EP2997318B1 - Condenseur - Google Patents

Condenseur Download PDF

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Publication number
EP2997318B1
EP2997318B1 EP14723838.0A EP14723838A EP2997318B1 EP 2997318 B1 EP2997318 B1 EP 2997318B1 EP 14723838 A EP14723838 A EP 14723838A EP 2997318 B1 EP2997318 B1 EP 2997318B1
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EP
European Patent Office
Prior art keywords
condenser
tube
region
flow channel
refrigerant
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.)
Active
Application number
EP14723838.0A
Other languages
German (de)
English (en)
Other versions
EP2997318A1 (fr
Inventor
Helmut EIBNER
Klaus FÖRSTER
Uwe FÖRSTER
Andreas Dränkow
Martin Kaspar
Christoph Kästle
Thomas Mager
Herbert Hofmann
Markus Pflieger
Holger STRIEGE
Christoph Walter
David Mayor Tonda
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.)
Mahle International GmbH
Original Assignee
Mahle International GmbH
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Filing date
Publication date
Application filed by Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP2997318A1 publication Critical patent/EP2997318A1/fr
Application granted granted Critical
Publication of EP2997318B1 publication Critical patent/EP2997318B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B39/00—Evaporators; 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
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • 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
    • 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
    • F25B2339/0444—Condensers with an integrated receiver where the flow of refrigerant through the condenser receiver is split into two or more flows, each flow following a different path through the condenser 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/007—Condensers
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0073—Gas coolers
    • 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

  • the invention relates to a condenser in a stacked disk design, with a first flow channel for a refrigerant and with a second flow channel for a coolant according to claim 1.
  • Condensers are used in refrigeration circuits of automotive air conditioning systems to cool and condense the refrigerant to the condensation temperature.
  • Capacitors can have a collector which holds a volume of refrigerant. Volume fluctuations in the refrigerant circuit can be compensated for via this volume of refrigerant.
  • the collector is usually arranged on the capacitor. It is flowed through by the refrigerant, which has already flowed through part of the condenser. After flowing through the collector, the refrigerant is returned to the condenser and subcooled in a subcooling below the condensation temperature.
  • the refrigerant for this purpose is led out of the condenser from one of the manifolds arranged at the side of the tube-rib block and introduced into the collector.
  • the collector may be attached to the disk stack as an additional layer in the form of disk elements.
  • solutions are known in which the refrigerant is led out of the stacked-disc condenser via a special distributor plate and fed to an external collector. After flowing through the collector, the refrigerant is returned to the condenser.
  • US 2009/071189 A1 discloses a capacitor according to the preamble of claim 1.
  • a disadvantage of the solutions of the prior art is in particular that an integration of capacitors, collectors and subcoolers is associated with great effort.
  • the known from the prior art capacitors are characterized by a complex structure and increased manufacturing costs. This results in additional costs that make the use of such capacitors unattractive.
  • the object of the present invention to provide a condenser suitable for condenser, storage and further subcooling refrigerant, the condenser being characterized by a simple structure and compact design and inexpensive to manufacture.
  • the object of the present invention is achieved by a capacitor in stacking disk construction with the features of claim 1.
  • the invention relates to a capacitor in a stacked disk design, comprising a first flow channel for a refrigerant and a second flow channel for a coolant, wherein a plurality of disc elements is provided, which form stacked adjacent channels between the disc elements, wherein a first number of channels the a first number of channels is associated with the second flow channel, wherein the first flow channel has a first area for desuperheating and condensation of the vapor refrigerant and a second area for subcooling the condensed refrigerant, with a collector for storing a refrigerant, wherein a refrigerant transfer from the first region leads into the second region through the collector, wherein the collector via a first connection element, which forms a first fluid port of the collector, with the first Bere I am in fluid communication, wherein the collector is in fluid communication with the second region via a second connection element, which forms a second fluid connection of the collector, wherein the first connection element and / or the second connection element are formed by a tube which passes through
  • a collector in the refrigerant circuit In order to keep the volume of refrigerant in the refrigerant circuit constant and the refrigerant in addition to drying and / or to filter, it is advantageous to integrate a collector in the refrigerant circuit. This is advantageously integrated at a point in the flow channel of the refrigerant, to which the refrigerant is already fully condensed, but not yet undercooled.
  • the condenser may be formed outside the condenser by a stack of discs consisting predominantly of identical disc elements, despite the arrangement of the header.
  • the tube is guided through a series of adjacent disc elements.
  • the tube is preferably guided through the openings of the disc elements.
  • the tube is thereby introduced into the disc stack such that it opens into one of the channels, which is assigned to the desired flow channel.
  • a channel of the first flow channel In the present case a channel of the first flow channel.
  • the first connection element is designed as a tube and the tube leads from the second region through the first region to a fluid connection of the collector, wherein the tube is in fluid communication with the second region of the first flow channel and the collector.
  • the collector is connected directly to the Enthitzungs Scheme and the condensation region.
  • This first region of the condenser viewed in the flow direction of the refrigerant, is located in front of the second region in which the subcooling takes place.
  • the tube In order to direct the entire refrigerant from the second region of the first flow channel into or out of the collector, the tube is dimensioned so that it passes through all the disk elements of the first region and opens into a channel of the second region. This way the refrigerant gets pass the first area directly into the collector or out of the collector.
  • At least one of the tubes has a taper and / or a shoulder and / or an at least partially encircling flange and / or a widening, by means of which it can be supported on one of the disc elements and fixed in the condenser.
  • a flange can be produced for example by upsetting, alternatively, the flange can also be designed as a separate component, which is attached to a pipe.
  • the flange serves to support against one or more of the disc elements and contributes to a better seal.
  • a taper can be provided on one of the tubes, with which the tube can be inserted into an opening.
