EP0415840A1 - Condenser with receiver/subcooler - Google Patents

Condenser with receiver/subcooler 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
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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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German (de)
French (fr)
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EP0415840B1 (en
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
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Valeo Engine Cooling Inc
Blackstone Corp
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Publication of EP0415840A1 publication Critical patent/EP0415840A1/en
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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)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un condenseur (32,32') pour automobile ayant un collecteur primaire (34,34') et un collecteur secondaire (36,36'), montés verticalement, en communication avec respectivement des canalisations d'admission et d'évacuation et des tubes généralement disposés horizontalement reliant ces collecteurs, dans lequel le collecteur secondaire (36,36') est dimensionné de façon telle que le gaz réfrigérant se sépare du liquide réfrigérant pour former un volume supérieur de gaz réfrigérant et un volume inférieur de liquide réfrigérant.The invention relates to a condenser (32,32 ') for a motor vehicle having a primary collector (34,34') and a secondary collector (36,36 '), mounted vertically, in communication with respectively inlet and outlet pipes. outlet and generally horizontally arranged tubes connecting these manifolds, in which the secondary manifold (36.36 ') is dimensioned so that the refrigerant gas separates from the refrigerant to form a higher volume of refrigerant gas and a lower volume of liquid refrigerant.

Description

Les systèmes de climatisation des automobiles du type à détendeur thermostatique peuvent avantageusement être doté d'un réservoir monté dans le circuit entre leur condenseur et ce détendeur offrant ainsi un volume de stockage suffisant à l'agent réfrigérant pour faire face aux variations inhérentes aux conditions de fonctionnement du système ainsi qu'aux pertes d'agents réfrigérants dues au phénomène de diffusion et aux petites fuites.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.

Pour qu'un tel réservoir soit efficace, il doit se trouver en aval du point où la condensation de l'agent réfrigérant se produit, il doit avoir une configuration interne offrant une capacité suffisante et/ou un dispositif intérieur centrifugeur ou à chicanes pour séparer les phases gazeuses des phases liquides de l'agent réfrigérant, il doit avoir un orifice de sortie de liquide placé de façon telle qu'il communique avec l'agent sous l'interface liquide/gaz, et il faut enfin que le système de climatisation soit rempli d'une quantité d'agent réfrigérant telle que l'interface liquide/gaz se trouve dans le volume intérieur offert par un tel réservoir lorsque le système fonctionne dans des conditions normales d'emploi.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.

Quand un système de climatisation pour automobile est équipé d'un réservoir et que le niveau de charge de l'agent réfrigérant du système est tel qu'il ne provoque pas le débordement de ce réservoir dans les conditions normales d'emploi, un condenseur classique, pour l'essentiel, produit un liquide réfrigérant avec un niveau de sous-refroidissement nul. Dans le cas où ce débordement de réservoir se produit, un condenseur classique peut fonctionner avec un niveau de sous-­refroidissement qui varie directement avec le volume de réfrigérant ayant débordé et avec les conditions de fonctionnement du système, mais il est souhaitable d'éviter réellement un tel sous-refroidissement parce qu'il a pour effet de réduire dans le condenseur le volume disponible pour la condensation de l'agent réfrigérant conduisant à des pressions plus élevées dans le condenseur et des performances moindres du système.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.

Les systèmes de climatisation des automobiles fonctionnant avec un réservoir et un niveau de remplissage d'agent réfrigérant fixé de telle façon que l'interface liquide/gaz soit maintenue à l'intérieur du réservoir dans des conditions normales d'emploi, peuvent fournir de meilleures performances, pour un matériel donné, lorsqu'on ajoute un refroidisseur secondaire indépendant installé dans le circuit entre le réservoir et le détendeur thermostatique. Cependant, les systèmes connus utilisant des refroidisseurs secondaires ont les inconvénients de coûter plus cher, d'être complexes et d'offrir des risques plus grands de fuites de agent réfrigérant.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. However, known systems using secondary coolers have the disadvantages of being more expensive, of being complex and of offering greater risks of refrigerant leakage.

