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EP2909563B1 - Condenseur - Google Patents

Condenseur Download PDF

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Publication number
EP2909563B1
EP2909563B1 EP13756157.7A EP13756157A EP2909563B1 EP 2909563 B1 EP2909563 B1 EP 2909563B1 EP 13756157 A EP13756157 A EP 13756157A EP 2909563 B1 EP2909563 B1 EP 2909563B1
Authority
EP
European Patent Office
Prior art keywords
flow channel
condenser
refrigerant
region
fluid
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
EP13756157.7A
Other languages
German (de)
English (en)
Other versions
EP2909563A1 (fr
Inventor
Herbert Hofmann
Martin Kaspar
Thomas Mager
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP2909563A1 publication Critical patent/EP2909563A1/fr
Application granted granted Critical
Publication of EP2909563B1 publication Critical patent/EP2909563B1/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
    • 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
    • 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
    • F28D9/0056—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 with U-flow or serpentine-flow inside conduits; with centrally arranged openings on the plates
    • 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
    • F28D9/0062—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 spaced plates with inserted elements
    • F28D9/0075—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 spaced plates with inserted elements the plates having openings therein for circulation of the heat-exchange medium from one conduit to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F28F9/0251—Massive connectors, e.g. blocks; Plate-like connectors
    • F28F9/0253—Massive connectors, e.g. blocks; Plate-like connectors with multiple channels, e.g. with combined inflow and outflow channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • 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
    • F25B2339/043—Condensers made by assembling plate-like or laminated elements
    • 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

  • 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, wherein a plurality of disc elements are provided, which form stacked mutually adjacent channels between the disc elements, in particular according to the preamble of claim 1.
  • the US2009 / 0071189 discloses such a capacitor.
  • Condensers are used in refrigerant circuits of motor vehicle air-conditioning systems to cool the refrigerant to the condensation temperature and then to condense the refrigerant.
  • capacitors have a collector in which a volume of refrigerant is kept in order to compensate for volume fluctuations in the refrigerant circuit and to achieve a stable supercooling of the 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 becomes 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 a tube-rib block and introduced into the collector.
  • a stacked disc capacitor in which a first stack of disc elements represents a first cooling and condensing region and a second stack of disc elements constitutes a subcooling region.
  • the first stack is separated from the second stack by a housing containing a collector and dryer.
  • a disadvantage of the devices of the prior art is that the integration of capacitors in stacked disc design, collectors and subcoolers has been solved quite expensive.
  • the capacitors from the prior art are characterized by an increased production cost. This results in the use of the capacitors additional costs that make their use 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.
  • a collector in the refrigerant circuit is advantageously integrated in the flow channel of the refrigerant, at a point after the complete condensation of the refrigerant and before the collection, drying and / or filtering of the refrigerant.
  • the first connection element is designed as a channel and the channel leads from the first region through the second region to the fluid inlet of the collector, wherein the channel is only in fluid communication with the first region of the first flow channel.
  • the second connection element is designed as a channel and the channel leads from the fluid outlet of the collector through the first region into the second region.
  • 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 inserted so deeply into the disc stack until 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 first region through the second region to the fluid inlet of the collector, wherein the tube is only in fluid communication with the first region of the first flow channel.
  • the collector is connected directly to the Enthitzungs- and condensation area.
  • 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 guide the entire refrigerant from this first region of the first flow channel into the collector, the tube is dimensioned so that it passes through all the disk elements of the second region and opens into a channel of the first region. In this way, the refrigerant is passed over the second area directly into the collector.
  • 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.
  • a fluid inlet or fluid outlet of the second flow channel has a second tube which is in fluid communication with another channel of the second flow channel.
  • both the fluid inlet and the fluid outlet can be arranged at a common end region of the disk stack.
  • the other channel is one of the last channels of the second flow channel, which lies substantially opposite the insertion side of the tube in the disc stack.
  • 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 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 section of the second region is replaced in this 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 an internal heat exchanger, generally in countercurrent to one another, in two different flow channels.
  • the refrigerant which thereby 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 two flow channels is achieved.