  • a taper can be generated for example by a pressing or by a machining.
  • An expansion can be generated for example by a hydroforming process.
  • a pipe can be supported particularly advantageously on the disk elements of the capacitor and fixed in the capacitor.
  • the elements described above can serve in particular as a stop.
  • At least one of the disk elements is designed as a separating disk and / or one of the disk elements as a deflecting disk.
  • a cutting disk differs essentially from a deflection disk in that the openings in the respective disk element, over which the channel formed between the disks is in fluid communication with an adjacent channel, are provided at different locations. Otherwise, the two disc elements may have a very similar or identical structure. The different arrangement of the openings can for example be achieved by a side-by-side juxtaposition of the disc elements.
  • a deflection disk is characterized in particular by the fact that it provides no opening with respect to the opening of the adjacent cutting disk, which allows an inflow of a fluid into one of the flow channels, and thus deflects or deflects the inflowing fluid within the channel.
  • the tube is supported in the condenser on a deflection plate.
  • the tube has radial and / or axial openings.
  • radial openings are provided through which a fluid can flow out of the pipe or into the pipe.
  • the radial openings may be formed for example by holes, slots or other recesses.
  • the openings are advantageously located at one of the end portions of the tube to create a defined overflow from the tube into one or more of the flow channels.
  • the tube is supported on one of the outer disc elements of the second region.
  • an outer disk element is meant here in particular one of the disk elements, which closes off the second area, which is formed from a stack of a plurality of disk elements, to an adjacent area.
  • a second tube is provided at the fluid inlet and / or at the fluid outlet of the first flow channel, which is in fluid communication with another channel of the first flow channel.
  • a third tube is provided at the fluid inlet and / or at the fluid outlet of the second flow channel, which is in fluid communication with another channel of the second flow channel.
  • the fluid flowing through the corresponding flow channel can be guided past adjacent channels and thus introduced or discharged into or out of a predetermined channel. It can thereby be achieved a design of the capacitor, which has both the fluid inlet and the fluid outlet of the respective flow channel at a common end region.
  • the other channel is one of the last channels of the respective flow channel, which is the insertion side of the tube in the disc stack substantially opposite.
  • the refrigerant or the coolant flows through the entire condenser or the flow path provided within the condenser, before it flows back through the pipe through the entire condenser and at the same end region of the disk stack, in which it Slice stack has flowed, also flows out again.
  • the disc elements have openings with or without passage.
  • the at least one tube is guided through the openings in the disc elements and is soldered to at least a part of the disc elements, in particular the passages.
  • the tubes By inserting the tubes into the openings and soldering the tubes with the disc elements and in particular with the passages, a compact unit is achieved, which is characterized by a high strength.
  • the tubes can be soldered to the disc stack in a single operation here. This is particularly advantageous, in particular with regard to an optimized production process.
  • At least one of the tubes has an at least partially circumferential flange, via which it can be supported on one of the disc elements.
  • a flange can be generated as by upsetting, alternatively, the flange can also be designed as a separate component, which is attached to a pipe becomes.
  • the flange serves to support against one or more of the disc elements and contributes to a better seal.
  • a preferred embodiment is characterized in that at least one of the tubes is chamfered at one end region or at both end regions.
  • a bevelled pipe is advantageously produced by a section through the pipe along a plane which is at a predeterminable angle to the central axis of the pipe. This results in a sweep of the tube.
  • a tapered tube can be achieved, that the tube with the resulting tip on a stop surface, in particular on a disc element, can be supported within the capacitor and at the same time a fluid can flow into the tube.
  • At least one of the tubes has a flexible region, wherein the tube can be compressed and / or stretched in the axial direction by the flexible region.
  • a change in length of the capacitor can be compensated.
  • a so-called settling occurs in the capacitor. This settlement is caused by a relative movement of the disc elements to each other during the soldering process.
  • a flexible region in the tubes can thus prevent the occurrence of voltages within the capacitor.
  • the flexible area can accommodate both compression due to settlement operations as well as stretching due to other mechanical or thermal influences.
  • the flexible region is formed by a concertina-like design of the tube.
  • the flexible region makes it possible to absorb compressions and / or strains in a particularly simple manner.
  • the flexible area is formed by folded material areas, which are moved towards each other in the event of compression and are moved away from each other in case of an expansion.
  • the tube can be designed such that a compression or elongation can be absorbed once or several times.
  • the flexible region is formed from an elastic material, such as plastic or rubber, wherein a compression or expansion of the tube in the axial direction and / or in the radial direction is reversible.
  • An embodiment of the flexible body of a material, such as plastic or rubber is particularly advantageous to allow a reversible deformation of the tube.
  • Plastics and rubber have a much higher formability to change than metallic materials.
  • At least one of the tubes is formed from a plurality of tube sections, wherein the tube sections are connected to one another in a fluid-tight manner.
  • a tube which is formed from a plurality of pipe sections, can particularly advantageously represent a length compensation. This can be achieved by the pipe sections perform a relative movement to each other.
  • the pipe sections are inserted into one another, wherein a pipe section has a smaller outer diameter than the inner diameter of the respective other pipe section.
  • a fluid-tight connection of the respective pipe sections with each other is particularly advantageous in order to produce no unwanted mixing of the fluid streams within the capacitor.
  • Such a pipe construction is particularly suitable for compensating for the changes in length that occur during soldering of the disk stack.
  • the effect of heat can lead to so-called setting processes during soldering, as a result of which the individual disk elements at least partially slide into one another.
  • This change in length can be compensated advantageously by a multi-part tube.
  • the pipe sections are then advantageously also soldered together, so that a relative movement of the sections is prevented from each other. In this way, the fluid tightness of the tube can be generated in a simple manner.