La présente invention concerne un condenseur, destiné particulièrement au système de climatisation des automobiles, du type à détendeur thermostatique.The present invention relates to a condenser, particularly intended for the air conditioning system of automobiles, of the thermostatic expansion valve type.

Le condenseur pour automobile de le présente invention comprend un collecteur primaire et secondaire montés verticalement, communiquant avec des canalisations d'admission et d'évacuation et interconnectés par des tubes généralement disposés horizontalement, est caractérisé en ce que le collecteur secondaire est dimensionné pour permettre au gaz réfrigérant de se séparer du liquide réfrigérant de façon à offrir un espace pour le gaz réfrigérant dans sa partie supérieure et un espace pour le liquide réfrigérant dans sa partie inférieure mise en communication avec l'orifice d'évacuation.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.

Dans cette configuration et quand il est utilisé dans un système de refroidissement rempli d'une quantité d'agent réfrigérant telle que l'interface liquide/gaz se produise dans le volume formé par le collecteur secondaire, un tel collecteur secondaire permet d'éviter l'obligation d'utiliser un système de climatisation pour automobile du type décrit plus haut comprenant un réservoir distinct du condenseur.In this configuration and when used in a cooling system filled with a quantity of refrigerant such that the liquid / gas interface occurs in the volume formed by the manifold secondary, 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.

Dans une autre application de cette invention, un condenseur du type décrit plus haut est équipé d'au moins un tube de réfrigération secondaire monté horizontalement dans le but de placer le volume inférieur dans le circuit d'écoulement avec la canalisation d'évacuation.In another application of this invention, 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.

Cette configuration évite la construction d'un système de réfrigération de climatisation pour automobile comprenant un refroidisseur secondaire distinct et offre des performances générales de refroidissement meilleures que celles d'un condenseur classique présentant une zone frontale de contact identique pour l'échange de chaleur avec un agent de refroidissement.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.

La nature et le mode de fonctionnement de la présente invention sont maintenant explicités plus complètement dans les descriptions détaillées qui accompagnent les croquis ci-dessous :

  • - la figure 1 est un schéma fonctionnel d'un système classique de réfrigération de climatisation pour automobile ;
  • - la figure 2 est une vue du condenseur de la présente invention modifié pour remplir les fonctions du condenseur et du réservoir montrés dans la Figure 1 ;
  • - la figure 3 est un schéma fonctionnel d'un système classique de climatisation pour automobile employant un refroidisseur secondaire distinct ; et
  • - la figure 4 est une vue du condenseur d'une autre application de la présente invention dans laquelle il a été modifié pour remplir les fonctions de condenseur, de réservoir et de refroidisseur secondaire de la Figure 3.
The nature and mode of operation of the present invention are now explained more fully in the detailed descriptions which accompany the sketches below:
  • - Figure 1 is a block diagram of a conventional air conditioning refrigeration system for cars;
  • - Figure 2 is a view of the condenser of the present invention modified to fulfill the functions of the condenser and the tank shown in Figure 1;
  • - Figure 3 is a block diagram of a conventional automobile air conditioning system employing a separate secondary cooler; and
  • FIG. 4 is a view of the condenser of another application of the present invention in which it has been modified to fulfill the functions of condenser, reservoir and secondary cooler of FIG. 3.