  • the first flow channel has a third region which follows the second region and the subcooling of the refrigerant serves, wherein the third region has a third flow channel for a fluid, wherein the first and the third flow channel at least in sections as a heat exchanger, preferably as an internal heat exchanger in stacked disk design, can be ausgestaltbar.
  • the arrangement of an internal heat exchanger after the second area, in which the supercooling takes place, further lowers the temperature of the refrigerant. There is a greater undercooling of the refrigerant, as by the pure use of a subcooling or an internal heat exchanger.
  • the condenser is constructed so that the heat transfer between the refrigerant and the refrigerant takes place in the first area in which the refrigerant is deprived and condensed.
  • the heat transfer also takes place between the refrigerant and the coolant.
  • the heat transfer then takes place between the refrigerant in a first temperature range and the refrigerant in a second temperature range.
  • the second flow channel of the coolant is guided through the condenser so that only the first region and the second region are flowed through and the coolant is subsequently led out of the condenser.
  • the third region of the disk stack has a fluid inlet and a fluid outlet, via which the third flow channel can be flown with the refrigerant.
  • 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, since so a higher temperature difference between the third flow channel and the first flow channel can be achieved.
  • an additionally cooled fluid is supplied.
  • the collector is in fluid communication with only the first 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 second 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.
  • the collector can be effectively supplied to the refrigerant from the region of the first flow channel, in which the refrigerant is already completely condensed.
  • the tubes are dimensioned so that the refrigerant is discharged from one of the channels of the first flow channel into the collector and then in the subsequent channel of the first flow channel again is initiated.
  • the two channels of the first flow channel are only in fluid communication with each other via the collector.
  • the openings of the disc element of the channel, from which the refrigerant is diverted, are so closed that no liquid can take place directly into the subsequent channel.
  • 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.
  • the discs have apertures with or without passage to create or seal fluid communication between adjacent channels.
  • the fluid flows directly into the next but one channel of the disk stack. This ensures that a change between channels that belong to the first flow channel and channels that belong to the second flow channel is achieved in the disk stack. In this case, a uniform distribution can be generated so that a channel of the first flow channel always follows a channel of the second flow channel. Even deviating distributions can be generated with this method.
  • the tubes are guided through openings in the disc elements and with at least a portion of the disc elements, in particular with the passages, are soldered.
  • 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.
  • 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 capacitor 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 filtering the refrigerant. In this way, the refrigerant can be easily withdrawn excess moisture and continue to be 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. It is particularly advantageous if the first section in the second channel has a plurality of flow paths through which the flow direction is alternately reversed.
  • the second section in the second channel has a plurality of flow paths through which the flow direction is alternately reversed in succession.
  • FIGS. 1 to 7 different embodiments of a capacitor 1, 60, 70 are shown in stacked disc design. These are capacitors 1, 60, 70 for use in an air conditioning system for motor vehicles. All shown capacitors 1, 60, 70 are formed from a multiplicity of disc elements stacked on top of one another to form a slice stack 11, 68, 87.
  • the essential advantage of the construction as a condenser 1, 60, 70 in stacked disk design is that the disk elements are largely identical and only the outer terminal plates and individual, built in the stack deflection or blocking plates, which deflect or block the inner flow channels of the differ fundamentally identical shape of the disc elements. This allows a low-cost and easy production.
  • the capacitors 1, 60, 70 are indicated only by a schematic diagram.
  • the individual portions of the capacitors 1, 60, 70, such as the Enthitzungs Society 3, 80 or the subcooling 4, 81 and the region of an internal heat exchanger 61, 82 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 always adjacent to each other. In simple embodiments, it may be that channels for the refrigerant and channels for the coolant in one equally distributed alternating order are arranged. Likewise, it is conceivable to choose a deviating from the uniform distribution distribution of refrigerant to coolant channels. It is conceivable to realize the alternating rhythm between coolant and coolant channels by a ratio of 1: 1.
