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WO2008000823A1 - Procédé et système de distribution d'un liquide expansible - Google Patents

Procédé et système de distribution d'un liquide expansible Download PDF

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Publication number
WO2008000823A1
WO2008000823A1 PCT/EP2007/056588 EP2007056588W WO2008000823A1 WO 2008000823 A1 WO2008000823 A1 WO 2008000823A1 EP 2007056588 W EP2007056588 W EP 2007056588W WO 2008000823 A1 WO2008000823 A1 WO 2008000823A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
refrigerant
evaporator
condenser
inlet
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.)
Ceased
Application number
PCT/EP2007/056588
Other languages
English (en)
Inventor
Claes Stenhede
Peter Kaden
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Alfa Laval Corporate AB
Original Assignee
Alfa Laval Corporate AB
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
Application filed by Alfa Laval Corporate AB filed Critical Alfa Laval Corporate AB
Publication of WO2008000823A1 publication Critical patent/WO2008000823A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • 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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/022—Evaporators with plate-like or laminated elements

Definitions

  • the present invention relates to a method and a system for improved distribution of an expanding liquid in heat-exchanger systems.
  • a system of this kind is disclosed in US-A-5.749,237.
  • a mixture of liquid and gas i.e. a two-phase flow
  • a mixture of liquid and gas enters through a port into a header and is subsequently distributed to channels, and as the mixture passes the chan- nets of the plate heat exchanger, heat from a medium surrounding the channels is absorbed by the mixture through evaporation of the mixture, in the case of a two-phase flow the liquid refrigerant enters an expansion valve upstream of the port at a high pressure, normally a pressure close to the condensing pressure. In the valve, the liquid expands or "flashes" to just above the evaporation pressure and a part of the liquid vaporizes.
  • each channel should ideally be charged with a precise amount of liquid and gaseous components. It is important to know that the expansion valve does not control the evaporation pressure, and the pressure drop over the valve is constant over short periods and is given by the refrigeration duty and the ambient conditions but not by the valve.
  • the valve controls the flow (capacity) by changing the cross section, that is. the internal resistance.
  • a precise distribution can be either an equai distribution between the various channels, or any other well defined distribution corresponding to a certain case, e.g. when the evaporator has two sections, which are used to cool two different fluids, having different properties.
  • the channels in the two sections shall have different, yet precise, flow rates.
  • the distribution can be improved if the pressure drops over the channels are great compared to the pressure drop in the header. The higher this ratio is, the less the pressure drop difference between the channels and the belter the distribution will be.
  • Prior art solutions include distributors that are arranged close to the entrance of each (or every second/third) channel
  • the distributors generally comprise a fixed restriction of the channel cross section, which results in a pressure drop prior to the channel but after the mixture has been distributed along the length of the header, as opposed to the previously described situation in which the main pressure drop occurs in the valve, before the mixture is distributed.
  • the channel pressure drop is now increased as compared to the header pressure drop
  • a device for uniform expansion of a liquid/gas two-phase refrigerant mass flow in a plate evaporator is described in US-A-5 806 586.
  • the evaporator has a distribution duct, which is capable of being loaded on the inlet side with the refrigerant mass flow coming from an expansion valve.
  • the evaporator further has a plurality of exchanger sections branched off essentially perpendicularly to the distribution duct along the latter at a distance from one another.
  • a porous body is arranged in the distribution duct.
  • the object of the present invention is to eliminate or at least alleviate the above referenced drawbacks and to provide an improved method and a system for precise distribution of a refrigerant into each channel of a heat exchanger, particularly during part load conditions
  • each restrictor will be fed with a precise amount of liquid so that each channel will be fed with a precise amount of liquid and vapour.
  • the pressure altering means comprise a pump, and the step of changing the pressure is performed by said pump.
  • a pump arranged upstream of the evaporator is a convenient way of achieving an increased pressure.
  • the increased pressure before the evaporator makes it possible to vary the pressure upstream of the restrictors within a larger interval without risking that the refrigerant flashes. Since the pressure drop over the restrictors will govern the flow through the channels the larger pressure interval will result in a larger flow interval and thereby a larger capacity interval.
  • both a pump and a valve are used. If the pressure generated by the pump is difficult to control, the valve is arranged downstream of the pump. The valve makes it possible to lower the pressure up- streams of the restrictors and the variable pressure drop over the restrictors results in a changed capacity (flow).
  • the pressure generated by the pump is regulated by a motor of variable speed. This is a straightforward way of achieving a variable pressure prior to the evaporator. In such an embodiment the valve is obsolete.
  • the condenser is disposed in an elevated position to create a static pressure difference through a liquid column.
  • a liquid column can atso be obtained by a tank in an elevated position containing refrigerant.
  • the step of changing the temperature is preferably performed by a subcooler arranged upstream of the evaporator.
  • the subcooler is capable of lowering the temperature of the refrigerant in such a way that the refrigerant will remain in a liquid state even after the decrease in pressure experienced in the pressure altering means.
  • the pressure altering means preferably comprise a valve but couid also consist of the previously mentioned pump.
  • the subcooler constitutes a separate section of the evaporator, such that the refrigerant flows from the condenser into said separate section of the evaporator, where it is cooled down, and then to the valve.
  • the subcooling can also be effected with refrigerant that is bypassed from the heat-exchanger circuit, in a system called an economizer in the field of refrigeration.