On prendra pour référence d'abord la Figure 1, dans laquelle le système de réfrigération de climatisation pour automobile est désigné avec le chiffre 10 et montre , reliés en série, un condenseur 12, un réservoir 14, un détendeur thermostatique 16, un évaporateur 18, et un compresseur 20. Le compresseur 20 a pour fonction de faire circuler l'agent réfrigérant à travers le système, grâce à quoi l'agent réfrigérant sous forme gazeuse sous haute pression est fourni au condenseur 12 par la canalisation 22 ; le condenseur dissipe la chaleur du gaz réfrigérant et délivre du liquide ou un mélange liquide/gaz refroidi au réservoir 14 par la canalisation 24 ; le réservoir délimite une interface gaz/liquide et délivre le liquide réfrigérant au détendeur 16 par la canalisation 26 ; le détendeur réduit la pression du liquide réfrigérant et fournit un mélange gaz/liquide de pression et de température plus basses à l'évaporateur 18 par la canalisation 28 ; et l'évaporateur absorbe la chaleur d'un fluide atmosphérique à refroidir puis délivre un gaz réfrigérant basse température/basse pression au compresseur par la canalisation 30. Dans un système plus élaboré, le réservoir 14 peut comprendre une cartouche démontable, non montrée sur le croquis, comprenant un filtre et un desséchant pour déshydrater le liquide réfrigérant ; ce réservoir peut présenter un configuration interne, à savoir des compartiments et/ou des équipements favorisant la séparation liquide/gaz, comme, par exemple des séparateurs centrifugeurs ou à chicanes, pour effectuer la séparation des phases liquides et gazeuses de l'agent réfrigérant afin de réaliser une interface gaz/liquide bien nette. Le réservoir doit aussi normalement servir à empêcher un refoulement de l'agent réfrigérant vers le condenseur 12, ce qui aurait, dans le cas ou l'équipement ne le prévoit pas, un effet défavorable sur son fonctionnement. Il doit également présenter une réserve d'agent réfrigérant suffisante pour faire face aux pertes dues à la diffusion et aux petites fuites.Reference will first be made to Figure 1, in which 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. In a more elaborate system, 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.

La figure 2 illustre un condenseur 32 pour automobile construit conformément à la présente invention et adapté pour remplacer le condenseur 12 et le réservoir 14 du système de réfrigération de la Figure 1. Le condenseur 32 est semblable au condenseur 12 en ce sens qu'il comprend un collecteur primaire ou d'admission 34 et un collecteur secondaire ou d'évacuation 36, généralement verticaux, ou boîtes à fluide 34 et 36 sur lesquels sont raccordés respectivement une canalisation 34a d'admission de l'agent réfrigérant et une canalisation 36a d'évacuation de l'agent réfrigérant ; et un faisceau 38 de tubes d'échange de chaleur pour placer les chambres intérieures 34b et 36b des collecteurs 34 et 36 dans le circuit d'écoulement. La canalisation d'admission 34a devra être reliée au conduit 22, la canalisation d'évacuation 36a au conduit 26.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.

De même que dans un condenseur classique, le condenseur 32 est équipé d'ailettes 40 d'échange de chaleur installés en association avec les tubes 38 pour participer au transfert de chaleur entre le condenseur et l'agent refroidisseur, comme l'air par exemple, s'écoulant normalement à la surface frontale du condenseur comme le montre la figure 2 et dont les fonctions sont le refroidissement et la condensation du réfrigérant gazeux introduit dans la canalisation d'admission 34a. Les collecteurs 34 et 36 , au premier chef parallèles l'un à l'autre, sont montés verticalement mais peuvent, si cela est nécessaire, être inclinés jusqu'à 60° de la verticale.As in a conventional condenser, 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.

Le collecteur primaire 34, conformément aux procédés connus de fabrication des condenseurs, devra être construit avec une surface de section intérieure minimum pour maximiser la résistance à l'éclatement du collecteur pour une épaisseur donnée du métal utilisé pour sa fabrication et qui devrait normalement ne pas être plus grande que la surface des ouvertures pratiquées dans la paroi latérale pour y insérer les extrémités des canalisations d'admission 38a des tubes 38.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.