  • FIGS. 1 to 7 The flow channels of the coolant and the refrigerant are in the FIGS. 1 to 7 also indicated only schematically. Each of the cuboidal elements is traversed in the figures only once by a refrigerant or coolant flow channel. This illustration is intended to illustrate only the flow principle of the individual capacitors 1, 60, 70 and has no delimiting effect.
  • the flow channels of the refrigerant 25, 64, 73, 79 are each represented by a dotted line.
  • the flow channels of the coolant 26, 42, 52, 67, 76 are each represented by a solid solid line.
  • FIGS. 1 to 7 shown flow directions of the refrigerant and the coolant are each only one example and can in reality just as in opposite directions to those in the FIGS. 1 to 7 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.
  • the refrigerant is brought into a thermal exchange with a coolant, which also flows through the Enthitzungs Scheme 3.
  • a subcooling 4 is connected.
  • the completely liquid refrigerant is further cooled 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 inlet 12 a tube 5, which is guided through the sub-cooling region 4 and is in the decompression region 3 in fluid communication with the flow channel of the refrigerant.
  • the fluid outlet 6 of the collector 2 is in turn in fluid communication with the flow channel of the refrigerant in the subcooling region 4. In this way, it is ensured that the refrigerant is completely conducted from the Enthitzungs Scheme 3 in the collector 2.
  • the collector 2 thus represents the passage of fluid from the desuperheating area 3 into the subcooling area 4, in particular for the refrigerant.
  • 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.
  • FIG. 2 also shows a capacitor 1, which corresponds to the in FIG. 1 shown capacitor 1 corresponds substantially.
  • Flow channels 25, 26 shown for a coolant and a refrigerant flows through a arranged at the upper end portion of the disk stack 11 fluid inlet 21 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 openings 24, which are arranged between the individual disc elements.
  • the refrigerant flows into the collector 2 via the pipe 5.
  • the collector 2 for the purpose of storage, filtration and drying and then flows through the fluid outlet 6 of the collector 2 into the subcooling region 4 of the condenser 1.
  • the refrigerant flows out of the subcooling region 4 through the fluid outlet 23 ,
  • the coolant flows through the fluid inlet 20 at the upper end portion of the condenser 1 into the dewarning area 3.
  • the coolant flows through the individual channels of the Enthitzungs Schemes 3 and the subcooling 4 in parallel.
  • the coolant through upper openings 24, which lie in an approximately rectilinear imaginary extension to the fluid inlet 20 of the coolant, from top to bottom through the disk stack 11 and then spreads across the width of the capacitor 1. After the coolant over the entire width of the Condenser 1, it then flows through a plurality of openings 24 in the disc elements from bottom to top through the fluid outlet 22 of the coolant from the condenser 1.
  • FIG. 3 shows a similar structure as it already in the Figures 1 and 2 was presented.
  • the flow channel 25 of the refrigerant is analogous to FIG. 2 through the condenser 1 of FIG. 3 arranged. Deviating from FIG. 2 the coolant flows in FIG. 3 now no longer in a parallel arrangement 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 lower region of the condenser 1 into the subcooling region 4. There it is distributed over the width of the capacitor 1 and flows through an inner opening 24 upwards into the Enthitzungs Scheme 3. There it also spreads over the entire width of the capacitor 1 and flows upward through a further inner opening 24 in the upper Area of the Enthitzungs Schemes 3 and finally flows after a redistribution across the width of the capacitor 1 through the fluid outlet 31 from the condenser 1 from.
  • the flow channel 32 of the coolant extends in the FIG. 3 , So as well as the flow channel 25 of the refrigerant in series through the individual channels in the interior of the condenser 1. By in FIG. 3 As shown, the refrigerant flow over the entire condenser 1 is in countercurrent to the coolant.
  • FIG. 4 again shows a capacitor 1 analogous to FIGS. 1 to 3 ,
  • the refrigerant flow channel 25 is analogous to Figures 2 and 3 executed. Deviating from the Figures 2 and 3 Now, the flow channel 42 of the coolant is disposed within the capacitor 1, that there are both areas in which the capacitor is flowed through in parallel, as well as areas in which it is passed through in series.
