[go: up one dir, main page]

EP2606291B1 - Module de condenseur à réfrigérant - Google Patents

Module de condenseur à réfrigérant Download PDF

Info

Publication number
EP2606291B1
EP2606291B1 EP11745804.2A EP11745804A EP2606291B1 EP 2606291 B1 EP2606291 B1 EP 2606291B1 EP 11745804 A EP11745804 A EP 11745804A EP 2606291 B1 EP2606291 B1 EP 2606291B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
cooling tubes
supercooling
region
condenser assembly
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
EP11745804.2A
Other languages
German (de)
English (en)
Other versions
EP2606291A1 (fr
Inventor
Guillaume David
Uwe FÖRSTER
Matthias Jung
Andreas Kemle
Christoph Walter
Herbert Hofmann
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 Behr GmbH and Co KG
Original Assignee
Mahle Behr GmbH and Co KG
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 Behr GmbH and Co KG filed Critical Mahle Behr GmbH and Co KG
Publication of EP2606291A1 publication Critical patent/EP2606291A1/fr
Application granted granted Critical
Publication of EP2606291B1 publication Critical patent/EP2606291B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/04—Desuperheaters
    • 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 present invention relates to a refrigerant condenser assembly according to the preambles of claim 1.
  • refrigerant condenser assemblies for a power tool air conditioning system
  • vaporous refrigerant is converted into a liquid state of aggregation and then the liquid refrigerant is further "subcooled" in a subcooling region.
  • the refrigerant condenser assembly forms part of a refrigeration circuit of an automotive air conditioning system with an evaporator, an expansion device and a compressor.
  • the DE 10 2007 018 722 A1 shows a condenser for the air conditioning system of a motor vehicle having two manifolds and a container arranged adjacent to the one collecting tube for receiving the desiccant of the refrigerant of the air conditioner.
  • the refrigeration cycle of an automotive air conditioning system is reduced by up to 10%.
  • the performance of a refrigeration circuit in a Kraftmairnastrom can be increased inter alia, that at a subcooling of the refrigerant condenser assembly, the already liquefied refrigerant is cooled more.
  • the refrigerant in gaseous form enters the refrigerant condenser assembly at an inlet port and is cooled to a saturation temperature at an overheat region. Subsequently, the refrigerant flows into a condensation region and in this the gaseous refrigerant is further cooled and liquefied. Subsequently, the liquid refrigerant flows into a subcooling region and is cooled below the boiling point, for example to a temperature of 6 or 7 K below the boiling temperature of the refrigerant. By a greater cooling of the refrigerant in the Uhterkühlungs Scheme below the boiling point of the refrigerant higher power of the refrigerant circuit can be achieved.
  • the refrigerant capacitor assembly within the motor vehicle a predetermined space, for example given by a certain depth, height and width available, so that although a greater cooling of the refrigerant at the subcooling by a larger surface at the subcooling and a larger space associated therewith
  • refrigerant condenser assembly is possible, but in general due to the predetermined dimensions of the space for the refrigerant condenser assembly no larger space is available.
  • the aim is to increase the subcooling to, for example, 15 K.
  • more cooling tubes or proportionally more area required by the capacitor This has the consequence that less space is available for the condensation area, the cooling takes place at a higher saturation temperature and the associated saturation pressure increases. This causes a negative effect on the cooling capacity in the refrigeration cycle, which reduces or even nullifies the desired advantage.
  • the object of the present invention is to provide a refrigerant condenser assembly in which the refrigerant is strongly cooled in a subcooling region of the refrigerant condenser assembly without substantially increasing the condensing pressure in the refrigerant condenser assembly.