Le condenseur 32 s'écarte des procédés connus de fabrication des condenseurs, dans lesquels le collecteur secondaire 36 devrait recevoir une surface de section intérieure équivalente à celle du collecteur primaire 34, en ce sens que le collecteur secondaire est fabriqué avec une surface de section intérieure qui est nettement plus grande que celle requise pour adapter l'insertion des extrémités de canalisation d'évacuation 38b des tubes 38. Plus précisément, la surface de section intérieure du collecteur secondaire 36 est suffisamment grande pour permettre au gaz réfrigérant de se séparer nettement du liquide réfrigérant produit par le gaz réfrigérant passant par les tubes 38, délimitant ainsi un volume supérieur 42a formé essentiellement de gaz et un volume inférieur 42b formé essentiellement de liquide, ces volumes étant séparés par une interface 44. L'interface 44 ne saurait être normalement horizontale ni être totalement continue dans les conditions de la conduite automobile, en raison des forces d'accélération verticales et horizontales auxquelles est soumis constamment le condenseur 32. Pour que la présente invention assure un fonctionnement efficace, il suffit que la chambre 36b du collecteur secondaire 36 soit dimensionnée intérieurement pour que la vitesse du fluide qui s'y écoule soit réduite au point que la phase gazeuse puisse se séparer de la phase liquide sous l'influence de la gravité et qu'elle ne soit pas emportée avec la phase liquide vers la canalisation d'évacuation 36a, parvenant par là à établir et maintenir une séparation nette entre les phases liquides et gazeuses de l'agent réfrigérant à l'intérieur du collecteur secondaire dans les conditions normales d'emploi du condenseur ; il suffit également que la canalisation d'évacuation 36a soit raccordée dans la zone la plus base possible du volume 42b. L'écoulement du réfrigérant par les tubes 38 en-dessous de l'interface 44 n'est pas alors affecté de façon défavorable.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. For the present invention to ensure efficient operation, it suffices that 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.

Les condenseurs utilisés actuellement dans les automobiles peuvent avoir des tubes de transfert de chaleur avec une section dont la dimension transversale peut descendre jusqu'à 6,35 mm (0,25 inch), déterminant ainsi des surfaces de section intérieure des collecteurs primaires et secondaires avec lesquels ils sont associés quelque peu supérieures à 1,29 mm carré (0,05 inch carré). La plus grande surface de section intérieure connue dans les techniques antérieures à l'invention est quelque peu inférieure à 25,39 mm carré (1,0 inch carré). En comparaison, on envisage, par exemple, de donner à la section du collecteur secondaire 36 du condenseur 32 une surface plus grande que 31,74 mm carré (1,25 inch carré) environ. De plus, on envisage de donner au collecteur secondaire 36 une dimension verticale supérieure à 178 mm (7 inches), pour les systèmes de réfrigération ayant des vitesses d'écoulement maximum de 2,25 kg (5 livres) par minute ou plus.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). In comparison, it is envisaged, for example, to give the cross-section of the secondary collector 36 of the condenser 32 an area greater than approximately 31.74 mm square (1.25 square inch). In addition, it is contemplated to give the secondary manifold 36 a vertical dimension greater than 178 mm (7 inches), for refrigeration systems having maximum flow rates of 2.25 kg (5 pounds) per minute or more.

Il est préférable de monter tous les tubes 38 parallèlement entre eux pour maximiser la dimension verticale utilisable du volume de capacité du collecteur secondaire 36. Des tubes à parcours multiples 38 subdiviseraient ce volume et seule, la partie la plus base de cette subdivision est utile pour la séparation gaz/liquide. Cependant, si l'espace vertical destiné à l'installation du condenseur le permet, il est possible de transformer le condenseur 32 en un condenseur à parcours multiples en montant en série un ou plusieurs tubes d'échange de chaleur additionnels, non montrés sur la Figure, entre l'orifice d'admission 34a et les tubes parallèles 38. La forme des tubes 38 peut être d'une configuration classique et ne peut, en aucun cas, limiter l'application de la présente invention.It is preferable to mount all the tubes 38 parallel to each other to maximize the usable vertical dimension of the volume of capacity of the secondary collector 36. 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.

