EP0415840A1 - Verflüssiger mit Sammler/Nachkühler - Google Patents

Verflüssiger mit Sammler/Nachkühler Download PDF

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Publication number
EP0415840A1
EP0415840A1 EP90402372A EP90402372A EP0415840A1 EP 0415840 A1 EP0415840 A1 EP 0415840A1 EP 90402372 A EP90402372 A EP 90402372A EP 90402372 A EP90402372 A EP 90402372A EP 0415840 A1 EP0415840 A1 EP 0415840A1
Authority
EP
European Patent Office
Prior art keywords
chamber
condenser
collector
lower chamber
volume
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.)
Granted
Application number
EP90402372A
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English (en)
French (fr)
Other versions
EP0415840B1 (de
Inventor
Paul Beatenbough
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.)
Valeo Engine Cooling Inc
Original Assignee
Valeo Engine Cooling Inc
Blackstone Corp
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 Valeo Engine Cooling Inc, Blackstone Corp filed Critical Valeo Engine Cooling Inc
Publication of EP0415840A1 publication Critical patent/EP0415840A1/de
Application granted granted Critical
Publication of EP0415840B1 publication Critical patent/EP0415840B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05375—Assemblies of conduits connected to common headers, e.g. core type radiators with particular pattern of flow, e.g. change of flow direction
    • 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
    • F25B39/04—Condensers
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0084—Condensers