  • a first pipe section tapers in a funnel shape in the axial direction and the second pipe section widens in a funnel shape in the axial direction, wherein the two pipe sections are inserted into one another such that the relative movement between the second pipe section and the first pipe section by a striking of the widening area is limited at the tapered area.
  • the first pipe section has an inner diameter which is sufficiently large so that the second pipe section can be moved within the first pipe section.
  • the tube is received in a connection element and is connected to this fluid-tight.
  • connection element can be formed, for example, by a flange on the condenser or on the collector.
  • the second region has a plurality of flow paths through which the refrigerant can flow, wherein the flow paths are each formed by individual channels of the first flow channel and / or are formed by subregions of individual channels of the first flow channel.
  • a plurality of flow paths for guiding the refrigerant in the second region of the first flow channel is advantageous in order to achieve improved heat transfer between the refrigerant and the coolant.
  • the flow paths can be formed by channels, which are formed between adjacent disc elements, or by subregions of these channels.
  • release agents may be provided in the channels, whereby the channels are subdivided into subregions.
  • the individual flow paths can be flowed through in parallel or in series by the refrigerant.
  • a flow of the refrigerant can be achieved in cocurrent and / or in countercurrent with the coolant.
  • the second region has a plurality of channels, wherein at least individual channels of the second region are in thermal contact with the second flow channel, wherein the coolant and the refrigerant flow in cocurrent and / or countercurrent to each other through the channels of the the second region and the second flow channel are flowable.
  • a flow of refrigerant and coolant in a plurality of mutually adjacent channels is particularly advantageous in order to realize the largest possible heat transfer can.
  • a particularly large heat transfer can be achieved in particular by a counterflow arrangement.
  • a mixed arrangement of passages in countercurrent and passages in the DC or a pure DC arrangement may be advantageous.
  • the channels forming the first flow channel can be flowed through by the refrigerant in series and / or in parallel.
  • the channels forming the second flow channel can be flowed through by the coolant in series and / or in parallel.
  • advantages can be achieved in the heat transfer to be achieved.
  • a targeted influencing of the flow direction of the first and the second flow channel a continuous flow in countercurrent of the refrigerant and the coolant can be achieved.
  • the second flow channel can be flowed through in series and a fluid inlet and a fluid outlet of the second flow channel are each arranged at the same end region of the disk stack.
  • the condenser By arranging the fluid inlet and the fluid outlet at the same end region of the disk stack, the condenser can be designed to be particularly compact.
  • the first region or the second region of the first flow channel with a third flow channel forms an internal heat exchanger in stacked disk design, wherein the first and the third flow channel can be flowed through by a refrigerant.
  • the subcooling path of the second region is at least partially replaced in one embodiment by an internal heat exchanger.
  • the subcooling of the refrigerant does not take place here by a heat transfer between the refrigerant and the coolant.
  • the cooling of the refrigerant in the condenser can be amplified once again, which leads to an overall higher performance of the condenser.
  • refrigerant flows in two different flow channels, which are aligned such that a heat transfer between the fluids in the flow channels is made possible.
  • the fluids flow in countercurrent to each other.
  • the refrigerant which flows in the two flow channels, is supplied to the inner heat exchanger from different sections of the refrigerant circuit, whereby the largest possible temperature difference between the fluids in the two flow channels is achieved.
  • the third flow channel can be supplied with a coolant independently of the first flow channel or with a coolant independently of the second flow channel.
  • the independent supply of the third flow channel with either a coolant or a refrigerant is particularly advantageous because in this way a higher temperature difference between the third flow channel and the first flow channel can be achieved. This applies in particular when an additionally cooled fluid is supplied to the third flow channel.
  • the collector is in fluid communication with the second portion of the first flow passage via a pipe leading through a portion of the disk stack forming the fluid inlet into the accumulator, and the fluid outlet of the accumulator is formed via another pipe which passes through a portion of the disk stack and is in fluid communication only with the first portion of the first flow channel.
  • the collector can be placed outside the disk stack and at the same time the simple construction of the disk stack can be achieved by using many identical disk elements.
  • the tubes are guided by the disc elements of the portions of the disc stack, with which they are not supposed to be in fluid communication, and then open into the channels of the disc stack, with which they are in fluid communication.
  • a further preferred embodiment of the invention provides that the fluid inlet and / or the fluid outlet of the internal heat exchanger are formed by a tube.
  • connection of the inner heat exchanger via one or two tubes is advantageous because in this way the simple structure of the disk stack stack of the capacitor can be maintained.
  • the refrigerant, which flows through the third flow channel of the inner heat exchanger can be selectively guided through a pipe into a channel of the third flow channel and also be selectively led out of a channel of the third flow channel.
  • first connection element is a tube and the second connection element is a flange or vice versa.
  • an advantageous connection of the collector to the condenser can be achieved.
  • a very stable connection can be achieved by means of a flange, while the tube can be used to selectively supply the fluid into the condenser.
  • the collector is designed for filtering and / or drying the refrigerant.
  • the collector advantageously also implements the function of drying the refrigerant via suitable means for drying and further the filtering of the refrigerant. In this way, the excess moisture can be removed from the refrigerant and it can be further freed of impurities.
  • the integration of these functions in a single component is particularly advantageous in terms of the variety of parts and the space utilization.
  • FIGS. 1 to 8 different embodiments of a capacitor 1, 1a, 70, 80 are shown in stacked disk design. These are capacitors 1, 1a, 70, 80 for use in an air conditioning system for motor vehicles. All shown capacitors 1, 1a, 70, 80 are formed of a plurality of disk elements stacked on each other to form a disk stack 11, 11a, 73, 93.