  • the subcooler comprises an individual cooling circuit in which a sufficiently cold cooling media flows. An individual circuit is a convenient way of making the subcooler independent of the rest of the heat-exchanger system.
  • An inventive heat-exchanger system comprises means for executing the above steps.
  • Fig. 1 is a schematic of a basic refrigeration cycle
  • Fig. 2 is a partial schematic of a plate heat exchanger according to prior art
  • Fig. 3 is a schematic of a plate heat exchanger in accordance with Fig. 2. provided with a main expansion valve;
  • Fig. 4 is a schematic of a plate heat exchanger in accordance with Fig. 2. provided with individual expansion valves for each channel;
  • Figs. 5-7 are schematics of a plate heat exchanger in accordance with Fig. 2. provided with individual fixed restrictors for each channel and a main expansion valve;
  • Fig. 8 is a schematic of a plate heat exchanger according to a first em- bodiment of the present invention.
  • Fig. 9 is a schematic of a plate heat exchanger according to a third embodiment of the present invention.
  • FIG. 1 The basic compressor refrigeration cycle according to prior art is shown in Fig. 1.
  • the actual use of the cycle can obviously be in an air conditioning apparatus/plant, a heat pump as well as in a proper refrigeration apparatus/plant.
  • the control of the valve 2 in conjunction with the evaporator 3 contributes to a good functioning of the cycle.
  • the valve 2 has to be adjusted accordingly. If too much refrigerant leaves the valve 2. liquid might not evaporate completely in the channels. This results in liquid leaving the evaporator 3, which in certain cases can damage the compressor 4. If too little refrigerant passes through the valve 2, the required capacity cannot be maintained. It is therefore essential that the expansion valve 2 is accurately controlled. Subcooling the refrigerant by cooling, increased pressure or a combination of both leads to a control range. This control range is relatively wide and used to control the expansion valve 2 and thereby the capacity of the evaporator 3.
  • a heat exchanger in a heat exchanger, see Fig 2, composed of a number of parallel channels 6, it can be difficult to obtain a precise distribution of a fluid from a distribution header 5 to the parallel channels 6 and then into a collection header 7.
  • the distribution header 5, or header is a distribution manifoid from which the channels 6 are branched off.
  • the heat exchanger is just indicated as separated surfaces 8. It can be composed of any type of channels connected in parallel.
  • FIG. 3 shows the vaive/evaporator assembly.
  • Saturated or almost saturated liquid refrigerant enters the valve 2 at a high pressure, usually close to the condensing pressure. In the valve 2 it expands to just above the evaporation pressure, whereby a part of the liquid vaporizes.
  • the resulting two-phase fluid has a large volume, which increases the pressure drop in the header 5, which compounds the problem. If the refrigerant velocity is low in the distribution header 5, the liquid part settles at the entrance part of the distribution header 5 and enters preferentially in the first channels, extending from that part of the distribution header 5.
  • the pressure drop C-O is still comparatively low, while the pressure drop A-A'-D and B-B'-C is high, practically corresponding to the differential pressure between the condensing and evaporation pressures.
  • the flow of refrigerant through different channels will be precise, since there is a precise amount of liquid refrigerant passing each variable restrictor 2'. There is consequently no distribution problem as there is only liquid refrigerant and no gaseous refrigerant in the distribution header 5.
  • the solution of using a large number of small, adjustable restrictors is costly, and to actually integrate the valves into the evaporator 3 is difficult. Further the maintenance and cleaning of such valves or restrictors are difficult.
  • the fixed restrictors 9-11 can be in the form of a pipe with fixed restrictors 9 in its peripheral wall, said pipe being inserted in the distribution header 5, see Fig. 5.
  • the pfates can be formed into a plate-like restrictor 10 at each channel infet. see Fig. 6, or disks with drilled restrictors 11 , inserted in a port hole of each channel, see Fig. 7.
  • the fixed restrictors 9-11 if allowed to take the full differential pressure, will do a good job distributing the refrigerant.
  • valve 2 in order to operate at part load the valve 2 has to be used to realise the necessary pressure drop in order to vary the flow through the channels, and the larger the pressure drop, the more of the previously mentioned problems with the two- phase flow will recur.
  • optimal size of the restrictors varies with nominal capacity, pressure, type of refrigerant among others, i.e. each refrigeration system needs individually tailored restrictors.
  • the use of fixed restrictors in the above context will be an inflexible solution.
  • FIG. 8 shows a partial schematic view of a plate heat-exchanger system according to the first embodiment of the invention, showing the evaporator 3 with its distribution header 5 and channels 6 connecting the distribution header 5 to the collection header 7.
  • Fixed restrictors 12 are distributed along the length of the distribution header 5, said re- strictors 12 fluidly connecting the inside of the distribution header 5 and the channels 6.
  • the restrictors 12 can be of a type described earlier with reference to Figs. 5-7.
  • Upstream of the valve 2 a subcooler 13 is arranged for cooling of the refrigerant.
  • the subcooler 13 can constitute a part of the evaporator 3 in such a way that the refrigerant flows from the condenser 1 into a separate section of the evaporator 3. where it is cooled and then to the valve 2.
  • the subccoler 13 can also comprise a separate cooling circuit or an economizer.
  • the subcooler 13 cools the refrigerant with a cooling fluid, and in gen- eral.
  • the cooling fluid can be any sufficiently cold fluid, including a flow from an economizer.
  • This first embodiment of the invention solves the distribution problem in the following way: Consider a situation where flashing occurs at the expansion valve 2. With the inventive system the refrigerant can be cooled down by the subcooler 13 before entering the expansion valve 2. As the refrigerant passes the expansion valve 2 it will ex- perience a pressure drop, but since the temperature is lowered the refrigerant will not flash. Thus, a one-phase flow is present in the distribution header 5, which eliminates said drawbacks.
