⁇ gerant mixture before the evaporator, whereas the latter depends on the magnitude of the head or discharge pressure
  • the pressure of the refrigerant as it enters the compressor is referred to as the suction pressure level and the pressure of the ref ⁇ gerant as it leaves the compressor is referred to as the head pressure level
  • the head pressure can range from about 170 PSIG to about 450 PSIG
  • Compression ratio is the term used to express the pressure difference between the head pressure and the suction pressure Compression ratio is calculated by converting the head pressure and the suction pressure onto an absolute pressure scale and dividing the head pressure by the suction pressure
  • Compression ratio increases, the compressor efficiency drops thereby increasing energy consumption (In most cases, the energy is used by the electric motor that drives the compressor )
  • the temperature of the ref ⁇ gerant vapor increases to the point that oil for lub ⁇ cation may be overheated which may cause corrosion in the ref ⁇ geration system
  • An evaporator is made of a long coil or a se ⁇ es of heat transfer panels which absorb heat from a volume of air that is desired to be cooled In order to absorb heat from this ambient volume, the temperature of the ref ⁇ gerant must be lower than that of the volume
  • the ref ⁇ gerant exiting the expansion device consists of low quality vapor, which is approximately 20% vapor and 80% liquid
  • the liquid portion of the ref ⁇ gerant is used to absorb heat from the desired volume as the liquid ref ⁇ gerant evaporates inside the evaporator
  • the vapor portion of the refrigerant is not utilized to absorb heat from the ambient volume In other words, the vapor portion of the ref ⁇ gerant does not contribute to cooling the ambient volume and decreases the effi ⁇ ency of the refngeration cycle
  • Vortex tube 20 converts at least a portion of the ref ⁇ gerant vapor that exits the expansion device into liquid so that it can be used in the evaporator to absorb heat from the ambient volume
  • Vortex tubes are well-known in other areas of art but are not commonly found in ref ⁇ geration systems
  • the vortex tube 20 is a device which converts a flow of compressed gas into two streams - one stream hotter than and the other stream colder than the temperature of the gas supplied to the vortex tube
  • a vortex tube does not contain any moving parts
  • a high pressure gas stream is shown entering the vortex tube 20 tangentially at one end (i e , the inlet 22)
  • the high pressure gas stream produces a strong vortex flow in the tube 20
  • the vortex flow is similar in shape to a helix
  • the high pressure gas separates into two streams having different temperatures, one along the outer wall and one along the axis of the tube
  • the ⁇ rcumferential velo ⁇ ty is inversely proportional to the radial position
  • the pressure within a vortex tube is lowest at the center of the tube and increases to a maximum at the wall
  • the high pressure gas that enters a vortex tube will be the refrigerant in a ref ⁇ geration cycle Since vapor refrigerant is a compressible medium, the pressure distribution within the vortex tube causes a temperature difference between the inner and outer streams
  • the vortex tube 20 is preferably placed proximate the evaporator 18 In order to reduce manufactu ⁇ ng costs, the vortex tube 20 may be placed immediately before the evaporator 18 However, other positions of the vortex tube proximate the evaporator including a percentage of the distance from the inlet of the evaporator may be desirable
  • a condenser 14 in the ref ⁇ geration cycle is used to convert superheated refngerant vapor to liquid by rejecting heat to the surroundings
  • the condenser is a long heat transfer coil or se ⁇ es of heat rejecting panels similar in appearance to the evaporator Refer ⁇ ng again to Figure 1 , as ref ⁇ gerant enters the condenser 14, the superheated vapor first becomes saturated vapor in the approximately first quarter- section of the condenser, and the saturated vapor undergoes phase change in the remainder of the condenser at approximately constant pressure
  • the refrigerant temperature has to be raised well above that of the surroundings This is accomplished by raising the pressure of the ref ⁇ gerant vapor, a task that is done by the compressor 12 Since vapor temperature is closely related to vapor pressure, it is critically important that the condenser effi ⁇ ently rejects heat from the ref ⁇ gerant to the surroundings If the condenser 14 is not effi ⁇ ent, the compressor 12 has to further increase the head pressure in an attempt to assist the condenser in dumping heat to the surroundings
  • another embodiment of the present invention utilizes a vortex tube 29 in the condenser to convert saturated refrigerant vapor to liquid thus increasing the condenser's efficiency
  • the first approximately one- quarter of the condenser is represented by 14A and the remaining three-quarters of the condenser is represented by 14B
  • the vortex tube 29 is inserted approximately one-quarter of the way into the condenser (i e , at the point where the superheated vapor becomes saturated vapor in full or in part)
  • the vortex tube 29 in an existing condenser, manufacturing costs may be minimized