  • the essential advantage of the construction as a condenser 1, 1a, 70, 80 in stacked disk design is that the disk elements are largely identical and only the outer terminal plates and individual, built in the stack deflecting or blocking plates, which deflect or block the inner flow channels, differ from the basically identical shape of the disc elements. This allows a low-cost and easy production.
  • the capacitors 1, 1a, 70, 80 are indicated only by a schematic diagram.
  • the individual portions of the capacitors 1, 1a, 70, 80, such as the Enthitzungs Society 3, 72, 81 or the subcooling 4, 71, 82 and the Area of an internal heat exchanger 88 are shown in the figures only as cuboidal elements.
  • Each of these cuboid elements actually consists of a plurality of disc elements. These disk elements are stacked on top of one another and, by means of a special arrangement of openings which may have passages, form a multiplicity of individual channels which, due to the design of the individual disk elements, are combined to form flow channels which carry either a coolant or a refrigerant.
  • the flow channels of the coolant and the flow channels of the refrigerant are arranged adjacent to each other.
  • channels for the refrigerant and channels for the coolant are arranged in an equally distributed alternating sequence.
  • the alternating rhythm between coolant channels and refrigerant channels can be realized deviating from a ratio of 1: 1.
  • FIGS. 1 to 8 The flow channels of the coolant and the refrigerant are in the FIGS. 1 to 8 also indicated only schematically. Each of the cuboidal elements is in the FIGS. 1 to 8 flows through only once from a refrigerant passage or a coolant channel. This illustration is intended to illustrate only the flow principle of the individual capacitors 1, 1a, 70, 80 and has no delimiting or restrictive effect.
  • the flow channels of the refrigerant 25, 25a, 52, 60, 87 are each represented by a dotted line.
  • the flow channels of the coolant 26, 26a, 32, 42, 52, 85 are each represented by a continuous line.
  • FIGS. 1 to 8 shown flow directions of the refrigerant and the coolant are each only one example and can also counter to those in the FIGS. 1 to 8 be executed directions shown.
  • the FIG. 1 shows a condenser 1, which consists of a Enthitzungs Scheme 3 and a subcooling 4.
  • the Enthitzungs Scheme 3 is used for desuperheating a refrigerant and the condensation of the refrigerant from its vapor phase into a liquid phase.
  • a coolant which also flows through the Enthitzungs Scheme 3.
  • a subcooling section 4 is connected at the top of the decarburization section 3.
  • the completely liquid refrigerant is further cooled below the condensation temperature by a further thermal exchange with a coolant.
  • a collector 2 is arranged, which is flowed through by the refrigerant.
  • the task of the collector 2 is to store, filter and dry the refrigerant.
  • the collector 2 has at its fluid outlet 12 a tube 5, which is guided through the Enthitzungs Scheme 3 and is in the subcooling 4 with the flow channel 25 of the refrigerant in fluid communication.
  • the fluid inlet 6 of the collector 2 is in turn in fluid communication with the flow channel 25 of the refrigerant in the decompression region 3.
  • the collector 2 After flowing through the collector 2, the refrigerant is passed completely into the subcooling region 4.
  • the collector 2 thus represents the passage of fluid from the decompression area 3 into the subcooling area 4.
  • openings 8, 9, 10 are arranged. These can represent fluid inlets as well as fluid outlets, depending on the design of the inner flow channels. Also shown at the lower end of the disk stack 11 is an opening 7, which may also be a fluid inlet or a fluid outlet, depending on the design of the inner flow channels.
  • flow channels 25, 26 are shown for a refrigerant and a coolant.
  • the refrigerant flows through the arranged at the lower end portion of the disk stack 11 fluid inlet 7 in the Enthitzungs Scheme 3 of the condenser 1. There it flows through the channels formed by the disc elements, which are associated with the flow channel 25 of the refrigerant.
  • the refrigerant flows through the fluid inlet 6 into the collector 2 into it. There it flows through the collector 2 for the purpose of storage, filtration and drying and then flows through the fluid outlet 12 through the tube 5 into the subcooling region 4 of the condenser 1. After flowing through the subcooling region 4, the refrigerant flows through the fluid outlet 8 at the upper end region the capacitor 1 addition.
  • the coolant flows through the fluid inlet 9 at the upper end region of the condenser 1 into the subcooling region 4.
  • the coolant flows through the individual channels of the subcooling region 4 and of the de-icing region 3 in parallel.
  • the coolant flows through inner openings from top to bottom through the disk stack 11 and is distributed over the width of the capacitor 1.
  • the coolant After the coolant has flowed over the entire width of the capacitor 1, it then flows through a plurality of openings in the disk elements of down to the top through the fluid outlet 10 from the condenser 1.
  • FIG. 2 shows a similar structure, as it already in the FIG. 1 was presented.
  • the flow channel 25 of the refrigerant is analogous to FIG. 1 through the condenser 1 of FIG. 2 arranged. Deviating from FIG. 1 the coolant flows in FIG. 2 now no longer in parallel through the channels of the condenser 1, but flows through the condenser 1 as well as the refrigerant in series.
  • the coolant flows through the fluid inlet 30 at the upper region of the condenser 1 into the subcooling region 4. There it is distributed over the width of the condenser 1 and flows via an inner opening down into another channel of the subcooling region 4. There, the coolant spreads again over the entire width before it flows through a further opening down into the Enthitzungs Scheme 3. Finally, after a redistribution over the width of the condenser 1, the coolant flows out of the condenser 1 through the fluid outlet 31 at the lower end region.
  • the flow channel 32 of the coolant extends in the FIG. 2 as well as the flow channel 25 of the refrigerant in series through the individual channels in the interior of the condenser 1.
  • the refrigerant flow over the entire condenser 1 is in countercurrent to the coolant flow.