  • the coolant flows through the fluid inlet 40 into the subcooling region 4 of the condenser 1. There it is distributed both over the width of the condenser 1 as well as upwardly through an inner opening 24 in the Enthitzungs Scheme 3. In the desuperheating 3, the coolant is also distributed over the entire width of the condenser 1.
  • the coolant flow in the subcooling 4 also flows over an inner opening 24 upwards into the Enthitzungs Scheme 3, where the coolant flow from the sub-cooling region 4 and the Enthitzungs Scheme 3 reunites. Together, the coolant flows there via a further inner opening 24 in the upper region of the Enthitzungs Schemes 3 and there again distributed over the entire width of the capacitor 1 and finally flows out of the condenser 1 via the fluid outlet 41 of the coolant.
  • the condenser 1 is partially flowed through in parallel and partially in series by the coolant. This results in areas in which the coolant flows with the refrigerant in countercurrent, as well as areas in which the coolant flows with the refrigerant in the DC flow.
  • FIG. 5 also shows a capacitor 1 analogous to the embodiments of FIGS. 1 to 4 ,
  • the flow channel 25 of the refrigerant is again unchanged from the FIGS. 2 to 4 executed.
  • the coolant is now purely serially passed through the condenser 1 and is on the condenser by a, arranged at one of its end portions, fluid inlet 50 and fluid outlet 51 and removed.
  • the coolant is not distributed over the width of the condenser 1 as in the preceding figures, but is guided through a pipe 53, which is connected to the fluid inlet 50, through openings 54 in the disk elements down into the subcooling region 4 of the condenser 1 , Only in the subcooling region 4 does the coolant leave the tube 53 and spread over the width of the condenser 1.
  • the coolant flows again through an inner opening 24 in the Enthitzungs Scheme 3, where it is distributed over the width of the capacitor 1 again. It then flows through a further opening 24 in the upper region of the Enthitzungsshare and is also distributed there across the width of the capacitor 1, before it flows out of the condenser 1 via the fluid outlet 51 of the coolant.
  • the coolant thus flows completely serially through the regions of the condenser 1.
  • the coolant flowing in the flow channel 52 thus flows countercurrently to the refrigerant in the flow channel 25 at all times.
  • FIG. 6 shows a capacitor 60, which unlike the capacitors 1 of FIGS. 1 to 5 now has a Enthitzungs Suite 3 in the upper part and arranged underneath an internal heat exchanger 61, which in place of the subcooling 4 of the FIGS. 2 to 5 occurs.
  • the flow channel 25 of the refrigerant is analogous to FIGS. 2 to 5 passed through the capacitor 60.
  • the coolant flows into the condenser 60 through a fluid inlet 65 at the top of the disk stack 68 of the condenser 60. There, it is distributed through an inner opening 24 in depth via the Enthitzungs Scheme 3 and then distributed there across the width of the capacitor 60 before it flows out through openings 24 and the fluid outlet 66 back out of the condenser 60.
  • the Enthitzungs Scheme 3 flows through the coolant in parallel.
  • the desuperheating region 3 is further serially flowed through by the refrigerant through the flow channel 25 of the refrigerant, thereby adjusting portions of the direct current and portions of the counterflow between the refrigerant and the coolant.
  • the region 61 which represents the inner heat exchanger, is not flowed through by the coolant. Instead, the inner heat exchanger 61 on a third flow channel 64, which is also traversed by the refrigerant.
  • the refrigerant flows through a fluid inlet 62 into the inner heat exchanger 61 and is distributed over the width of the condenser 60 before it flows out of the condenser 60 via the fluid outlet 63.
  • the refrigerant in the flow channel 64 and the refrigerant in the flow channel 25 are in countercurrent to each other. In this way, a higher heat transfer between the two flow channels 64, 25 can be achieved.
  • the refrigerant which flows through the flow channel 64 of the inner heat exchanger 61, comes as the refrigerant in the flow channel 25 from the same refrigerant circuit.