  • two separate condensers each about the respective size of condenser portions 14A and 14B, may be used
  • the size of the condenser in p ⁇ or art refrigeration systems is often chosen larger than necessary in order to ensure the exchange of heat
  • the present method allows the size of the condenser 14 to be reduced because the substantial amount of saturated ref ⁇ gerant vapor is converted to liquid by the vortex tube
  • the present invention allows the use of a smaller condenser than is the case without a vortex tube thereby redu ⁇ ng the size of air conditioning systems, refrigerators and heat pumps
  • a further embodiment of the present invention utilizes two vortex tubes, one before the evaporator and the second in the condenser, as illustrated in Figure 7
  • the vortex tubes operate in a similar fashion as described in a ref ⁇ geration system when only one vortex tube is used
  • the effi ⁇ ency of the ref ⁇ geration system illustrated in Figure 7 is greater than the effi ⁇ ency of the ref ⁇ geration illustrated in either Figure 3 or Figure 5
  • FIG. 8 illustrates a va ⁇ ation of the two vortex tube ref ⁇ geration systems illustrated in Figure 7 Instead of the vapor that exits vortex tube 20 being recombined with the liquid before entering the evaporator 18, a separate path for the vapor, bypassing the evaporator, is shown This va ⁇ ation should be slightly more efficient than recombining the liquid with the vapor because the vapor does not absorb any heat as it passes through the evaporator Accordingly, only liquid refngerant enters evaporator 18
  • a liquid/vapor separator 35 may be utilized before a ref ⁇ gerant enters the vortex tube 20 Liquid/vapor separators are known in other art areas
  • the liquid/vapor separator 35 ensures that only compressed vapor enters the vortex tube 20 Liquid from the liquid/vapor separator 35 is combined with the liquid that is output by vortex tube 20 and enters the evaporator 18 Any ref ⁇ gerant vapor that is still present bypasses the evaporator and is directed to the compressor 12
  • Vortex tube 31 separates the superheated ref ⁇ gerant into a hot vapor component and a cool vapor component
  • the hot vapor from vortex tube 31 is directed to condenser 14A
  • the output of condenser 14A is combined with the cool vapor output from vortex tube 31
  • the liquid refrigerant from vortex tube 29 bypasses condenser 14B
  • the liquid ref ⁇ gerant output from condenser 14B is mixed with the liquid refngerant output from vortex tube 29
  • This refrigeration system includes the compressor 12, the condenser 14, the expansion device 16, a first vortex tube 20, the evaporator 18, and a second vortex tube 21
  • the vapor refrigerant that is separated out by first vortex tube 20 is combined with the ref ⁇ gerant that exits evaporator 18 and is input into second vortex tube 21
  • FIG. 10B A variation of the ref ⁇ geration system of Figure 10A is shown in Figure 10B in which the vapor ref ⁇ gerant from the first vortex tube 20 is directed to the inlet of evaporator 18
  • the first vortex tube 20 has two inlets, a tangential inlet and a central inlet that communicates wit the vacuum that is created in the central core of the vortex tube.
  • the refrigerant that enters from the tangential inlet creates the vortex motion which eventually creates a vacuum inside the vortex tube.
  • the refrigerant, or component thereof that is separated out by the first vortex tube 20 is directed to the input of the evaporator 18.
  • the refrigerant absorbs heat from the surroundings.
  • the second vortex tube 21 only utilizes a single tangential inlet, i.e., the central inlet is effectively closed off.
  • the second vortex tube 21 also separates the refrigerant into a liquid component and a vapor component.
  • the vapor component from vortex tube 21 is directed to the compressor 12.
  • the liquid refrigerant from second vortex tube 21 is combined with the refrigerant that exits the expansion device 16 via conduit 55.
  • the liquid refrigerant that exits second vortex tube 21 will have suffi ⁇ ent velocity or pressure to be directed back to the inlet of the first vortex tube 20 This can be accomplished by using a two-inlet vortex tube for the first vortex tube 20.
  • a vacuum is created inside the first vortex tube as the vapor refrigerant is converted to the liquid refrigerant and this vacuum communicates with a first central inlet of the first vortex tube.
  • the volume of the refrigerant decreases by a factor of 10 to 100, depending on the type of refrigerants, as phase change occurs from vapor to liquid.
  • the vacuum inside the first vortex tube draws the liquid refrigerant exiting the second vortex tube without an additional pump.
  • the first vortex tube 20 acts as a pump.
  • Second vortex tube 21 also ensures that only vapor ref ⁇ gerant is returned to compressor 12, this also improves the efficiency of the refrigeration cycle
  • the volume of the vapor ref ⁇ gerant ente ⁇ ng the compressor is significantly reduced (by 20%-30% when compared with a refrigeration system that does not use vortex tubes), thus de ⁇ easing the compressor work and increasing the efficiency of the refrigeration cycle
  • approximately 30%-40% is being recycled around the evaporator while approximately 70%-80% is fed back to the compressor Note though that 100% of the ref ⁇ gerant passes through the evaporator 18