  • FIG. 3 shows a capacitor 1 analogous to Figures 1 and 2
  • the refrigerant flow channel 25 is analogous to Figures 1 and 2 executed.
  • the flow channel 42 of the coolant is disposed within the capacitor 1, that both arise areas that are traversed in parallel, as well as areas that are flowed through serially.
  • the coolant flows through the fluid inlet 40 into the subcooling region 4 of the condenser 1. There it is distributed over both the width of the capacitor 1, as well as down through inner openings within the subcooling 4. The subcooling 4 is thereby completely flows through in parallel. The coolant then flows through openings from the subcooling region 4 into the desuperheating region 3. From there, the coolant flows out of the condenser 1 via the fluid outlet 41.
  • the Enthitzungs Scheme 3 is only flows through serially.
  • the condenser 1 is partially flowed through in parallel and partially in series by the coolant. This results in areas in which the refrigerant flows in countercurrent with the refrigerant and areas in which the refrigerant flows with the refrigerant in the DC.
  • FIG. 4 also shows a capacitor 1 analogous to the embodiments of FIGS. 1 to 3 ,
  • the flow channel 25 of the refrigerant is unchanged from the FIGS. 1 to 3 , Notwithstanding the preceding figures, the coolant is now passed completely in series through the condenser 1.
  • the coolant flows through the fluid inlet 50 into the condenser 1 and out of the condenser 1 via the fluid outlet 51.
  • Fluid inlet 50 and fluid outlet 51 lie in this case at a common end region of the condenser 1.
  • the coolant flows into the subcooling region 4 and is distributed over the width of the condenser 1. It then flows through openings into an underlying part of the subcooling region 4 and likewise distributes itself again over the entire width of the condenser. It then passes through openings in the interior of the condenser 1 in the Enthitzungs Scheme 3. After being distributed across the width of the condenser 1, the coolant flows out of the condenser 1 through the tube 53 via the fluid outlet 51.
  • the tube 53 is in fluid communication with one of the channels of the second flow channel 52. Through the pipe 53, the coolant can be led out of the Enthitzungs Scheme 3 through the entire sub-cooling region 4 from the condenser 1, without it can come to a thorough mixing of the refrigerant with the refrigerant.
  • the coolant thus flows completely serially through the regions 3 and 4 of the condenser 1.
  • the coolant flowing in the flow channel 52 therefore flows countercurrently to the refrigerant in the flow channel 25 at all times.
  • FIG. 5 shows a condenser 1.
  • the course and orientation of the coolant channel 26 correspond to that in FIG. 1 already shown course.
  • the course of the refrigerant channel 60 corresponds in many parts also the course of the flow channel 25 of FIG. 1 ,
  • the fluid inlet 61 is now likewise arranged at the upper end region of the condenser 1, as is the fluid outlet 62.
  • the condenser 1 has a tube 63 which connects a channel of the de-icing area 3 with the fluid inlet 61.
  • the refrigerant therefore flows through the pipe 63 into the Enthitzungs Scheme 3 and from there as already described in the preceding figures serially through the individual channels of the first flow channel in the Enthitzungs Scheme 3 and in the subcooling. 4
  • FIG. 6 shows a further view of a capacitor 1a, as in the previous FIGS. 1 to 5 .
  • the condenser 1a now has a further subcooling path.
  • the subcooling area 4a is thus larger and has more channels than the subcooling area 4 of the previous ones FIGS. 1 to 5 ,
  • the flow guide of the first flow passage 25a, through which the refrigerant flows, is completely serial.
  • the flow guide of the second flow channel 26a is completely parallel.
  • the positioning of the fluid outlet 8a is compared to the arrangement of Fluid outlet 8 of FIG. 1 changed.
  • the fluid outlet 8a is arranged, in contrast to FIG. 1, on the opposite side of the condenser 1a.
  • the fluid inlet 7 and the fluid outlet 8a are in common alignment.
  • the number of channels associated with the first flow channel 25a and the second flow channel 26a depends mainly on the number of disk elements used in the disk stack 11a. There is always a higher number or a lower number predictable.
  • the embodiments shown here have no limiting character in this regard.
  • FIG. 7 shows an embodiment of a capacitor 70, wherein the subcooling region 71 is represented by two cuboidal elements.
  • the Enthitzungs Society 72 is different from the versions of FIGS. 1 to 6 represented by 3 cuboidal elements.
  • An increase or decrease in the number of cuboid elements can be achieved by changing the number of disk elements in the disk stack 73.
  • FIG. 8 shows a capacitor 80 with a Enthitzungs Scheme 81 at the lower end of the capacitor 80 and two overlying subcooling regions 82.
  • the capacitor 80 is substantially formed by the disk stack 93.
  • Both the subcooling region 82 and the de-icing region 81 are flowed through in parallel by the coolant.
  • Both the fluid inlet 83 and the fluid outlet 84 of the second flow channel 85 are arranged at the lower end region of the condenser 80.
  • the fluid inlet 86 of the first flow channel 87 is arranged at the lower end region.
  • the flow through the Enthitzungs Schemes 81 and the subcooling region 82 with the refrigerant is done serially similar to that in the illustrations of FIGS. 1 to 4 ,
  • This cuboidal element forms an internal heat exchanger 88.
  • the inner heat exchanger 88 has a third flow channel 89. At the same time, the refrigerant from the flow channel 87 is guided into the inner heat exchanger 88. Between the fluid of the third flow channel 89 and the refrigerant of the first flow channel 87, a heat transfer in the internal heat exchanger 88 can take place.
  • the third flow channel 89 can be flowed through either by refrigerant or by a coolant. As with the other areas of the capacitors shown, and the inner heat exchanger 88 can be flowed through in DC and / or in countercurrent. By flowing in countercurrent, a higher heat transfer between the two fluid streams can be achieved.