  • the refrigerant in the flow channel 64 differs from the refrigerant in the flow channel 25 substantially by its temperature. Since it is intended that refrigerant in the flow channel 25 within the inner Heat exchanger 61 continue to cool, the refrigerant in the flow channel 64 has a lower temperature, whereby the refrigerant in the flow channel 25 further heat can be withdrawn.
  • FIG. 6 embodiment shown represents an alternative to that in the FIGS. 1 to 5 Instead of subcooling by a thermal transition between a coolant and the refrigerant, here a thermal transition between the refrigerant of a first temperature level and the refrigerant of a second temperature level is generated.
  • FIG. 7 now shows a capacitor 70, which consists of a disk stack 87.
  • the capacitor 70 is a combination of the embodiments of FIGS. 1 to 6 .
  • At the upper Enthitzungs Scheme 80 is followed at the bottom of a subcooling 81.
  • An internal heat exchanger 82 is connected to the subcooling region 81 at the bottom.
  • the upper portion of the condenser 70 which consists of the Enthitzungs Scheme 80 and the subcooling 81, is a coolant according to the flow, which is already in FIG. 2 for the coolant is shown, flows through.
  • a coolant flows through the fluid inlet 74 into the Enthitzungs Scheme 80 and there is distributed through inner openings along the depth of the condenser 70 into the sub-cooling region 81. It then flows through the capacitor 70 in its width uniformly, before it at the opposite end by internal openings flows upward and out of the condenser 70 via the fluid outlet 75.
  • the coolant flows through the condenser 70 in its flow channel 76 completely parallel.
  • the refrigerant flows through a fluid inlet 71 into the Enthitzungs Scheme 80 and flows through the Enthitzungs Scheme 80 serially.
  • the refrigerant then flows from the Enthitzungs Scheme 80 via a pipe 84 which passes through the subcooling 81 and the inner heat exchanger 82, directly into the collector 2. From the collector second
  • the refrigerant flows via the pipe 83 back into the subcooling region 81 and is distributed over the width of the capacitor 70 thereafter. It then flows through an inner opening from the subcooling 81 into the underlying inner heat exchanger 82 and also flows through the individual channels of the internal heat exchanger 82 serially before it flows out of the inner heat exchanger 82 via the fluid outlet 72 from the condenser 70.
  • the inner heat exchanger 82 is also traversed by a refrigerant.
  • a refrigerant flows via a fluid inlet 77, which may be formed as a tube 85, into the internal heat exchanger 82. There it is distributed over the width of the inner heat exchanger 82 and flows through an inner opening in the upper region of the inner heat exchanger 82. There it also spreads again across the width of the capacitor 70 and finally flows through a tube 86 which passes through the lower Area of the internal heat exchanger 82 leads out of the condenser 70.
  • the tube 86 thus also forms the fluid outlet 78 of the flow channel 79 of the refrigerant.
  • FIGS. 1 to 7 shown positions of the fluid inlets or fluid outlets are each exemplary. Deviating orientations, for example laterally on the condenser, are just as conceivable as the arrangement of a fluid inlet or outlet in a middle region of the condensers. Rather, the FIGS. 1 to 7 Embodiments show that it is possible to lead a refrigerant flow and a coolant flow both in the DC principle as well as in the countercurrent principle by the individual regions of the capacitors 1, 60, 70. This results in different advantages for the arrangement of the fluid inlets or fluid outlets. Depending on the intended application of the capacitors 1, 60, 70, a corresponding internal design of the disk stack 11, 68, 87 of the capacitors 1, 60, 70 make.
  • the capacitors 1, 60, 70 can be selectively produced from a combination of desuperheating area 3, 80, subcooling area 4, 81 and internal heat exchanger 61, 82.
  • Optimal configurations can be created depending on the application all follow a simple structure of individual disc elements and thus are very flexible in their construction.
  • FIGS. 1 to 7 shown pipes are also inexpensive to manufacture and are introduced in the simplest case in the disk stack 11, 68, 87, 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 can be soldered to the individual tubes in one operation.
  • the tubes are in particular soldered to the openings which have passages.
  • the FIG. 8 shows a section through a connecting element, with which, for example, the collector 2 to the respective lower portion of the capacitors 1, 60 in the FIGS. 1 to 6 can be connected.
