EP2997318A1 - Condenseur - Google Patents

Condenseur

Info

Publication number
EP2997318A1
EP2997318A1 EP14723838.0A EP14723838A EP2997318A1 EP 2997318 A1 EP2997318 A1 EP 2997318A1 EP 14723838 A EP14723838 A EP 14723838A EP 2997318 A1 EP2997318 A1 EP 2997318A1
Authority
EP
European Patent Office
Prior art keywords
region
tube
flow channel
refrigerant
capacitor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP14723838.0A
Other languages
German (de)
English (en)
Other versions
EP2997318B1 (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
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 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

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—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 flows through the refrigerant "which has already passed through a portion of the capacitor. 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.
  • 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.
  • One embodiment of the invention relates to a condenser in a stacked disc design, having a first flow channel for a refrigerant and a second flow channel for a coolant, wherein a plurality of disc elements is provided, which stacked to each other adjacent channels form between the disc elements, wherein a first number of channels associated with the first flow channel and a second number of the channels is associated with the second flow channel, wherein the first flow channel has a first region for desuperheating and condensation of the vapor refrigerant and a second region for supercooling 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 et, in fluid communication with the first region, wherein the collector is in fluid communication with the second region via a second connection
  • the construction of a capacitor in stacking disk design is particularly simple and inexpensive to implement. As a rule, a multiplicity of identical disk elements can be used for the construction. Only the outer boundary plates of the disk stack or disk elements in the interior of the disk stack, which have additional functionalities, such as the blocking or deflection of a flow channel, have a different design.
  • a collector into the refrigerant circuit. This is advantageously integrated at a location in the flow channel of the refrigerant at which the refrigerant is already fully condensed, but not yet supercooled.
  • 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 lead the entire refrigerant out of 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 beispielswei- se be achieved via 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 arranged at one of the end regions of the tube in order to generate a defined overflow from the tube into one or more of the flow channels.
  • an outer disk element is meant in particular one of the disk elements, which is the second region, which consists of a stack of several
  • Disc elements is formed, terminates 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 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 chamfered pipe is vorteühaft note by a section through the tube along a plane which is at a predeterminable angle to the central axis of the tube produced. This results in a sweep of the tube.
  • 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.
  • An accordion-like design of 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 stowage or stretching 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 shape-changing ability 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 rough up construction is particularly suitable to compensate for the changes in length that arise when soldering 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.
  • the fluid tightness of the tube can be generated in a simple manner. It may also be expedient if 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 accommodated in a connection element and is connected to it in a fluid-tight manner.
  • connection element can be formed, for example, by a flange on the condenser or on the collector. Furthermore, it is advantageous if the second region has a plurality of flow paths, through which the refrigerant can flow, wherein the flow mungsumblen are each formed by individual channels of the first flow channel and / or 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 refrigerant 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 reinforced once more, 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, thereby achieving the greatest possible temperature between the fluids in the two flow channels.
  • 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 only the second portion of the first flow passage via a pipe leading through a part of the disk stack and forming the fluid inlet into the collector, and the fluid outlet of the accumulator is formed via another pipe "which performs a portion of the disk stack and is in fluid communication only with the first area of the first flow channel.
  • the collector By means of this connection of the collector to the first and the second region of the first flow channel by means of pipes, 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 Fiuidauslass the inner 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 directed through a pipe into a channel of the third flow channel and can also be directed 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.
  • first and second connection element as described above, 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 filtering 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.
  • 1 is a schematic view of a capacitor with a representation of two flow channels, wherein the refrigerant flows through the condenser in series and the coolant flows through the condenser in parallel
  • 2 shows a schematic view of a condenser, according to FIG. 1, wherein the refrigerant flows through the condenser in series and the coolant flows through the condenser in series
  • FIGS. 1 to 2 shows a schematic view of a condenser, according to FIGS. 1 to 2, wherein the refrigerant flows through the condenser in series and the coolant flows through the condenser both serially and parallel,