  • a refrigerant condenser assembly for an automotive air conditioning system comprising cooling tubes for passing a refrigerant, two header tubes for fluidly connecting the cooling tubes, preferably a header with at least one overflow opening by means of which the header is in fluid communication with the cooling tubes and / or a header, the cooling tubes an overheating section for cooling the vapor refrigerant, a condensing section for condensing the refrigerant as at least a parallel section, and a subcooling section as a subcooler parallel section for cooling the liquid refrigerant, wherein the flow cross sectional areas of the cooling tubes, particularly all of the cooling tubes, of the subcooling section are smaller than the product of 0.9 or 0.7 or 0.5 and the flow cross-sectional areas of the cooling tubes, in particular of all cooling tubes, the overheating area and / or the condensation area.
  • the flow cross-sectional area is the cross-sectional area of the cooling tubes for passing the refrigerant.
  • the cooling tubes of the subcooling region thus have a smaller flow cross-sectional area than the cooling tubes of the overheating region and / or the condensation region.
  • a smaller flow cross-sectional area can be achieved, for example, by cooling tubes with a smaller cross-sectional area or by cooling tubes with the same cross-sectional area, wherein turbulence inserts in the cooling tubes of the sub-cooling area reduce the flow cross-sectional area.
  • the refrigerant can be cooled more advantageously at the subcooling, for example, to a temperature of 14 K below the boiling temperature of the refrigerant without thereby increasing the dimensions of the refrigerant condenser assembly and thus the refrigerant condenser assembly finds place in a given space of a motor vehicle.
  • the performance of a refrigeration circuit of an automotive air conditioning system can be improved and thereby the power reduction when using the new refrigerant R1234yf be at least partially compensated.
  • An increased pressure drop in the subcooling area is not detrimental to the performance of the refrigerant condenser assembly or performance reducing. This is due to the fact that the pressure drop takes place after the wet steam area, while the system's high pressure is oriented at the saturation temperature before the subcooling area or after the condensation area.
  • At least two cooling tubes act as the first subcooler in parallel with the refrigerant
  • the refrigerant flowing out of the first subcooler enters into a first subcooling passage and the first subcooling passage opens into at least two cooling tubes as the second subcooler and preferably flows into the subcooling region second subcooling parallel section into a second subcooling intermediate flow channel and the second subcooling intermediate flow channel opens into at least two cooling tubes as the third subcooler parallel section.
  • the subcooling region of the refrigerant condenser assembly is thus divided into a total of two or three subcooler parallel sections, each interconnected by the subcooling intercooler passage. As a result, the refrigerant at the subcooling region can be cooled even further below the boiling point of the refrigerant.
  • the subcooling region of the refrigerant condenser assembly is thus subdivided into a first and a second subcooler parallel section, and in the subcooler parallel sections, at least two cooling tubes are respectively hydraulically or fluid-conductively supplied in parallel with the refrigerant.
  • the refrigerant exiting from the first subcooler parallel section is introduced into and mixed in a first subcooling intermediate flow channel, and the refrigerant is introduced into the second subcooler parallel section from the first subcooling intermediate flow channel.
  • the refrigerant is conducted in parallel in the subcooling region, for example, by four, seven or nine cooling tubes.
  • the first and second subcooler parallel sections have, for example, two, three or five cooling tubes.
  • the refrigerant has a smaller flow cross-sectional area at the first and second subcooler parallel sections as in the refrigerant condenser assembly known in the art, thereby causing a larger flow velocity of the refrigerant to occur at the subcooling region and thereby improve or increase the heat transfer from the refrigerant to the air flowing around the refrigerant condenser assembly.
  • one subcooler parallel section or the subcooling region between two or eight cooling tubes acted upon in parallel and / or the surface of the cooling tubes and preferably the headers of the subcooling region is less than 50%, 40%, 35%, 30%, 25% or 15% of the surface of the heat exchanger of the refrigerant condenser assembly and in particular, the heat exchanger consists of the cooling tubes and preferably the headers.
  • At least two cooling tubes are acted upon as a first parallel section in a fluid-conducting manner in parallel.
  • the refrigerant flowing out of the first parallel section opens into a first intermediate flow channel and the first intermediate flow channel opens into at least two cooling tubes as the second parallel section.