Il est essentiel, pour l'application de la présente invention, que le volume de chargement de l'agent réfrigérant du système 10 soit choisi de telle façon que, dans les conditions normales de fonctionnement retenues pour le système, le volume inférieur 42b, contenant pour l'essentiel de l'agent réfrigérant sous forme liquide, soit constamment maintenu à l'intérieur du collecteur secondaire 36.It is essential, for the application of the present invention, that 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.

La figure 3 illustre un système de réfrigération de climatisation pour automobile classique 10′, dans lequel les composants identiques au système 10 reçoivent les mêmes chiffres affectés d'un prime (′). Le système 10′ diffère du système 10 par l'adjonction d'un refroidisseur secondaire 46 ayant un orifice d'admission et un orifice d'évacuation reliés au réservoir 14′ et au détendeur 16′ par les canalisations 26a et 26b. Le refroidisseur secondaire 46 est normalement distinct du condenseur 12, mais peut y être adjacent comme le montre la Figure 3.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.

Les systèmes de réfrigération de climatisation pour automobile utilisant un refroidisseur secondaire 46 donnent des niveaux de performances plus élevés, pour un condenseur 12,12′donné, un évaporateur 18,18′donné et un compresseur 20,20′ donné, que les systèmes dépourvus de refroidisseur secondaire, même si l'agent réfrigérant utilisé pour obtenir le refroidissement secondaire est par la suite envoyé dans le condenseur ou si l'agent réfrigérant est envoyé dans le refroidisseur secondaire après avoir passé par le condenseur.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.

La figure 4 illustre un condenseur 32′pour automobile construit selon la seconde application proposée dans la présente invention, et dans laquelle les composants similaires à ceux du condenseur 32 sont désignés par les mêmes chiffres affectés d'un prime (′). Le dessin du condenseur 32′ diffère du dessin du condenseur 32 dans le fait que les collecteurs primaire et secondaire 34′ et 36′ sont pourvus de cloisons transversales primaire et secondaire 50 et 52 qui définissent les chambres basses primaire et secondaire 54 et 56, disposées respectivement sous les chambres 34b et 36b ; un premier tube de refroidissement secondaire 58 est monté sous le tube 38′ le plus bas avec ses extrémités opposées dans le circuit d'écoulement avec le volume inférieur 42b′ et la chambre basse primaire ; un second tube de refroidissement secondaire 60 est monté sous le premier tube de refroidissement secondaire avec ses extrémités opposées dans le circuit d'écoulement avec les chambres basses primaire et secondaire ; un orifice de sortie 36a′ est aménagé dans la chambre basse secondaire pour l'écoulement du liquide dans le volume inférieur 42b′ via le second tube de refroidissement, la chambre basse primaire et le premier tube de refroidissement secondaire.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 tube.

Dans la réalisation préférentielle actuellement décrite, les tubes 38′ sont montés en parallèle avec les tubes de refroidissement secondaire 58 et 60 qui, eux, sont montés en série.In the preferred embodiment currently described, the tubes 38 ′ are mounted in parallel with the secondary cooling tubes 58 and 60 which, themselves, are mounted in series.

Le condenseur 32′ peut être modifié, si on le souhaite, de façon à ne présenter qu'un seul tube de refroidissement secondaire 58 dans lequel l'orifice 36a′ peut être relié à la chambre basse 54, ou de façon à présenter une ou plusieurs chambres basses additionnelles communiquant en série avec un ou plusieurs tubes de refroidissement secondaires additionnels. Cependant, il est préférable, dans tous les cas, que les tubes 38′ occupent au moins 80% de la surface frontale du condenseur 32′ comme le montre la figure 4. Un niveau de performance supérieur est obtenu en utilisant le condenseur 32′, si on le compare au condenseur 32, même dans le cas ou ces condenseurs occupent la même surface frontale.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. However, it is preferable, in all cases, that 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.