  • FIGS. 1 to 3 shows a schematic view of a condenser, according to FIGS. 1 to 3, wherein the refrigerant flows through the condenser in series and the coolant flows through the condenser in series, the coolant being conducted through the condenser by means of a pipe
  • FIG View of a condenser according to the figures 1 to 4, wherein the refrigerant flows through the condenser in series and is introduced via a tube from above into the condenser, wherein the coolant flows through the condenser in parallel
  • Fig. 6 is a schematic view of a condenser, wherein the subcooling is increased in comparison to the figures 1 to 5
  • FIG. 8 shows a schematic view of a condenser, wherein an internal heat exchanger is provided in addition to the de-icing area and the sub-cooling area
  • FIG. 9 shows a sectional view through the connection area at which the collector is connected to the condenser
  • 10 is a more detailed sectional view of the connection region according to FIG. 9,
  • 1 1 is a sectional view through the connection region, wherein the tube has two beveled end portions, and
  • Fig. 12 shows two different embodiments of an inventive
  • Pipe wherein in the left part of the figure, a pipe is shown with a flexible region and in the right part of the figure, a multi-part pipe.
  • capacitor 1, 1 a, 70, 80 different embodiments of a capacitor 1, 1 a, 70, 80 are shown in stacked disk design. These are capacitors 1, 1 a, 70, 80 for use in an air conditioning system for motor vehicles. All shown capacitors 1, 1 a, 70, 80 are formed from a plurality of disc elements, which stacked on one another a disk stack 1 1, 1 1a, 73, 93 result.
  • the main advantage of the construction as a condenser 1, 1 a, 70, 80 in stacking disk design is that the disc 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 , deviate from the fundamentally identical shape of the disc elements. This allows a low-cost and easy production.
  • the capacitors 1, 1 a, 70, 80 are indicated only by a schematic diagram.
  • the individual portions of the capacitors 1, 1 a, 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.
  • 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 or of the refrigerant are also indicated only schematically in FIGS. 1 to 8.
  • Each of the parallelepiped-shaped elements is flown through in each case only once from a coolant channel or a coolant channel in FIGS.
  • This illustration is intended to illustrate only the flow principle of the individual capacitors 1, 1 a, 70, 80 and has no delimiting or limiting 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.
  • the flow directions of the refrigerant and of the coolant shown in FIGS. 1 to 8 each represent only one example and can also be executed in opposite directions to the directions shown in FIGS. 1 to 8.
  • FIG. 1 shows a condenser 1, which consists of a desuperheating area 3 and a subcooling area 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 section 4 is connected. In this subcooling region 4, 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 in Unterküh I Scheme 4 with the flow channel 25 of the refrigerant in fluid communication
  • the fluid inlet 6 of the collector 2 is in turn with the flow channel 25 of the refrigerant in the desaturation 3 in fluid communication.
  • 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 fluid overflow from the desuperheating 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.
  • 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 1 1 fluid inlet 7 in the Enthitzungs Scheme 3 of the condenser 1. There it flows through the channels formed by the disk 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 out of the condenser 1 through the fluid outlet 8 at the upper end region.
  • 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 1 1 and distributed over the width of the capacitor first After the coolant has flowed over the entire width of the condenser 1, it then flows out of the condenser 1 through a plurality of openings in the disc elements from bottom to top through the fluid outlet 10.
  • the openings through which the coolant in the condenser 1 flows downwards, or the openings through which the coolant flows in the condenser 1 upwards, are each in alignment with one another. In the condenser 1 results in the construction of both countercurrently flowed through areas as well as in the DC flow areas.
  • FIG. 2 shows a similar construction as has already been shown in FIG.
  • the flow channel 25 of the refrigerant is arranged analogously to FIG. 1 through the condenser 1 of FIG.
  • the coolant in FIG. 2 no longer flows in parallel through the channels of the condenser 1, but instead flows through the condenser 1 in series, as does the refrigerant.
  • 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 through a further opening down into the Enthitzungsbe- area. 3 flows. 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 figure 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 condenser 1 analogous to FIGS. 1 and 2.
  • the refrigerant flow channel 25 is designed analogously to FIGS. 1 and 2.
  • the flow channel 42 of the coolant is now arranged inside the condenser 1 in such a way that both regions are created which are flowed through in parallel, as well as regions which are flowed through in series.
  • 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 where 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 FIGS. 1 to 3.
  • 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 in an underlying part of the subcooling 4 and also distributed again over the entire width of the capacitor. 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.
  • the coolant can be led out of the desuperheating area 3 through the entire subcooling area 4 out of the condenser 1, without it being possible for the coolant to be mixed 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 capacitor 1.
  • the course and the orientation of the coolant channel 26 correspond to the course already shown in FIG.
  • the course of the refrigerant channel 60 also largely corresponds to 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 Enthitzungsberetch 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 the supercooling 4.