  • the connection element has a tube 90, which forms a flow channel 96 between a fluid inlet 93 and a fluid outlet 94.
  • This tube 90 corresponds in the FIGS. 1 to 6 the pipe 5, which connects the collector 2 with the lower part of the Enthitzungs Schemes 3.
  • the collector 2 is in fluid communication via the flow channel 97, which is formed between the fluid inlet 91 and the fluid outlet 92, with the subcooling region 4 or the internal heat exchanger 61.
  • the tube 90 engages through at least one of the disk elements of the capacitors 1, 60.
  • the capacitor is in FIG. 8 designated by the reference numeral 95. It can be seen in particular that the flow channel 97 extends completely around the tube 90 around.
  • FIG. 9 shows a further alternative connection element, which in particular in an arrangement according to the FIG. 7 can be used.
  • a first tube 100 is arranged parallel to a second tube 101.
  • the tube 100 forms a flow channel 106 which extends between a fluid inlet 102 and a fluid outlet 103.
  • the tube 101 also forms a flow channel 107, which runs between a fluid inlet 104 and a fluid outlet 105.
  • the capacitor is in FIG. 9 indicated by the reference numeral 108.
  • Main task of the connection element of FIG. 9 it is to discharge a fluid from a region of the condenser 1, 60, 70, 108 and supply it to the collector 2. This is done via the longer tube 101.
  • the return of the fluid from the collector 2 into the condenser 1, 60, 70, 108 is done via the shorter tube 100.
  • By the length of the tubes 100, 101 and thus resulting different heights of the fluid outlets 103rd , 105 it is possible to divert the fluid at different heights relative to the condenser 1, 60, 70, 108 from the condenser 1, 60, 70, 108 and feed it again.
  • FIGS. 8 and 9 shown fluid inlets and fluid outlets can also be arranged reversed depending on the flow direction.

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

Claims (17)

  1. Condenseur (1, 60, 70) du type à plaques empilées, comprenant un premier conduit d'écoulement (25, 64, 73, 79) pour un fluide frigorigène, et comprenant un deuxième conduit d'écoulement (26, 31, 42, 52, 67) pour un liquide de refroidissement, où il est prévu une pluralité d'éléments de plaques qui forment, entre les éléments de plaques, des conduits empilés les uns sur les autres et contigus les uns aux autres, où une première partie des conduits est associée au premier conduit d'écoulement (25, 64, 73, 79), et une deuxième partie des conduits est associée au deuxième conduit d'écoulement (26, 31, 42, 52, 67), où le premier conduit d'écoulement (25, 64, 73, 79) présente une première zone (3, 80) servant à la désurchauffe et à la condensation du fluide frigorigène à l'état de vapeur, et présente une deuxième zone (4, 81, 62) servant au surrefroidissement du fluide frigorigène condensé, comprenant un collecteur (2) servant au stockage d'un fluide frigorigène, où un débordement de fluide frigorigène sortant de la première zone (3, 80) et passant dans la deuxième zone (4, 81, 62) se produit à travers le collecteur (2), où le collecteur (2) est en communication fluidique avec la première zone (3, 80), par un premier élément de raccordement qui forme l'entrée de fluide (12) du collecteur (2), où un deuxième élément de raccordement servant de sortie de fluide (6) du collecteur (2) est en communication fluidique avec la deuxième zone (4, 81, 62), caractérisé en ce que le premier élément de raccordement ou le deuxième élément de raccordement est un tube (5) qui, par des ouvertures situées dans des éléments de plaques, pénètre à travers un certain nombre d'éléments de plaques.
  2. Condenseur (1, 60, 70) selon la revendication 1, caractérisé en ce que le premier élément de raccordement (5) est configuré comme un tube, et le tube, à partir de la première zone (3, 80), conduit à travers la deuxième zone (4, 81, 61) jusqu'à l'entrée de fluide (12) du collecteur (2), où le tube est en communication fluidique seulement avec la première zone (3, 80) du premier conduit d'écoulement (25, 64, 73, 79).