Claims (10)

1) Condenseur comprenant un collecteur primaire (34′34′) et un collecteur secondaire (36,36′) montés généralement verticalement, un faisceau de tubes condenseurs généralement disposés horizontalement, au moins certains desdits tubes ayant leurs orifices d'admission raccordés audit collecteur primaire et leurs orifices d'évacuation raccordés audit collecteur secondaire pour former par ce moyen des chemins d'écoulement parallèles entre les collecteurs et une arrivée d'agent réfrigérant sous forme gazeuse communiquant avec lesdits orifices d'admission, caractérisé en ce que le collecteur secondaire (36,36′) est dimensionné pour permettre au gaz réfrigérant de se séparer de façon nette du liquide réfrigérant produit par ledit gaz réfrigérant passant par lesdits tubes et de créer ainsi un volume supérieur (42a, 42a′) de gaz réfrigérant et un volume inférieur (42b, 42b′) de liquide réfrigérant à l'intérieur dudit collecteur secondaire et un orifice d'évacuation (36a,36a′) de liquide réfrigérant en communication avec ledit volume inférieur.1) Condenser comprising a primary collector (34′34 ′) and a secondary collector (36,36 ′) mounted generally vertically, a bundle of condenser tubes generally arranged horizontally, at least some of said tubes having their inlet ports connected to said collector primary and their discharge orifices connected to said secondary manifold to thereby form parallel flow paths between the collectors and an inlet for refrigerant in gaseous form communicating with said intake orifices, characterized in that the secondary manifold (36.36 ′) is dimensioned to allow the refrigerant gas to separate cleanly from the refrigerant produced by said refrigerant gas passing through said tubes and thereby create an upper volume (42a, 42a ′) of refrigerant gas and a volume lower (42b, 42b ′) of coolant inside said secondary manifold and an orifi this discharge (36a, 36a ′) of coolant in communication with said lower volume. 2) Condenseur selon la revendication 1, caractérisé en ce que, au moins un desdits collecteurs délimite une chambre basse additionnelle (54,56), et en ce que la chambre secondaire (42b,42b′) dudit collecteur secondaire est dimensionnée pour permettre au gaz réfrigérant de se séparer de façon nette du liquide réfrigérant produit lorsque ledit gaz réfrigérant passe par lesdits tubes et pour constituer ainsi un volume supérieur de gaz réfrigérant et un volume inférieur de liquide réfrigérant à l'intérieur de ladite chambre secondaire et en ce qu'il est prévu un tube de refroidissement secondaire (58,60) plaçant ledit volume inférieur dans le circuit d'écoulement avec ladite chambre inférieure additionnelle, et un orifice d'évacuation (36a′) du liquide réfrigérant en communication avec ladite chambre inférieure additionnelle.2) Condenser according to claim 1, characterized in that, at least one of said collectors delimits an additional lower chamber (54,56), and in that the secondary chamber (42b, 42b ′) of said secondary collector is dimensioned to allow the refrigerant gas to separate cleanly from the coolant produced when said coolant gas passes through said tubes and thereby to constitute a larger volume of coolant gas and a lower volume of coolant inside said secondary chamber and in that there is provided a secondary cooling tube (58,60) placing said lower volume in the flow circuit with said additional lower chamber, and an orifice evacuation (36a ′) of the coolant in communication with said additional lower chamber. 3) Condenseur selon la revendication 2, caractérisé en ce que l'orifice d'évacuation (36a,36a′) dudit liquide réfrigérant communique avec ledit volume inférieur (42b′)par au moins un tube de réfrigération secondaire (58,60) disposé pour que son axe soit strictement parallèle auxdits certains tubes (38′).3) Condenser according to claim 2, characterized in that the discharge orifice (36a, 36a ′) of said coolant communicates with said lower volume (42b ′) by at least one secondary refrigeration tube (58,60) disposed so that its axis is strictly parallel to said certain tubes (38 ′). 