  • both the fluid inlet 90 and the fluid outlet 91 of the third flow channel 89 are arranged.
  • the fluid outlet 92 of the first flow channel 87 is arranged.
  • FIGS. 1 to 8 shown positions of the fluid inlets or fluid outlets are each exemplary.
  • different orientations, such as on the side of the capacitor are as predictable as the arrangement of a fluid inlet or fluid outlet in a central region of the capacitors.
  • the capacitors 1, 1a, 70, 80 are optionally to be produced from a combination of desuperheating region 3, 72, 81, subcooling region 4, 71, 82 and internal heat exchanger 88.
  • Optimal configurations can be created depending on the application, all of which follow a simple structure of individual disk elements and are thus very flexible in their construction.
  • FIGS. 1 to 8 shown pipes 5, 53, 63, 77 are also inexpensive to produce and are introduced in the simplest case in the disk stacks 11, 11a, 73, 92, thereby leading through inner openings of the disk elements.
  • this is done in an early part of the production process, so that the disc elements with the individual tubes 5, 53, 63, 77 can be soldered in one operation.
  • the tubes 5, 53, 63, 77 in particular with the openings, which have passages, soldered.
  • FIG. 9 shows a sectional view of a capacitor 100 according to the invention.
  • the connection region is shown, to which a collector, not shown, is connected via a flange 102 to the disk stack of the capacitor 100.
  • the flange 102 has an inlet 104 and a drain 103. Via this, a fluid from the condenser 100 can drain into a collector or run back from the collector into the condenser 100.
  • the outlet 103 opens into a tube 101, which itself opens into a flow channel 107.
  • the flow channel 107 is one of the channels, which results between, for example, two stacked disk elements 105 and 106.
  • a detailed view of the connection of the tube 101 to the disc element 105 is shown in the following FIG. 10 shown.
  • a fluid can flow around the tube 101 and further up into an area below the disc element 105.
  • the exact design of the channels is also in the FIG. 10 shown.
  • FIG. 10 shows a detailed view of the arrangement of the tube 101, as it is already in FIG. 9 was shown. It can be seen in FIG. 10 in particular, how the tube 101 is inserted into a drain 103 of the flange 102.
  • the drain 103 is formed by a horizontally extending bore within the flange 102.
  • the tube 101 is inserted via a vertically opening from the top of the bore 103 of the drain hole.
  • the inlet 104 also opens into a bore within the flange 102.
  • the larger diameter bore into which the inlet 104 opens is concentric with the bore, which opens into the drain 103 aligned.
  • the tube 101 is thus flowed around with the fluid which flows along the inlet 104, while it flows through with the fluid which flows to the outlet 103. There is no fluid communication of the fluid flow outside the tube 101 with the fluid flow within the tube 101.
  • the tube 101 has an at least partially circumferential flange 108 in its upper end region.
  • This flange 108 is in FIG. 10 produced by a compression and a resulting material doubling of the tube 101.
  • the flange 108 abuts against the underside of the disk element 105.
  • the disc member 105 further includes a passage 112 formed around the opening through which the tube 101 is inserted. Above the disk element 105, a flow channel 107 is formed, below the disk element 105, a flow channel 109 is formed.
  • multiple numbers of flow channels can also be provided above and below the disk element 105.
  • the presentation of the FIG. 10 is exemplary.
  • the tube 101 is primarily connected to the disc element 105. This can be achieved for example by a gluing process or a soldering process.
  • the flange 102 is fastened to a lower disk element 110 by means of connecting elements 111.
  • the disk element 110 has an opening which has a downward passage.
  • the connecting means 111 are in the FIG. 10 formed over material extensions of the flange 102, which engage behind the passage of the disc member 110 and thus prevent slipping out of the flange 102 from the opening of the disc member 110.
  • Between the flange 102 and the disk element 110 may also be provided, for example, an adhesive connection or a solder joint for permanent connection.
  • FIG. 11 also shows a connection of a flange 120 to a capacitor, which is formed from a plurality of disk elements 128, 129 and 132.
  • the structure of the flange 120 corresponds substantially to the already shown flange 102.
  • the flange 120 is also connected to a passage of an opening of the lower disc member 132 to the capacitor again.
  • the tube 125 has a bevel on both the upper end portion 126 and the lower end portion 127. This chamfer is achieved by a cut, which was generated in a plane which is at a predeterminable angle to the central axis of the tube 125. By the tapered end portions 126, 127, the tube has a sweep at both ends.
  • the tube 125 is supported by the tip on the disc element 128 lying on top.
  • the disk element 128 forms a deflection disk for the flow channel 123 shown.
  • the lower disk element 129 forms a separating disk for the flow channel 123.
  • the tube 125 thus provides fluid communication between the drain 121 and the flow channel 123. Due to the sweep, the tube 125 can abut an area with an end region 126 and thereby position the tube 125 as well as a suitable fluid transfer surface from the tube Form 125 in the flow channel or from a flow channel in the tube 125.
  • the tube 125 is also connected to a passage 131 which is formed around the opening 130 of the disc member 129 with the disc member 129.
  • the tube 125 also has a bevelled end region 127. Via this beveled end region, the tube can be supported in the flange 120 and at the same time represent a suitable flow cross section for the passage of fluid out of the drain 121 into the tube 125.
  • FIG. 12 shows two embodiments of a tube 140 and 150.
  • the pipe 140 is shown in the left part of FIG. 12 . This has at the bottom of a peripheral flange 143, with which it can be supported against disc elements or a flange.
  • the tube 140 has a flexible region 141.
  • This flexible region 141 is generated by a concertina-like design of the tube 140.
  • the accordion-like region has a plurality of material folds 142.