  • Figure 6 shows a further view of a capacitor 1 a, As in the preceding figures 1 to 5.
  • the condenser 1a now has a further subcooling path.
  • the subcooling region 4a is thus larger and has more channels than the subcooling region 4 of the preceding FIGS. 1 to 5.
  • the flow guidance of the first flow channel 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 compared to the arrangement of Fluid outlet 8 of Figure 1 changed.
  • the fluid outlet 8a is arranged in contrast to Figure 1 on the opposite side of the capacitor 1 a.
  • the fluid inlet 7 and the fluid outlet 8a lie in a common alignment.
  • the number of channels, which are 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 1 1 a. There is always a higher number or a lower number vorseh bar.
  • the embodiments shown here have no limiting character in this regard.
  • FIG. 7 shows an exemplary embodiment of a capacitor 70, wherein the subcooling region 71 is represented by two cuboidal elements.
  • the de-icing region 72 is 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.
  • pipes 77 of different lengths, each of which produces a fluidic connection to the channels of the first flow channel, are shown at the fluid inlet 74 of the collector 75 and the fluid outlet 76.
  • FIG. 8 shows a condenser 80 with a de-icing region 81 at the lower end region of the condenser 80 and two super-cooling regions 82 located above it.
  • the condenser 80 is essentially 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. Furthermore, the fluid inlet 88 of the first flow channel 87 is arranged at the lower end region.
  • the flow through the Enthitzungs Schemes 81 and the subcooling 82 with the refrigerant is done serially similar to the representations of Figures 1 to 4. Above the subcooling 82, a further cuboidal element is shown. 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 internal 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.
  • the positions of the fluid inlets or fluid outlets shown in FIGS. 1 to 8 are each by way of example. Deviating orientations, for example at the side of the condensate Tor, are as predictable as the arrangement of a fluid inlet or fluid outlet in a central region of the capacitors.
  • the capacitors 1, 1 a, 70, 80 are selectively produced from a combination of Enthitzungs Society 3, 72, 81, subcooling 4, 71, 82 and inner 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.
  • 53, 63, 77 are also inexpensive to manufacture and are introduced in the simplest case in the disc stack 1 1, 1 a, 73, 92, thereby leading through inner openings of the disc 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.
  • FIG. 9 shows in particular the connection region to which a collector (not shown) is connected to the disk stack of the capacitor 100 via a flange 102.
  • 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 Scheibeneiement 105 is shown in the following Figure 10. From the inlet 104, 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 shown in FIG.
  • FIG. 10 shows a detailed view of the arrangement of the tube 101, as already shown in FIG. It can be seen in Figure 10 in particular as 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 above the bore of the drain 103 bore.
  • 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 Abiauf 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 produced in FIG. 10 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 12 formed around the opening through which the tube 101 is inserted.
  • a flow channel 107 is formed, below the disk element 105 is a Strömungskana! 109 trained.
  • multiple numbers of flow channels can also be provided above and below the disk element 105.
  • the representation of FIG. 10 is exemplary.
  • the tube 101 is primarily connected to the disc member 105, this can be achieved for example by a gluing process or a soldering process.
  • the flange 102 is attached to a lower disc element 1 10 by means of connecting elements 1 1 1.
  • the disk element 110 has an opening which has a downwardly directed passage.
  • the connecting means 1 1 1 are formed in the figure 10 via 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 1 10 may also be provided, for example, a glue 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 chamfer both at the upper end region 126 and at the lower end region 127. This bevel is achieved by a cut, which in a plane which is at a 'predeterminable angle to the central axis of the tube 125 has been generated.
  • 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 disc for the flow channel 123 shown, the lower disc member 129 forms a flow disc 123 for the flow channel.
  • 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 against a surface both with an end region 126 and thereby position the tube 125 as well as a suitable fluid transfer surface form the tube 125 in the flow channel or of 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.
  • the pipe can be supported in the flange 120 via this beveled end region and, at the same time, form a suitable flow cross-section for the fluid passing out of the drain 121 into the pipe 125.
  • FIG. 12 shows two exemplary embodiments of a tube 140 or 150.
  • the tube 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.
  • 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.
  • 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 design of the tubes 140 and 150 of Figure 12 is exemplary.
  • the embodiments of Figure 12 have no limiting character with regard to the design of the tube.
  • FIGS. 9 to 12 The illustration of the connection of a pipe or a flange to a condenser shown in FIGS. 9 to 12 is likewise exemplary.
  • the various tubes shown in FIGS. 9 to 12 may be combined as desired with the different capacitors of FIGS. 1 to 8.
  • the tubes shown in FIGS. 9 to 12 can be used both for connecting the collectors and for connecting channels with fluid inlets and fluid outlets in the remaining region 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)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Fixed Capacitors And Capacitor Manufacturing Machines (AREA)