4) Condenseur selon la revendication 2 ou 3, caractérisé en ce que, au moins un des tubes de réfrigération secondaire (58,60) est disposé pour que son axe soit strictement parallèle auxdits certains tubes (38′), et en ce que le collecteur primaire (34′) est divisé pour définir, par leur position relative, une chambre supérieure (34b) et une chambre inférieure (54), ladite chambre supérieure communiquant avec lesdits orifices d'admission, ledit premier tube de réfrigération secondaire (58) communiquant avec ledit volume inférieur (42b′) et ladite chambre inférieure (54) et l'orifice d'évacuation du collecteur secondaire (36′) du liquide réfrigérant communiquant avec ledit volume inférieur via ladite chambre inférieure et ledit premier tube de réfrigération secondaire.4) Condenser according to claim 2 or 3, characterized in that, at least one of the secondary refrigeration tubes (58,60) is arranged so that its axis is strictly parallel to said certain tubes (38 ′), and in that the primary manifold (34 ′) is divided to define, by their relative position, an upper chamber (34b) and a lower chamber (54), said upper chamber communicating with said intake ports, said first secondary refrigeration tube (58) communicating with said lower volume (42b ′) and said lower chamber (54) and the orifice for discharging the secondary collector (36 ′) of the coolant communicating with said lower volume via said lower chamber and said first secondary refrigeration tube. 5) Un condenseur selon l'une des revendications précédentes, caractérisé en ce que le collecteur secondaire (36′) est divisé pour délimiter, par leur position relative, une chambre supérieure contenant lesdits volumes supérieur et inférieur (42a′,42b′) et une chambre inférieure (56) reliée à ladite chambre inférieure (54) du collecteur primaire (34′) par un second tube de refroidissement secondaire (60), et en ce que l'orifice d'évacuation (36a′) du liquide réfrigérant communiquant avec ladite chambre inférieure dudit collecteur secondaire.5) A condenser according to one of the preceding claims, characterized in that the secondary collector (36 ′) is divided to delimit, by their relative position, an upper chamber containing said upper and lower volumes (42a ′, 42b ′) and a lower chamber (56) connected to said lower chamber (54) of the primary collector (34 ′) by a second secondary cooling tube (60), and in that the discharge orifice (36a ′) of the communicating coolant with said lower chamber of said secondary manifold. 6) Condenseur selon l'une des revendications 2 à 5, caractérisé en ce que la chambre additionnelle a une forme définie par ledit collecteur primaire.6) Condenser according to one of claims 2 to 5, characterized in that the additional chamber has a shape defined by said primary collector. 7) Condenseur selon l'une des revendications précédentes, caractérisé en ce que la chambre basse secondaire a une forme définie par ledit collecteur secondaire et en ce que l'orifice d'évacuation du liquide réfrigérant communique avec ladite chambre inférieure additionnelle par un circuit d'écoulement vers ladite chambre inférieure secondaire et en ce qu'un second tube refroidisseur secondaire relie ladite chambre inférieure secondaire à ladite chambre inférieure additionnelle.7) Condenser according to one of the preceding claims, characterized in that the secondary lower chamber has a shape defined by said secondary collector and in that the coolant discharge orifice communicates with said additional lower chamber by a circuit d flow to said secondary lower chamber and in that a second secondary cooling tube connects said secondary lower chamber to said additional lower chamber. 8) Système de climatisation pour automobile du type comprenant un condenseur, un détendeur (16,16′) thermostatique, un évaporateur (18,18′) et un compresseur (10,10′) installés en série sur un circuit d'écoulement, dans lequel le condenseur (32,32′) comprend des collecteurs primaire et secondaire (34,34′;36,36′) géneralement montés verticalement, un faisceau de tubes condenseurs disposés généralement horizontalement avec des orifices d'admission reliés audit collecteur primaire et des orifices d'évacuation reliés audit collecteur secondaire pour former des écoulement parallèles entre les deux collecteurs, une canalisation d'admission communiquant avec lesdits orifices d'admission pour y introduire le gaz réfrigérant provenant du compresseur, caractérisé en ce que le collecteur secondaire (36,36′) est dimensionné pour permettre au gaz réfrigérant de se séparer nettement du liquide réfrigérant produit lorsque le gaz réfrigérant passe dans lesdits tubes et de constituer ainsi un volume supérieur (42a,42a′) de