  3. Condenseur (1, 60, 70) selon la revendication 1 ou 2, caractérisé en ce que le deuxième élément de raccordement (6) est configuré comme un tube, et le tube, à partir de la sortie de fluide du collecteur, conduit dans la deuxième zone en traversant la première zone.
  4. Condenseur (1, 60, 70) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une entrée de fluide (50) ou une sortie de fluide du deuxième conduit d'écoulement (26, 31, 42, 52, 67) présente un deuxième tube (53) qui est en communication fluidique avec un autre conduit du deuxième conduit d'écoulement (26, 31, 42, 52, 67).
  5. Condenseur (1, 60, 70) selon la revendication 4, caractérisé en ce que l'autre conduit est l'un des derniers conduits du deuxième conduit d'écoulement (26, 31, 42, 52, 67), lequel autre conduit se trouve, dans la pile de plaques, pratiquement en face du côté d'introduction du tube (53).
  6. Condenseur (1, 60, 70) selon l'une quelconque des revendications précédentes, caractérisé en ce que le deuxième conduit d'écoulement (52) peut être traversé en série, et une entrée de fluide (50) et une sortie de fluide (51) du deuxième conduit d'écoulement (52) sont disposées à chaque fois au niveau de la même zone d'extrémité de la pile de plaques.
  7. Condenseur (1, 60, 70) selon l'une quelconque des revendications précédentes, caractérisé en ce que la deuxième zone du premier conduit d'écoulement (25) forme, avec un troisième conduit d'écoulement (64), un échangeur de chaleur intérieur (61) du type à plaques empilées, où le premier (25) et le troisième conduit d'écoulement (64) peuvent être traversés par un fluide frigorigène.
  8. Condenseur (1, 60, 70) selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier conduit d'écoulement (73) présente une troisième zone (82) qui suit la deuxième zone (4, 81) et sert au surrefroidissement du fluide frigorigène, où la troisième zone (82) présente un troisième conduit d'écoulement (79) pour un fluide, où le premier et le troisième conduit d'écoulement peuvent être configurés au moins partiellement comme un échangeur de chaleur, de préférence comme un échangeur de chaleur intérieur (82) du type à plaques empilées.
  9. Condenseur (1, 60, 70) selon la revendication 8, caractérisé en ce que le troisième conduit d'écoulement (79) peut être alimenté en fluide frigorigène, de façon indépendante par le premier conduit d'écoulement, ou bien en liquide de refroidissement, de façon indépendante par le deuxième conduit d'écoulement.
  10. Condenseur (1, 60, 70) selon l'une quelconque des revendications 7 à 9, caractérisé en ce que le collecteur (2) est en communication fluidique seulement avec la première zone (80) du premier conduit d'écoulement (73), par un tube (84) qui passe à travers une partie de la pile de plaques (87) et forme l'entrée de fluide dans le collecteur (2), et la sortie de fluide du collecteur (2) est formée par un autre tube (83) qui passe à travers une partie de la pile de plaques (87) et est en communication fluidique seulement avec la deuxième zone (81) du premier conduit d'écoulement (73).
  11. Condenseur (1, 60, 70) selon l'une quelconque des revendications 7 à 10, caractérisé en ce que l'entrée de fluide (77) et / ou la sortie de fluide (78) de l'échangeur de chaleur intérieur (82) est formée par un tube (85, 86).
  12. Condenseur (1, 60, 70) selon l'une quelconque des revendications précédentes, caractérisé en ce que les plaques présentent des ouvertures (24) avec ou sans passage, pour produire une communication fluidique, ou pour en assurer l'étanchéité, entre des conduits contigus.
  13. Condenseur (1, 60, 70) selon l'une quelconque des revendications précédentes, caractérisé en ce que les tubes (5, 50, 83, 84, 86, 87) sont guidés dans les éléments de plaques à travers des ouvertures (24) et sont brasés avec au moins une partie des éléments de plaques, en particulier avec les passages.
  14. Condenseur (1, 60, 70) selon l'une quelconque des revendications précédentes, caractérisé en ce que le premier élément de raccordement est un tube, et le deuxième élément de raccordement est une bride ou inversement.