Abstract

L'invention concerne un condenseur (1, 1a, 70, 80, 100) de type à plaques empilées, comprenant un premier canal d'écoulement (25, 25a, 80, 87) pour un fluide frigorigène et un deuxième canal d'écoulement (28, 26a, 32, 42, 52, 85) pour un fluide de refroidissement. Une pluralité d'éléments plaques, une fois empilés, forment des canaux adjacents entre les éléments plaques. Un premier nombre de ces canaux est associé au premier canal d'écoulement (25, 25a, 80, 87) et un deuxième nombre de ces canaux est associé au deuxième canal d'écoulement (28, 26a, 32, 42, 52, 85). Le premier canal d'écoulement (25, 25a, 80, 87) comporte une première zone (3, 72, 81) de désurchauffe et de condensation du fluide frigorigène à l'état de vapeur et une deuxième zone (4, 71, 82) de sous-refroidissement du fluide frigorigène condensé. Le condenseur comprend également un collecteur (2) servant à stocker le fluide frigorigène, un débordement du fluide frigorigène hors de la première zone vers la deuxième (4, 71, 82) zone traversant le collecteur (2). Le collecteur (2) est en communication fluidique avec la première zone (3, 72, 81) par l'intermédiaire d'un premier élément de raccordement qui forme un premier raccordement fluidique du collecteur (2), le collecteur (2) est en communication fluidique avec la deuxième zone (4, 71, 82) par l'intermédiaire d'un deuxième élément de raccordement qui forme un deuxième raccordement fluidique du collecteur (2), le premier élément de raccordement et/ou le deuxième élément de raccordement étant formés d'un tube (5, 101, 125, 140, 150) qui traverse un certain nombre d'éléments plaques par des ouvertures ménagées dans les éléments plaques.
EP14723838.0A 2013-05-16 2014-05-15 Condenseur Active EP2997318B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013209157.5A DE102013209157A1 (de) 2013-05-16 2013-05-16 Kondensator
PCT/EP2014/060024 WO2014184323A1 (fr) 2013-05-16 2014-05-15 Condenseur

Publications (2)

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

Family

ID=50721813

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14723838.0A Active EP2997318B1 (fr) 2013-05-16 2014-05-15 Condenseur

Country Status (7)