  • the previous method of ensuring a precise distribution is based on the fact that when the refrigerant cools down from the saturated condensing tem- perature to a temperature somewhat above the evaporation temperature, the pressure can be lowered in the distribution header 5. from which the restric- tors 12 lead into the channels 6, without causing any flashing. It should be noted that the relevant pressures and temperatures vary between different types of refrigerant and that the inventive concept is not limited to any particu-sammlung refrigerant. Once a specific refrigerant is chosen, the temperatures and pressures are given. The variable differential pressure over the restrictors 12 is the parameter which controls the refrigerant flow and thus the capacity.
  • the maximum capacity of the evaporator 3 occurs when the restrictors 12 essentially discharge the total differential pres- sure.
  • the total differential pressure corresponds to the difference between the condensing and evaporation pressures.
  • the differential pressure over the restrictors 12 is the driving force for the flow.
  • the pressure drop over the valve 2 is increased, which reduces the pressure drop over the restrictors 12 and thus the flow through the channels 6.
  • a pump 14 is arranged upstream of the expansion valve 2. The pump 14 makes it possible, for example, to increase the pressure before the valve 2.
  • the temperature in the flow between the condenser 1 and the evaporator 3 is constant while the pressure is increased by means of a pump 14.
  • the pump 14 increases the pressure (a') after the condenser (not shown) to a higher pressure (a).
  • the variable valve 2 decreases this pressure (a) to a lower pressure (b).
  • the controlling variable for the refrigerant flow is the variabie pressure difference over the restrictors 12.
  • the restrictors 12 are laid out to give the required minimum capacity for the full differential pressure drop, that is. when the valve 2 is fully open and the pump 14 is inactive.
  • the valve 2 is only necessary if the pump 14 delivers a pressure (a) which is constant or difficult to control. If the pressure (a) provided by the pump 14 can be easily controlled by e.g. a motor with variable speed (not shown), the valve 2 can be removed.
  • the pump 14 can be any suitable pres- sure increasing device, such as a mechanical or thermal pump.
  • the inventive concept is universal in the sense that it can be used for many types of refrigerants.
  • some exemplifying figures are listed for several different cases In the examples shown in the following tables, line pressure drops and other non-relevant pressure drops are omitted.
  • Tabie Basic refrigeration system (refrigerant R507A).
  • ⁇ refers to the fact that the pressure is slightly higher before the evaporator than the evaporation pressure, which is defined at the exit of the evaporator
  • expansion valve is no longer strictly correct, since no expansion takes place.
  • pressure drop is minimal over the expansion valve.
  • the pressure before the fixed restrictions can. without the occurrence of flashing before the fixed restrictions, vary between 17.0 bar and 7.74 bar (the saturated pressure at 7°C), and consequently the capacity can be varied correspondingly, it should also be noted that the subcooling can be achieved with any of the devices described above. in the above example, the superheat can be used to control the expansion valve. In short, if the load decreases so does the superheat, which causes the expansion valve to close.
  • Table 3 exemplifies the second embodiment, in which a pump is arranged downstream the condenser. As mentioned earlier the expansion valve can be removed if the pump can supply a variable pressure. Also, a subcooler can be added.
  • ⁇ refers to the fact that the pressure is slightly higher before the evaporator than the evaporation pressure which is defined at the exit of the evaporator.
  • a subccoier 13 has certain advantages in conjunction with a pump. It can increase the thermodynamic efficiency of the system and moreover, it can improve the operation of the pump 14 as pumps sometimes have difficulties in pumping saturated liquids. Therefore, in a third embodiment, a subccoier 13 according to the first embodiment is arranged upstream of a pump 14 according to the second embodiment. This results in the stated advantages.
  • the restrictor can be either one restrictor or a number of restrictors each feeding one or more channels. In the later configuration the distribution will be improved, as previo ⁇ siy described.
  • the invention thus relates to a method and a system for improved distribution of an expanding liquid in a heat-exchanger system by changing one or more intensive variables for a refrigerant flowing in a heat-exchanger system. It should be pointed out that the above described embodiments used as standalone solutions can be combined.
  • the invention makes it possible to control the refrigerant flow (capacity) by changing the distribution of the pressure drop between a valve and a restrictor and not by changing the flow by means of a variable cross section in a valve. It should also be noted that the inventive concept has bearing on several applications where a number of parallel channels are to be fed by a two- phase flow, such applications including unit coolers, etc.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Système d'échange thermique comportant un circuit muni d'un condenseur (1), des moyens d'altération de pression (2 ; 14), un évaporateur (3) contenant une tête de distribution (5) en communication fluidique, via des restricteurs (9-12), avec plusieurs canaux de fluide (8) reliés en parallèle, et un compresseur (4). La sortie du condenseur (1) est raccordée à l'entrée des moyens d'altération de pression (2 ; 14), la sortie des moyens d'altération de pression (2 ; 14) est raccordée à l'entrée de l'évaporateur (Z), la sortie de l'évaporateur (3) est raccordée à l'entrée du compresseur (4), et la sortie du compresseur (4) est raccordée à l'entrée du condenseur (1). Le circuit contient un réfrigérant et le système comprend : (a) des moyens pour réduire la température du réfrigérant en aval du condenseur et en amont des moyens d'altération de pression ; et/ou (b) des moyens pour modifier la pression comprenant des moyens pour augmenter la pression du réfrigérant en aval du condenseur, de façon à empêcher le réfrigérant de se vaporiser par détente jusqu'à ce qu'il passe par les restricteurs (9-12), pour obtenir ainsi que le réfrigérant liquide s'écoule en une seule phase dans la tête de distribution (5).
PCT/EP2007/056588 2006-06-30 2007-06-29 Procédé et système de distribution d'un liquide expansible Ceased WO2008000823A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE0601442-7 2006-06-30
SE0601442A SE531665C2 (sv) 2006-06-30 2006-06-30 Förfarande och anordning för fördelning av en expanderande vätska