  • the tube 140 can accommodate both compressions and strains, particularly in the axial direction, particularly preferred.
  • the material folds 142 are moved towards each other, in the case of stretching they are pulled apart.
  • the possible length compensation which can be achieved via the tube 140, may vary in size.
  • the right part of the FIG. 12 shows an alternative design of a pipe 150.
  • the pipe 150 is formed by a first pipe section 151 and a second pipe section 152.
  • the pipe sections 151, 152 are inserted into one another in such a way that they are movable relative to each other.
  • the pipe sections 151, 152 are so fluid-tight to one another that no unwanted mixing between a fluid flowing around the pipe 150 and a fluid flowing through the pipe 150 is produced.
  • the second pipe section 152 has a funnel-shaped widening cross section in the axial direction upwards.
  • the first pipe section 151 has a funnel-shaped, tapered cross-section viewed in the axial direction downward.
  • the inner diameter of the first pipe section 151 is selected such that it is greater than the outer diameter of the second pipe section 152. In this way, the two pipe sections 151, 152 can be moved relative to each other.
  • the design of the funnel-shaped regions of the pipe section 151 or of the pipe section 152 simultaneously realizes a stop which defines a limitation of the maximum possible relative movement of the pipe sections 151, 152 relative to one another.
  • the configuration of the tubes 140 and 150 of the FIG. 12 is exemplary.
  • the tube 140 or 150 can advantageously metallic materials, but also more flexible Materials such as plastics or elastomers are used.
  • the embodiments of the FIG. 12 have no limiting character with regard to the design of the pipe.
  • FIGS. 1 to 8 Illustrations of a capacitor shown also have exemplary character and have no limiting effect. They can be combined with each other and clarify the idea of the invention.
  • FIGS. 9 to 12 shown representation of the connection of a pipe or a flange to a capacitor is also exemplary.
  • the various tubes shown the FIGS. 9 to 12 with the different capacitors of the FIGS. 1 to 8 can be combined arbitrarily. It can in the FIGS. 9 to 12 shown pipes are used both for the connection of the collector and for the connection of channels with fluid inlets and fluid outlets in the remaining area of the capacitors.

Landscapes

  • 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)
  • Fixed Capacitors And Capacitor Manufacturing Machines (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Claims (19)

  1. Condenseur (1, 1a, 70, 80, 100) du type à plaques empilées, ledit condenseur comprenant un premier conduit d'écoulement (25, 25a, 60, 87) pour un fluide frigorigène et comprenant un second conduit d'écoulement (26, 26a, 32, 42, 52, 85) pour un liquide de refroidissement, où il est prévu une pluralité d'éléments à plaques qui forment, entre lesdits éléments à plaques, des conduits contigus les uns aux autres et empilés les uns sur les autres, où un premier nombre de conduits est associé au premier conduit d'écoulement (25, 25a, 60, 87), et un second nombre de conduits est associé au second conduit d'écoulement (26, 26a, 32, 42, 52, 85), où le premier conduit d'écoulement (25, 25a, 60, 87) présente une première zone (3, 72, 81) servant à la désurchauffe et à la condensation du fluide frigorigène à l'état de vapeur et présente une seconde zone (4, 71, 82) servant au surrefroidissement du fluide frigorigène condensé, ledit condenseur comprenant un collecteur (2) servant au stockage d'un fluide frigorigène, où un débordement du fluide frigorigène conduit, à travers le collecteur (2), à passer de la première zone (3, 72, 81) dans la seconde zone (4, 71, 82), où le collecteur (2), par un premier élément de raccordement qui forme un premier raccordement de fluide du collecteur (2), est en communication fluidique avec la première zone (3, 72, 81), où le collecteur (2), par un second élément de raccordement qui forme un second raccordement de fluide du collecteur (2), est en communication fluidique avec la seconde zone (4, 71, 82), caractérisé en ce que le premier élément de raccordement et / ou le second élément de raccordement sont formés par un tube (5, 101, 125, 140, 150) qui, en passant par des ouvertures formées dans les éléments à plaques, s'engage à travers un certain nombre d'éléments à plaques.
  2. Condenseur (1, 1a, 70, 80, 100) selon la revendication 1, caractérisé en ce que le premier élément de raccordement est configuré comme un tube (5, 101, 125, 140, 150), et le tube (5, 101, 125, 140, 150), à partir de la seconde zone (4, 71, 82) et à travers la première zone (3, 72, 81), conduit jusqu'à un raccordement de fluide du collecteur (2), où le tube (5, 101, 125, 140, 150) est en communication fluidique avec la seconde zone (4, 71, 82) du premier conduit d'écoulement (25, 25a, 60, 87) et avec le collecteur (2).
  3. Condenseur (100) selon l'une des revendications précédentes, caractérisé en ce qu'au moins l'un des tubes (101, 140, 150) présente un rétrécissement et / ou un épaulement et / ou une bride (108, 143) au moins partiellement circulaire et / ou un élargissement (153), éléments par lesquels le tube peut venir en appui sur l'un des éléments à plaques et peut être fixé dans le condenseur.
  4. Condenseur (1, 1a, 70, 80, 100) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins l'un des éléments à plaques est configuré comme une plaque de séparation et / ou l'un des éléments à plaques est configuré comme une plaque de retour de flux.
  5. Condenseur (1, 1a, 70, 80, 100) selon la revendication 4, caractérisé en ce que le tube (5, 101, 125, 140, 150) est supporté, dans le condenseur (1, 1a, 70, 80, 100), sur une plaque de retour de flux.
  6. Condenseur (1, 1a, 70, 80, 100) selon l'une quelconque des revendications précédentes, caractérisé en ce que le tube (5, 101, 125, 140, 150) présente des ouvertures radiales et / ou axiales.