Abstract

On décrit un système frigorifique amélioré (10) qui comprend un ou plusieurs tubes Vortex (20, 21, 29, 31) lesquels produisent du frigorigène liquide à partir d'un frigorigène gazeux à l'état saturé dans un cycle frigorifique à compression de vapeur. L'efficacité d'un système frigorifique (10) peut être améliorée si on place des tubes Vortex avant et après l'évaporateur.
PCT/US2001/006551 2000-03-03 2001-03-01 Systeme frigorifique haute efficacite WO2001067011A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU2001239966A AU2001239966A1 (en) 2000-03-03 2001-03-01 High efficiency refrigeration system

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US09/517,922 2000-03-03
US09/517,922 US6250086B1 (en) 2000-03-03 2000-03-03 High efficiency refrigeration system
US09/535,126 2000-03-24
US09/535,126 US6425249B1 (en) 2000-03-03 2000-03-24 High efficiency refrigeration system

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Publication Number Publication Date
WO2001067011A1 true WO2001067011A1 (fr) 2001-09-13

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007107593A2 (fr) * 2006-03-21 2007-09-27 Loeffler Michael Dispositif à pompe à chaleur
WO2009123674A2 (fr) * 2008-02-28 2009-10-08 Greencentaire, Llc Unité de refroidissement
WO2011046458A1 (fr) * 2009-10-12 2011-04-21 Oleszkiewicz Blazej Pompe à chaleur à compression avec accélérateur thermique
CN103727697A (zh) * 2014-01-26 2014-04-16 天津商业大学 高压气体涡流膨胀的二氧化碳低温制冷系统
WO2014198555A1 (fr) * 2013-06-10 2014-12-18 Arcelik Anonim Sirketi Dispositif de refroidissement comprenant un régulateur d'écoulement
CN108773258A (zh) * 2018-08-10 2018-11-09 大连民族大学 基于涡流管的电动汽车供暖系统

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GB516375A (en) * 1938-06-23 1940-01-01 Richard John Cracknell Improvements in or relating to refrigerating processes and apparatus
US2489680A (en) * 1946-05-15 1949-11-29 Philco Corp Refrigerant circulating system
DE832762C (de) * 1944-12-03 1952-02-28 Linde Eismasch Ag Einrichtung zur UEberflutung von uebereinanderliegenden Verdampfern
GB771785A (en) * 1955-09-01 1957-04-03 John William Frederick Matthes Improvements in or relating to refrigerating systems
US3600904A (en) * 1969-05-27 1971-08-24 Emerson Electric Co Control for refrigeration system
US5706666A (en) * 1994-04-12 1998-01-13 Nippondenso Co., Ltd. Refrigeration apparatus

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB516375A (en) * 1938-06-23 1940-01-01 Richard John Cracknell Improvements in or relating to refrigerating processes and apparatus
DE832762C (de) * 1944-12-03 1952-02-28 Linde Eismasch Ag Einrichtung zur UEberflutung von uebereinanderliegenden Verdampfern
US2489680A (en) * 1946-05-15 1949-11-29 Philco Corp Refrigerant circulating system
GB771785A (en) * 1955-09-01 1957-04-03 John William Frederick Matthes Improvements in or relating to refrigerating systems
US3600904A (en) * 1969-05-27 1971-08-24 Emerson Electric Co Control for refrigeration system
US5706666A (en) * 1994-04-12 1998-01-13 Nippondenso Co., Ltd. Refrigeration apparatus

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007107593A2 (fr) * 2006-03-21 2007-09-27 Loeffler Michael Dispositif à pompe à chaleur
WO2007107593A3 (fr) * 2006-03-21 2007-12-06 Michael Loeffler Dispositif à pompe à chaleur
WO2009123674A2 (fr) * 2008-02-28 2009-10-08 Greencentaire, Llc Unité de refroidissement
WO2009123674A3 (fr) * 2008-02-28 2010-01-28 Greencentaire, Llc Unité de refroidissement
WO2011046458A1 (fr) * 2009-10-12 2011-04-21 Oleszkiewicz Blazej Pompe à chaleur à compression avec accélérateur thermique
WO2014198555A1 (fr) * 2013-06-10 2014-12-18 Arcelik Anonim Sirketi Dispositif de refroidissement comprenant un régulateur d'écoulement
CN103727697A (zh) * 2014-01-26 2014-04-16 天津商业大学 高压气体涡流膨胀的二氧化碳低温制冷系统
CN103727697B (zh) * 2014-01-26 2016-08-17 天津商业大学 高压气体涡流膨胀的二氧化碳低温制冷系统
CN108773258A (zh) * 2018-08-10 2018-11-09 大连民族大学 基于涡流管的电动汽车供暖系统

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