Publications (1)

Publication Number Publication Date
WO2008000823A1 true WO2008000823A1 (fr) 2008-01-03

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PCT/EP2007/056588 Ceased WO2008000823A1 (fr) 2006-06-30 2007-06-29 Procédé et système de distribution d'un liquide expansible

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SE (1) SE531665C2 (fr)
WO (1) WO2008000823A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011003416A3 (fr) * 2009-07-06 2011-04-28 Danfoss A/S Procédé pour réguler le débit d'un fluide frigorigène dans un évaporateur à tubes multiples
EP2674714A1 (fr) * 2012-06-14 2013-12-18 Alfa Laval Corporate AB Échangeur thermique de plaque avec des moyens d'injection
US9562722B2 (en) 2009-03-13 2017-02-07 Carrier Corporation Manifold assembly for distributing a fluid to a heat exchanger
CN111140985A (zh) * 2019-12-30 2020-05-12 宁波奥克斯电气股份有限公司 一种换热器流路的匹配调试装置及匹配调试方法
CN114017965A (zh) * 2021-11-02 2022-02-08 徐州医科大学 热管悬吊式快速低温恒温箱
US11879676B2 (en) 2021-07-30 2024-01-23 Danfoss A/S Thermal expansion valve for a heat exchanger and heat exchanger with a thermal expansion valve