  • a first and a second parallel section In the flow direction of the refrigerant before the first subcooler parallel section, ie before the subcooling region of the refrigerant condenser group, ie thus at the overheating region and / or at the condensation region of the refrigerant condenser assembly is thus arranged a first and a second parallel section.
  • the overheating region and / or the condensation region are subdivided into the first and second subcooler parallel sections between which the refrigerant is conducted through the first intermediate flow channel.
  • the refrigerant flowing out of the second parallel section opens into a second intermediate flow channel and the second intermediate flow channel opens into at least two cooling tubes as the third parallel section.
  • the refrigerant condenser assembly is divided into a total of three parallel sections with at least two, preferably at least four or six or eight, cooling tubes, which are each fluid-conductively connected to each other through the intermediate flow channel.
  • a parallel section has a greater number of cooling tubes than a subcooler parallel section, and preferably the number of cooling tubes of a parallel section is two, three, five or seven cooling tubes greater than the number of cooling tubes of a subcooler parallel section.
  • the second parallel section opens into a second intermediate flow channel and the second intermediate flow channel opens into the collecting container or the third parallel section opens into a third intermediate flow channel and the third intermediate flow channel opens into the collecting container.
  • the overheating and / or condensation region of the refrigerant condenser assembly has the first and second parallel sections, then the refrigerant discharged from the second parallel section is introduced into the first subcooler section, or the overheating and / or condenser section has three parallel sections, that of the third parallel section discharged refrigerant introduced into the first subcooler parallel section, wherein in each case between condensing region and subcooling of the collecting container is arranged.
  • the overheating and / or condensation region is subdivided into more than three parallel sections, for example four or five parallel sections.
  • the sum of the flow cross-sectional areas of all the cooling tubes of a subcooler parallel section is smaller than the product of 1.0 or 0.9 or 0.7 or 0.5 or 0.3 or 0.1 and the sum of the flow cross-sectional areas of all the cooling tubes of a parallel section and / or the cooling tubes are formed as flat tubes and corrugated ribs are arranged between the flat tubes.
  • the filling amount of refrigerant can be reduced.
  • the cost can be reduced.
  • the width of the cooling tubes, in particular of all cooling tubes, a subcooling parallel section or the subcooling region is smaller than the product of 1.0 or 0.9 or 0.7 or 0.5 or 0.3 or 0.1 and the width of the Cooling tubes, in particular all cooling tubes, a parallel section.
  • the heat transfer in the subcooling can also be controlled by the individual corrugated fins, which are arranged between the individual cooling tubes.
  • the corrugated fins have a different geometry in the subcooling region than the corrugated fins in the overheating region and / or condensation region.
  • the corrugated fins in the subcooling region are preferably designed such that the air-side heat transfer in this region increases or improves.
  • the corrugated fins in the subcooling region could be of the same height as in the overheating region and / or condensation region, but have a different geometry due to increased corrugated rib density or gill fields, which improves the heat transfer in this region.
  • the corrugated fins in the subcooling region could be designed with a lower height than in the overheating region and / or condensation region.
  • narrower cooling tubes could be used in the subcooling area in order to increase the flow velocity and thus the heat transfer.
  • the corrugated fins could be designed in the subcooling with a higher height than in the overheating area and / or condensation area. In this case, the air-side heat transfer would be deteriorated. However, since fewer cooling tubes are arranged in parallel on the refrigerant side, the heat transfer on the refrigerant side would increase.