  7. Condenseur (1, 1a, 70, 80, 100) selon l'une quelconque des revendications précédentes, caractérisé en ce que le tube (5, 101, 125, 140, 150) est supporté sur l'un des éléments à plaques extérieurs de la seconde zone (4, 71, 82).
  8. Condenseur (1) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'il est prévu, au niveau de l'entrée de fluide (61) et / ou au niveau de la sortie de fluide (62) du premier conduit d'écoulement (60), un deuxième tube (63) qui est en communication fluidique avec un autre conduit du premier conduit d'écoulement (60).
  9. Condenseur (1) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'il est prévu, au niveau de l'entrée de fluide (50) et / ou au niveau de la sortie de fluide (51) du second conduit d'écoulement (52), un troisième tube (53) qui est en communication fluidique avec un autre conduit du second conduit d'écoulement (52).
  10. Condenseur (1, 1a, 70, 80, 100) selon l'une quelconque des revendications précédentes, caractérisé en ce que le tube (5, 53, 63, 101, 125, 140, 150) au moins au nombre de un est guidé dans les éléments à plaques à travers les ouvertures, est brasé avec au moins une partie des éléments à plaques, en particulier brasé avec les passages.
  11. Condenseur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins l'un des tubes (125) est chanfreiné au niveau d'une zone d'extrémité (126, 127) ou bien au niveau des deux zones d'extrémité (126, 127).
  12. Condenseur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins l'un des tubes (140) présente une zone flexible, où le tube (140), sous l'effet de la zone flexible (141), est compressible et / ou extensible dans la direction axiale.
  13. Condenseur selon la revendication 9, caractérisé en ce que la zone flexible (141) est configurée par une forme du tube (140) en accordéon.
  14. Condenseur selon l'une des revendications précédentes 8 ou 9, caractérisé en ce que la zone flexible (141) est formée par un matériau élastique, comme par exemple de la matière plastique ou du caoutchouc, où une compression ou un allongement du tube (140) est réversible dans la direction axiale et / ou dans la direction radiale.
  15. Condenseur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins l'un des tubes (150) est formé par une pluralité de tronçons de tube (151, 152), où les tronçons de tube (151, 152) sont raccordés l'un à l'autre de façon étanche aux fluides.
  16. Condenseur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un premier tronçon de tube (151) se rétrécit en forme d'entonnoir dans la direction axiale, et le second tronçon de tube (152) s'élargit en forme d'entonnoir dans la direction axiale, où les deux tronçons de tube (151, 152) sont introduits l'un dans l'autre, de manière telle que le mouvement relatif se produisant entre le second tronçon de tube (152) et le premier tronçon de tube (151) soit limité, par le fait que la zone s'élargissant vient en butée sur la zone se rétrécissant.
  17. Condenseur (100) selon l'une quelconque des revendications précédentes, caractérisé en ce que le tube (101, 125) est logé dans un élément de raccordement (102, 120) et est raccordé à celui-ci de façon étanche aux fluides.
  18. Condenseur (1, 1a, 70, 80, 100) selon l'une quelconque des revendications précédentes, caractérisé en ce que la seconde zone (4, 4a, 71, 82) présente une pluralité de tronçons d'écoulement qui sont traversés par le fluide frigorigène, où les tronçons d'écoulement sont formés à chaque fois par différents conduits du premier conduit d'écoulement (25, 25a, 60, 87) et / ou formés par des zones partielles de différents conduits du premier conduit d'écoulement (25, 25a, 60, 87).
  19. Condenseur (1, 1a, 70, 80, 100) selon l'une quelconque des revendications précédentes, caractérisé en ce que la seconde zone (4, 4a, 71, 82) présente une pluralité de conduits, où au moins différents conduits de la seconde zone (4, 4a, 71, 82) sont en contact thermique avec le second conduit d'écoulement (26, 26a, 32, 42, 52, 85), où le liquide de refroidissement et le fluide frigorigène peuvent s'écouler à travers les conduits de la seconde zone (4, 4a, 71, 82) et à travers le second conduit d'écoulement (26, 26a, 32, 42, 52, 85), en circulant suivant un flux orienté, l'un par rapport à l'autre, dans le même sens et / ou en sens opposé.
EP14723838.0A 2013-05-16 2014-05-15 Condenseur Active EP2997318B1 (fr)

Applications Claiming Priority (2)

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DE102013209157.5A DE102013209157A1 (de) 2013-05-16 2013-05-16 Kondensator
PCT/EP2014/060024 WO2014184323A1 (fr) 2013-05-16 2014-05-15 Condenseur

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EP2997318A1 EP2997318A1 (fr) 2016-03-23
EP2997318B1 true EP2997318B1 (fr) 2019-02-06

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US (1) US10088204B2 (fr)
EP (1) EP2997318B1 (fr)
JP (1) JP6461104B2 (fr)
CN (1) CN105431691B (fr)
BR (1) BR112015026951A2 (fr)
DE (2) DE102013209157A1 (fr)
WO (1) WO2014184323A1 (fr)

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DE102020215226A1 (de) 2020-12-02 2022-06-02 Mahle International Gmbh Sammler eines Kältemittelkreislaufs

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BR112015026951A2 (pt) 2017-07-25
US20160091229A1 (en) 2016-03-31
JP2016519279A (ja) 2016-06-30
CN105431691A (zh) 2016-03-23
US10088204B2 (en) 2018-10-02
JP6461104B2 (ja) 2019-01-30
CN105431691B (zh) 2018-01-09
EP2997318A1 (fr) 2016-03-23
DE102013209157A1 (de) 2014-12-04
WO2014184323A1 (fr) 2014-11-20
DE112014002420A5 (de) 2016-01-28

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