Country Link
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)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6315191B2 (ja) * 2014-04-25 2018-04-25 パナソニックＩｐマネジメント株式会社 熱交換器
JP6719570B2 (ja) * 2016-09-30 2020-07-08 三菱電機株式会社 冷凍サイクル装置
EP3572753B1 (fr) * 2018-05-24 2020-12-16 Valeo Autosystemy SP. Z.O.O. Échangeur de chaleur
JP7400234B2 (ja) * 2019-07-16 2023-12-19 株式会社デンソー 熱交換器
DE102020215226A1 (de) 2020-12-02 2022-06-02 Mahle International Gmbh Sammler eines Kältemittelkreislaufs
DE102021113750A1 (de) * 2021-05-27 2022-12-01 Valeo Klimasysteme Gmbh Wärmetauscher für ein Kraftfahrzeug
FR3128521B1 (fr) * 2021-10-21 2023-10-27 Valeo Systemes Thermiques Echangeur thermique avec conduits de circulation

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE506845C2 (sv) * 1996-06-28 1998-02-16 Alfa Laval Ab Plattvärmeväxlare med bälgförsett foder till anslutningsrör
JP2002310592A (ja) * 2001-04-13 2002-10-23 Sanden Corp 積層型熱交換器
FR2846733B1 (fr) 2002-10-31 2006-09-15 Valeo Thermique Moteur Sa Condenseur, notamment pour un circuit de cimatisation de vehicule automobile, et circuit comprenant ce condenseur
JP4334965B2 (ja) * 2003-09-30 2009-09-30 株式会社日阪製作所 プレート式熱交換器
FR2924490A1 (fr) * 2007-11-29 2009-06-05 Valeo Systemes Thermiques Condenseur pour circuit de climatisation avec partie de sous-refroidissement
FR2950682B1 (fr) * 2009-09-30 2012-06-01 Valeo Systemes Thermiques Condenseur pour vehicule automobile a integration amelioree
DE102010026507A1 (de) * 2010-07-07 2012-01-12 Behr Gmbh & Co. Kg Kältemittelkondensatormodul
JP5960955B2 (ja) * 2010-12-03 2016-08-02 現代自動車株式会社Ｈｙｕｎｄａｉ Ｍｏｔｏｒ Ｃｏｍｐａｎｙ 車両用コンデンサ
DE102011008429A1 (de) * 2011-01-12 2012-07-12 Behr Gmbh & Co. Kg Vorrichtung zur Wärmeübertragung für ein Fahrzeug
US9239193B2 (en) * 2011-02-17 2016-01-19 Delphi Technologies, Inc. Unitary heat pump air conditioner having a heat exchanger with an integral receiver and sub-cooler
DE102011078136A1 (de) * 2011-06-27 2012-12-27 Behr Gmbh & Co. Kg Kältemittelkondensatormodul
JP5295330B2 (ja) * 2011-08-08 2013-09-18 三菱電機株式会社 プレート式熱交換器及び冷凍空調装置
KR101316859B1 (ko) * 2011-12-08 2013-10-10 현대자동차주식회사 차량용 컨덴서
DE102012217087A1 (de) * 2012-09-21 2014-03-27 Behr Gmbh & Co. Kg Kondensator

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2014184323A1 *

Also Published As

Publication number Publication date
BR112015026951A2 (pt) 2017-07-25
JP2016519279A (ja) 2016-06-30
CN105431691A (zh) 2016-03-23
US10088204B2 (en) 2018-10-02
DE102013209157A1 (de) 2014-12-04
EP2997318B1 (fr) 2019-02-06
US20160091229A1 (en) 2016-03-31
CN105431691B (zh) 2018-01-09
WO2014184323A1 (fr) 2014-11-20
DE112014002420A5 (de) 2016-01-28
JP6461104B2 (ja) 2019-01-30