Definitions

  • Automobile air conditioning systems of the thermostatic expansion valve type can advantageously be fitted with a reservoir mounted in the circuit between their condenser and this expansion valve, thus providing sufficient storage volume for the refrigerant to cope with the variations inherent in the conditions of operation of the system as well as losses of coolants due to diffusion phenomenon and small leaks.
  • a tank For such a tank to be effective, it must be downstream from the point where the condensation of the refrigerant occurs, it must have an internal configuration offering sufficient capacity and / or an internal centrifuge or baffle device to separate the gaseous phases of the liquid phases of the refrigerant, it must have a liquid outlet orifice placed so that it communicates with the agent under the liquid / gas interface, and finally, the air conditioning system is filled with a quantity of refrigerant such that the liquid / gas interface is in the interior volume offered by such a tank when the system is operating under normal conditions of use.
  • a conventional condenser When an automobile air conditioning system is equipped with a tank and the level of charge of the refrigerant in the system is such that it does not cause the tank to overflow under normal conditions of use, a conventional condenser , for the most part, produces a coolant with a zero subcooling level. In the event that this tank overflow occurs, a conventional condenser can operate with a subcooling level which varies directly with the volume of refrigerant overflowed and with the operating conditions of the system, but it is desirable to actually avoid such sub-cooling because that it has the effect of reducing in the condenser the volume available for the condensation of the refrigerant leading to higher pressures in the condenser and lower performance of the system.
  • Automotive air conditioning systems operating with a tank and a coolant fill level set so that the liquid / gas interface is maintained inside the tank under normal conditions of use, can provide better performance, for a given material, when adding an independent secondary cooler installed in the circuit between the tank and the thermostatic expansion valve.
  • known systems using secondary coolers have the disadvantages of being more expensive, of being complex and of offering greater risks of refrigerant leakage.
  • the present invention relates to a condenser, particularly intended for the air conditioning system of automobiles, of the thermostatic expansion valve type.
  • the automobile condenser of the present invention comprises a vertically mounted primary and secondary manifold, communicating with inlet and outlet pipes and interconnected by tubes generally arranged horizontally, is characterized in that the secondary manifold is dimensioned to allow the refrigerant gas to separate from the coolant so as to provide a space for the coolant in its upper part and a space for the coolant in its lower part placed in communication with the discharge orifice.
  • such a secondary collector avoids the obligation to use an automobile air conditioning system of the type described above comprising a separate tank from the condenser.
  • a condenser of the type described above is equipped with at least one secondary refrigeration tube mounted horizontally for the purpose of placing the lower volume in the flow circuit with the evacuation pipe.
  • This configuration avoids the construction of an automobile air conditioning refrigeration system comprising a separate secondary cooler and offers general cooling performance better than that of a conventional condenser having an identical front contact zone for heat exchange with a coolant.
  • FIG. 1 the refrigeration system of automobile air conditioning is designated with the number 10 and shows, connected in series, a condenser 12, a tank 14, a thermostatic expansion valve 16, an evaporator 18, and a compressor 20.
  • the compressor 20 has the function of circulating the agent refrigerant through the system, whereby the refrigerant in gaseous form under high pressure is supplied to the condenser 12 through the pipe 22; the condenser dissipates the heat of the refrigerant gas and delivers liquid or a liquid / gas mixture cooled to the reservoir 14 by the pipe 24; the reservoir defines a gas / liquid interface and delivers the coolant to the regulator 16 through the line 26; the pressure reducer reduces the pressure of the coolant and supplies a gas / liquid mixture of lower pressure and temperature to the evaporator 18 via the line 28; and the evaporator absorbs the heat of an atmospheric fluid to be cooled and then delivers a low temperature / low pressure refrigerant gas to the compressor through the pipe 30.
  • the reservoir 14 can comprise a removable cartridge, not shown on the sketch, comprising a filter and a desiccant to dehydrate the coolant; this reservoir may have an internal configuration, namely compartments and / or equipment promoting liquid / gas separation, such as, for example centrifugal or baffle separators, for effecting the separation of the liquid and gaseous phases of the refrigerant in order to create a clear gas / liquid interface.
  • the tank should also normally be used to prevent a backflow of the refrigerant to the condenser 12, which would, in the case where the equipment does not provide, an adverse effect on its operation. It must also have a sufficient refrigerant reserve to cope with losses due to diffusion and small leaks.
  • FIG. 2 illustrates a condenser 32 for an automobile constructed in accordance with the present invention and adapted to replace the condenser 12 and the reservoir 14 of the refrigeration system of FIG. 1.
  • the condenser 32 is similar to the condenser 12 in that it comprises a primary or intake manifold 34 and a secondary or discharge manifold 36, generally vertical, or fluid boxes 34 and 36 to which are connected respectively a pipe 34a for the refrigerant inlet and a pipe 36a for evacuation of the refrigerant; and a bundle 38 of heat exchange tubes for placing the interior chambers 34b and 36b of the collectors 34 and 36 in the flow circuit.
  • the intake pipe 34a must be connected to the duct 22, the exhaust pipe 36a to the duct 26.
  • the condenser 32 is equipped with heat exchange fins 40 installed in association with the tubes 38 to participate in the transfer of heat between the condenser and the cooling agent, such as air for example , flowing normally at the front surface of the condenser as shown in Figure 2 and whose functions are the cooling and condensation of the gaseous refrigerant introduced into the intake pipe 34a.
  • the manifolds 34 and 36 primarily parallel to each other, are mounted vertically but can, if necessary, be tilted up to 60 ° from the vertical.
  • the primary collector 34 in accordance with known methods of manufacturing the condensers, must be constructed with a minimum internal cross-sectional area to maximize the burst strength of the collector for a given thickness of the metal used for its manufacture and which normally should not be larger than the area of the openings made in the side wall to insert the ends of the inlet pipes 38a of the tubes 38.
  • the condenser 32 deviates from known methods of manufacturing the condensers, in which the secondary collector 36 should receive an interior cross-sectional area equivalent to that of the primary collector 34, in the sense that the secondary collector is manufactured with an internal cross-sectional area. which is considerably larger than that required to adapt the insertion of the ends of the evacuation pipe 38b of the tubes 38. More specifically, the internal cross-sectional area of the secondary manifold 36 is large enough to allow the refrigerant gas to separate clearly from the refrigerant produced by the refrigerant gas passing through the tubes 38, thus delimiting an upper volume 42a formed essentially of gas and a lower volume 42b formed essentially of liquid, these volumes being separated by an interface 44.
  • the interface 44 cannot normally be horizontal nor be totally continuous under the conditions of e driving, due to the vertical and horizontal acceleration forces to which the condenser 32 is constantly subjected.
  • the chamber 36b of the secondary collector 36 is dimensioned internally so that the speed of the fluid flowing therein is reduced to the point that the gaseous phase can separate from the liquid phase under the influence of gravity and that it is not carried with the liquid phase to the evacuation pipe 36a, arriving thereby establishing and maintaining a clear separation between the liquid and gaseous phases of the refrigerant inside the secondary collector under normal conditions of use of the condenser; it is also sufficient for the evacuation pipe 36a to be connected in the lowest possible area of the volume 42b. The flow of refrigerant through the tubes 38 below the interface 44 is not then adversely affected.
  • the condensers currently used in automobiles can have heat transfer tubes with a cross section of which the transverse dimension can go down to 6.35 mm (0.25 inch), thus determining the internal cross-sectional areas of the primary and secondary manifolds. with which they are associated somewhat greater than 1.29 mm square (0.05 square inch).
  • the largest interior cross-sectional area known in the techniques prior to the invention is somewhat less than 25.39 mm square (1.0 square inch).
  • Multipath tubes 38 would subdivide this volume and only the most basic part of this subdivision is useful for gas / liquid separation. However, if the vertical space intended for the installation of the condenser allows it, it is possible to transform the condenser 32 into a multi-path condenser by mounting in series one or more additional heat exchange tubes, not shown on the Figure, between the inlet orifice 34a and the parallel tubes 38.
  • the shape of the tubes 38 can be of a conventional configuration and cannot, in any case, limit the application of the present invention.
  • the loading volume of the refrigerant of the system 10 be chosen so that, under the normal operating conditions adopted for the system, the lower volume 42b, containing for the most part of the coolant in liquid form, is constantly maintained inside the secondary collector 36.
  • FIG. 3 illustrates an air conditioning refrigeration system for a conventional automobile 10 ′, in which the components identical to system 10 receive the same figures assigned a premium (′).
  • the system 10 ′ differs from the system 10 by the addition of a secondary cooler 46 having an inlet orifice and an outlet orifice connected to the tank 14 ′ and to the regulator 16 ′ by the pipes 26a and 26b.
  • the secondary cooler 46 is normally separate from the condenser 12, but can be adjacent to it as shown in Figure 3.
  • Automotive air conditioning refrigeration systems using a secondary cooler 46 give higher performance levels, for a given 12,12 ′ condenser, a given 18,18 ′ evaporator and a given 20,20 ′ compressor, than the systems without secondary cooler, even if the refrigerant used to obtain secondary cooling is subsequently sent to the condenser or if the refrigerant is sent to the secondary cooler after passing through the condenser.
  • FIG. 4 illustrates a condenser 32 ′ for an automobile constructed according to the second application proposed in the present invention, and in which the components similar to those of the condenser 32 are designated by the same figures assigned a premium (′).
  • the design of the condenser 32 ′ differs from the design of the condenser 32 in that the primary manifolds and secondary 34 ′ and 36 ′ are provided with primary and secondary transverse partitions 50 and 52 which define the primary and secondary lower chambers 54 and 56, arranged respectively under chambers 34b and 36b; a first secondary cooling tube 58 is mounted under the lowest tube 38 ′ with its opposite ends in the flow circuit with the lower volume 42b ′ and the primary lower chamber; a second secondary cooling tube 60 is mounted under the first secondary cooling tube with its opposite ends in the flow circuit with the primary and secondary lower chambers; an outlet orifice 36a ′ is arranged in the secondary lower chamber for the flow of the liquid in the lower volume 42b ′ via the second cooling tube, the primary lower chamber and the first secondary cooling
  • the tubes 38 ′ are mounted in parallel with the secondary cooling tubes 58 and 60 which, themselves, are mounted in series.
  • the condenser 32 ′ can be modified, if desired, so as to present only a single secondary cooling tube 58 in which the orifice 36a ′ can be connected to the lower chamber 54, or so as to present one or more several additional lower chambers communicating in series with one or more additional secondary cooling tubes.
  • the tubes 38 ′ occupy at least 80% of the front surface of the condenser 32 ′ as shown in FIG. 4. A higher level of performance is obtained by using the condenser 32 ′, if we compare it to the condenser 32, even in the case where these condensers occupy the same front surface.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP90402372A 1989-09-01 1990-08-28 Verflüssiger mit Sammler/Nachkühler Expired - Lifetime EP0415840B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US401764 1989-09-01
US07/401,764 US4972683A (en) 1989-09-01 1989-09-01 Condenser with receiver/subcooler