  15. Condenseur (1, 60, 70) selon l'une quelconque des revendications précédentes, caractérisé en ce que le collecteur (2) est conçu pour la filtration et / ou la déshydratation du fluide frigorigène.
  16. Condenseur (1, 60, 70) selon au moins l'une quelconque des revendications précédentes, caractérisé en ce que le premier tronçon présente, dans le deuxième conduit, plusieurs voies d'écoulement parcourues successivement, voies d'écoulement dans lesquelles la direction d'écoulement est inversée, à chaque fois de façon alternée.
  17. Condenseur (1, 60, 70) selon au moins l'une quelconque des revendications précédentes, caractérisé en ce que le deuxième tronçon présente, dans le deuxième conduit, plusieurs voies d'écoulement parcourues successivement, voies d'écoulement dans lesquelles la direction d'écoulement est inversée à chaque fois de façon alternée.
EP13756157.7A 2012-09-21 2013-09-02 Condenseur Active EP2909563B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012217090.1A DE102012217090A1 (de) 2012-09-21 2012-09-21 Kondensator
PCT/EP2013/068092 WO2014044520A1 (fr) 2012-09-21 2013-09-02 Condenseur

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EP2909563A1 EP2909563A1 (fr) 2015-08-26
EP2909563B1 true EP2909563B1 (fr) 2018-08-15

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US (1) US10060658B2 (fr)
EP (1) EP2909563B1 (fr)
KR (1) KR20150060779A (fr)
CN (1) CN104641199B (fr)
DE (1) DE102012217090A1 (fr)
WO (1) WO2014044520A1 (fr)

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FR3000183B1 (fr) * 2012-12-21 2018-09-14 Valeo Systemes Thermiques Condenseur avec reserve de fluide frigorigene pour circuit de climatisation
DE102016001607A1 (de) * 2015-05-01 2016-11-03 Modine Manufacturing Company Flüssigkeit-zu-Kältemittel-Wärmetauscher und Verfahren zum betrieb desselben
FR3059400A1 (fr) * 2016-11-25 2018-06-01 Valeo Systemes Thermiques Echangeur de chaleur entre un fluide refrigerant et un liquide caloporteur
CN109000389B (zh) * 2017-11-03 2021-07-27 株式会社电装 冷凝器及具备该冷凝器的制冷系统
CN107883616A (zh) * 2017-11-29 2018-04-06 上海加冷松芝汽车空调股份有限公司 过冷式水冷冷凝器
WO2019175616A1 (fr) * 2018-03-13 2019-09-19 Carrier Corporation Architecture de condenseur à segments multiples
EP3572753B1 (fr) * 2018-05-24 2020-12-16 Valeo Autosystemy SP. Z.O.O. Échangeur de chaleur
EP3572754B1 (fr) * 2018-05-24 2020-12-16 Valeo Autosystemy SP. Z.O.O. Échangeur de chaleur
CN108731307A (zh) * 2018-07-04 2018-11-02 浙江银轮机械股份有限公司 一种叠片式冷凝器
JP2020016379A (ja) * 2018-07-25 2020-01-30 株式会社デンソー 熱交換器
DE112019005896T5 (de) * 2018-11-27 2021-08-05 Modine Manufacturing Company Wärmetauscher zum Kühlen mehrerer Fluide
JP7400234B2 (ja) * 2019-07-16 2023-12-19 株式会社デンソー 熱交換器

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FR2947041B1 (fr) 2009-06-23 2011-05-27 Valeo Systemes Thermiques Condenseur avec reserve de fluide frigorigene pour circuit de climatisation
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Publication number Publication date
CN104641199A (zh) 2015-05-20
US20160161160A1 (en) 2016-06-09
WO2014044520A1 (fr) 2014-03-27
DE102012217090A1 (de) 2014-03-27
KR20150060779A (ko) 2015-06-03
EP2909563A1 (fr) 2015-08-26
US10060658B2 (en) 2018-08-28
CN104641199B (zh) 2017-03-01

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