gaz réfrigérant et un volume inférieur (42b,42b′) de liquide réfrigérant à l'intérieur dudit collecteur secondaire, et en ce qu'une canalisation d'évacuation (36a,36a′) communique avec ledit volume inférieur pour évacuer le liquide qui s'y trouve vers ledit détendeur.8) Air conditioning system for automobile of the type comprising a condenser, a thermostatic expansion valve (16,16 ′), an evaporator (18,18 ′) and a compressor (10,10 ′) installed in series on a flow circuit, in which the condenser (32.32 ′) comprises primary and secondary collectors (34.34 ′; 36.36 ′) generally mounted vertically, a bundle of condenser tubes generally arranged horizontally with inlet ports connected to said primary manifold and discharge orifices connected to said secondary manifold to form parallel flows between the two collectors, an intake pipe communicating with said intake orifices to introduce therein the refrigerant gas coming from the compressor, characterized in that the secondary manifold (36 , 36 ′) is sized to allow the refrigerant gas to separate clearly from the refrigerant produced when the refrigerant gas passes through said tubes and thus constitute an upper volume (42a, 42a ′) of refrigerant gas and a lower volume (42b, 42b ′) of refrigerant liquid inside said secondary manifold, and in that an evacuation pipe (36a , 36a ′) communicates with said lower volume to evacuate the liquid therein towards said regulator. 9) Système selon la revendication 8, caractérisé en ce que, au moins un premier tube de refroidissement secondaire (58) est monté strictement parallèlement auxdits tubes, provenant de fait que le collecteur principal (34,34′) est divisé pour définir, par leur position relative, une chambre supérieure et une chambre inférieure, ladite chambre supérieure communiquant avec lesdits orifices d'admission, ledit tube de refroidissement secondaire communiquant avec ledit volume inférieur et ladite chambre inférieure et lesdites canalisations d'évacuation communiquant avec ledit volume inférieur via ladite chambre inférieure et ledit premier tube de refroidissement secondaire.9) System according to claim 8, characterized in that at least a first secondary cooling tube (58) is mounted strictly parallel to said tubes, coming from the fact that the main collector (34,34 ′) is divided to define, by their relative position, an upper chamber and a lower chamber, said upper chamber communicating with said intake orifices, said secondary cooling tube communicating with said lower volume and said lower chamber and said evacuation pipes communicating with said lower volume via said lower chamber and said first secondary cooling tube. 10) Système selon la revendication 9, caractérisé en ce que le collecteur secondaire (36′) est divisé de façon à définir, par leur position relative, une chambre supérieure comprenant les volumes supérieur (42a′) et inférieur (42b′) et une chambre inférieure (56), provenant du fait qu'il est connecté à ladite chambre inférieure dudit collecteur principal par un second tube de refroidissement secondaire (60) et que lesdites canalisations d'évacuation communiquent avec ladite seconde chambre dudit collecteur secondaire.10) System according to claim 9, characterized in that the secondary collector (36 ′) is divided so as to define, by their relative position, an upper chamber comprising the upper (42a ′) and lower (42b ′) volumes and a lower chamber (56), originating from the fact that it is connected to said lower chamber of said main collector by a second secondary cooling tube (60) and that said discharge pipes communicate with said second chamber of said secondary collector.
EP90402372A 1989-09-01 1990-08-28 Condenser with receiver/subcooler Expired - Lifetime EP0415840B1 (en)

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)

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EP0415840A1 true EP0415840A1 (en) 1991-03-06
EP0415840B1 EP0415840B1 (en) 1993-03-10

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ID=23589139

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US (1) US4972683A (en)
EP (1) EP0415840B1 (en)
BR (1) BR9006901A (en)
CA (1) CA2037902A1 (en)
DE (1) DE69001055T2 (en)
WO (1) WO1991003692A1 (en)

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Also Published As

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

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