Similar Documents

Publication Publication Date Title
EP2997318B1 (fr) Condenseur
EP2909563B1 (fr) Condenseur
EP1724536B1 (fr) Echangeur de chaleur avec partie accumulatrice
EP3119623B1 (fr) Module de chauffage et de refroidissement
EP0521298A2 (fr) Dispositif d'échange de chaleur pour séchoir par réfrigération dans les installations d'air comprimé et échangeur de chaleur à tubes et plaques pour cette application
DE102012024722A1 (de) Verdampfer und Verfahren zur Luftaufbereitung
WO2015140034A1 (fr) Module de chauffage et de refroidissement
DE102013217287A1 (de) Innerer Wärmeübertrager für einen Kältemittelkreislauf, insbesondere für eine Klimaanlage eines Kraftfahrzeuges, und einen Kältemittelkreislauf mit einem Verdampfer
DE102007013125A1 (de) Wärmeübertrager
EP1272804A2 (fr) Echangeur de chaleur pour un climatiseur de vehicule au co2
EP2926073B1 (fr) Échangeur thermique
DE102019119124A1 (de) Kombinationswärmetauscher mit einem Chiller und einem inneren Wärmetauscher sowie Kühl-Kälte-Kreislaufsystem und Kraftfahrzeug mit einem solchen
EP2937658B1 (fr) Fluide caloporteur interne
DE102012209431A1 (de) Effizienter innerer Wärmeübertrager
DE102012223722A1 (de) Effizienter innerer Wärmeübertrager
DE112016000963T5 (de) Kältemittel-Verdampfer
WO2014095594A1 (fr) Échangeur de chaleur
EP2711658A2 (fr) Echangeur de chaleur
DE4118289A1 (de) Waermetauscher-vorrichtung fuer kaeltetrockner an druckluftanlagen
WO2017097634A1 (fr) Échangeur de chaleur, en particulier pour un véhicule automobile, muni de conduites de fluide flexibles et d'une structure de retenue
DE102011089091A1 (de) Wärmeübertrager
WO2016116345A1 (fr) Échangeur de chaleur à plaques empilées
EP2570754A2 (fr) Système d'évaporateur multi-canal
DE102022211047A1 (de) Wärmeübertrager
DE102022212155A1 (de) Wärmeübertrager

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20151216

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RIN1 Information on inventor provided before grant (corrected)

Inventor name: MAGER, THOMAS

Inventor name: WALTER, CHRISTOPH

Inventor name: EIBNER, HELMUT

Inventor name: HOFMANN, HERBERT

Inventor name: FOERSTER, UWE

Inventor name: FOERSTER, KLAUS

Inventor name: MAYOR TONDA, DAVID

Inventor name: KAESTLE, CHRISTOPH

Inventor name: STRIEGE, HOLGER

Inventor name: PFLIEGER, MARKUS

Inventor name: KASPAR, MARTIN

Inventor name: DRAENKOW, ANDREAS

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20180906

GRAJ Information related to disapproval of communication of intention to grant by the applicant or resumption of examination proceedings by the epo deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

GRAR Information related to intention to grant a patent recorded

Free format text: ORIGINAL CODE: EPIDOSNIGR71

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

INTC Intention to grant announced (deleted)
RIN1 Information on inventor provided before grant (corrected)

Inventor name: HOFMANN, HERBERT

Inventor name: PFLIEGER, MARKUS

Inventor name: MAGER, THOMAS

Inventor name: KASPAR, MARTIN

Inventor name: STRIEGE, HOLGER

Inventor name: DRAENKOW, ANDREAS

Inventor name: WALTER, CHRISTOPH

Inventor name: FOERSTER, UWE

Inventor name: EIBNER, HELMUT

Inventor name: KAESTLE, CHRISTOPH

Inventor name: MAYOR TONDA, DAVID

Inventor name: FOERSTER, KLAUS

INTG Intention to grant announced

Effective date: 20181220

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 1095170

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190215

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502014010761

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20190206

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190606

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190506

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190507

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190606

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190506

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502014010761

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

26N No opposition filed

Effective date: 20191107

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20190515

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190531

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190531

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20190531

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190515

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190515

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190515

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190531

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190531

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1095170

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190515

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190515

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20140515

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20190206

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20230519

Year of fee payment: 10