Citations (12)

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US2402802A (en) * 1944-02-17 1946-06-25 Detroit Lubricator Co Refrigerating apparatus
GB1213323A (en) * 1967-04-03 1970-11-25 Refrigerating Specialities Com Refrigerant feed control
US3664150A (en) * 1970-12-30 1972-05-23 Velt C Patterson Hot gas refrigeration defrosting system
US3722230A (en) * 1970-12-10 1973-03-27 United Brands Co Ship refrigeration
US4123919A (en) * 1977-07-25 1978-11-07 Npi Corporation Refrigeration feed system
US4599873A (en) * 1984-01-31 1986-07-15 Hyde Robert E Apparatus for maximizing refrigeration capacity
JPH05149650A (ja) * 1991-11-30 1993-06-15 Nippondenso Co Ltd 熱交換装置
WO1995025251A1 (fr) * 1994-03-15 1995-09-21 Hyde Robert E Amplification de la pression d'un liquide avec derivation
FR2731780A1 (fr) * 1995-03-13 1996-09-20 Mc International Systeme de refrigeration, installation frigorifique et procede de refrigeration
WO1997018420A1 (fr) * 1995-10-26 1997-05-22 Jdm, Ltd. Pompe a vitesse variable pour liquide refrigerant
US6145332A (en) * 1999-06-16 2000-11-14 Dte Energy Technologies, Inc. Apparatus for protecting pumps against cavitation
JP2003287321A (ja) * 2002-03-28 2003-10-10 Daikin Ind Ltd プレート式熱交換器及び該熱交換器を備えた冷凍装置

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2402802A (en) * 1944-02-17 1946-06-25 Detroit Lubricator Co Refrigerating apparatus
GB1213323A (en) * 1967-04-03 1970-11-25 Refrigerating Specialities Com Refrigerant feed control
US3722230A (en) * 1970-12-10 1973-03-27 United Brands Co Ship refrigeration
US3664150A (en) * 1970-12-30 1972-05-23 Velt C Patterson Hot gas refrigeration defrosting system
US4123919A (en) * 1977-07-25 1978-11-07 Npi Corporation Refrigeration feed system
US4599873A (en) * 1984-01-31 1986-07-15 Hyde Robert E Apparatus for maximizing refrigeration capacity
JPH05149650A (ja) * 1991-11-30 1993-06-15 Nippondenso Co Ltd 熱交換装置
WO1995025251A1 (fr) * 1994-03-15 1995-09-21 Hyde Robert E Amplification de la pression d'un liquide avec derivation
FR2731780A1 (fr) * 1995-03-13 1996-09-20 Mc International Systeme de refrigeration, installation frigorifique et procede de refrigeration
WO1997018420A1 (fr) * 1995-10-26 1997-05-22 Jdm, Ltd. Pompe a vitesse variable pour liquide refrigerant
US6145332A (en) * 1999-06-16 2000-11-14 Dte Energy Technologies, Inc. Apparatus for protecting pumps against cavitation
JP2003287321A (ja) * 2002-03-28 2003-10-10 Daikin Ind Ltd プレート式熱交換器及び該熱交換器を備えた冷凍装置

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9562722B2 (en) 2009-03-13 2017-02-07 Carrier Corporation Manifold assembly for distributing a fluid to a heat exchanger
WO2011003416A3 (fr) * 2009-07-06 2011-04-28 Danfoss A/S Procédé pour réguler le débit d'un fluide frigorigène dans un évaporateur à tubes multiples
EP2674714A1 (fr) * 2012-06-14 2013-12-18 Alfa Laval Corporate AB Échangeur thermique de plaque avec des moyens d'injection
WO2013186192A1 (fr) 2012-06-14 2013-12-19 Alfa Laval Corporate Ab Échangeur de chaleur à plaques ayant des moyens d'injection
US10107572B2 (en) 2012-06-14 2018-10-23 Alfa Lavalcorporate Ab Plate heat exchanger
CN111140985A (zh) * 2019-12-30 2020-05-12 宁波奥克斯电气股份有限公司 一种换热器流路的匹配调试装置及匹配调试方法
US11879676B2 (en) 2021-07-30 2024-01-23 Danfoss A/S Thermal expansion valve for a heat exchanger and heat exchanger with a thermal expansion valve
CN114017965A (zh) * 2021-11-02 2022-02-08 徐州医科大学 热管悬吊式快速低温恒温箱

Also Published As

Publication number Publication date
SE0601442L (sv) 2007-12-31
SE531665C2 (sv) 2009-06-23

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