Publications (2)

Publication Number Publication Date
EP0415840A1 true EP0415840A1 (de) 1991-03-06
EP0415840B1 EP0415840B1 (de) 1993-03-10

Family

ID=23589139

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90402372A Expired - Lifetime EP0415840B1 (de) 1989-09-01 1990-08-28 Verflüssiger mit Sammler/Nachkühler

Country Status (6)

Country Link
US (1) US4972683A (de)
EP (1) EP0415840B1 (de)
BR (1) BR9006901A (de)
CA (1) CA2037902A1 (de)
DE (1) DE69001055T2 (de)
WO (1) WO1991003692A1 (de)

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CN101978229B (zh) * 2008-10-20 2013-03-27 株式会社京滨冷暖科技 冷凝器
DE102011007216A1 (de) * 2011-04-12 2012-10-18 Behr Gmbh & Co. Kg Kältemittelkondensatorbaugruppe
EP2631566B1 (de) * 2012-02-24 2018-11-21 Airbus Operations GmbH Akkumulatoranordnung mit integriertem Unterkühler
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CN113776240A (zh) * 2021-09-28 2021-12-10 珠海格力电器股份有限公司 回热冷凝器和空气循环系统

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1748121A (en) * 1928-01-24 1930-02-25 Norman H Gay Condenser for refrigerating plants
GB362781A (en) * 1931-02-27 1931-12-10 Borsig Gmbh Condenser for refrigerating machines
US2028213A (en) * 1933-04-21 1936-01-21 Arthur R Hemphill Heat exchanger or cooler
US4201065A (en) * 1978-12-18 1980-05-06 Carrier Corporation Variable capacity vapor compression refrigeration system
NL8003452A (nl) * 1980-06-13 1982-01-04 Grasso Koninkl Maschf Windgekoelde condensor voor een koudemiddel.
DE3322474A1 (de) * 1983-06-22 1985-01-17 Linde Ag, 6200 Wiesbaden Verfahren zum betreiben eines kaeltemittelkreislaufs und kaeltemittelkreislauf zur durchfuehrung des verfahrens
EP0255313A2 (de) * 1986-07-29 1988-02-03 Showa Aluminum Kabushiki Kaisha Verflüssiger

Also Published As

Publication number Publication date
US4972683A (en) 1990-11-27
DE69001055D1 (de) 1993-04-15
EP0415840B1 (de) 1993-03-10
DE69001055T2 (de) 1993-06-17
CA2037902A1 (en) 1991-03-02
BR9006901A (pt) 1991-10-01
WO1991003692A1 (en) 1991-03-21

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