  • a method for operating a refrigeration cycle of an automotive air conditioning system comprising the steps of: passing refrigerant through conduits of a refrigerant circuit, compressing the gaseous refrigerant in a compressor so that the pressure of the gaseous refrigerant is increased, cooling and condensing the gaseous refrigerant in a refrigerant condenser assembly passed through cooling tubes by cooling the gaseous refrigerant in an overheating region to a saturation temperature, then cooling and liquefying the gaseous refrigerant to a boiling temperature in a condensation region and cooling the liquid refrigerant below the boiling temperature in a subcooling region; expanding the liquid Refrigerant on an expansion device, so that the pressure of the liquid refrigerant is reduced, heating and evaporation of the refrigerant in an evaporator, Le In the subcooling region, the refrigerant flows through cooling tubes with a smaller flow cross-sectional area into the gaseous refrigerant exiting from the steps of:
  • the refrigerant in the subcooling area, is passed in parallel through at least two cooling pipes of a first subcooler parallel section, the refrigerant flowing out of the first subcooling section is directed into a first subcooling intermediate channel, and the refrigerant passed through the first subcooling air channel is then passed in parallel through at least two cooling pipes of a second subcooler parallel section / or the condensation region and / or the refrigerant in the subcooling region is cooled by more than 7, 10, 12 or 14 K and is preferably cooled by less than 30 K or 20 K.
  • an automotive air conditioning system comprises a refrigerant condenser assembly, an evaporator, a compressor, preferably a blower, preferably a housing for accommodating the blower and the evaporator, the chill condenser assembly being a refrigerant condenser assembly described in this specification is formed and / or the vehicle air conditioning system described in this description method is executable.
  • the refrigerant is R1234yf or R134a.
  • the refrigerant condenser assembly has a closure device formed on the collecting container for closing a closure opening of the collecting container.
  • a dryer and / or a filter are arranged in the collecting container and / or in the closure device.
  • FIG. 1 and 2 a refrigerant condenser assembly 1 is shown in a perspective view.
  • the refrigerant condenser assembly 1 is part of an automotive air conditioning system with an evaporator and a compressor (not shown).
  • By horizontally arranged cooling tubes 2 as flat tubes 3 flows to be condensed and cooled refrigerant ( Fig. 1 and 2 ).
  • the cooling tubes 2 open at their respective ends in a vertical manifold 5, that is, there are two manifolds 5 respectively at the ends of the cooling tubes 2.
  • the collecting tube 5 has cooling tube openings through which the ends of the cooling tubes 2 project into the collecting tube 5.
  • baffles (not shown) are formed with which a certain flow path of the refrigerant can be achieved through the cooling tubes 2, so that the refrigerant through the cooling tubes 2 according to the flow diagram in Fig. 3 flows through the cooling tubes 2.
  • the cooling tubes 2 meandering corrugated fins 4 are arranged, which are in thermal communication with the cooling tubes 2 by means of heat conduction. This increases the area available for cooling the refrigerant.
  • the cooling tubes 2, the corrugated fins 4 and the two manifolds 4 are generally made of metal, in particular aluminum, and are materially connected together as a solder joint.
  • a fastening device 8 is arranged, with which the Kälternittelkondensatorbauteen on a motor vehicle, in particular on a body of a motor vehicle, can be attached.
  • a collecting container 6 is arranged ( Fig. 1 . 2 ).
  • the collecting container 6 is by means of two overflow openings (not shown) in fluid communication with the collecting tube 5 and thus also indirectly in fluid communication with the cooling tubes 2.
  • a dryer and a filter (not shown) is arranged in the collecting container 6.
  • the dryer is hygroscopic and can absorb water or moisture from the refrigerant.
  • the collecting container 6 is mechanically connected to the collecting tube 5 at the lower and upper ends with a concave support region. At the lower end of the collecting container 6 is closed by a closure device 7 fluid-tight.
  • the removable closure device 7 allows replacement of the dryer and filter in the sump 6.
  • the refrigerant condenser assembly 1 has an inlet port 9 for introducing the refrigerant R1234yf into the refrigerant condenser assembly 1, and an outlet port 10 for discharging the refrigerant from the refrigerant condenser assembly 1 (FIG. Fig. 1 and 3 ).
  • the ends of the cooling tubes 2 terminate in the manifolds 5.
  • baffles or flow guide plates, not shown, are arranged by means of which a certain predetermined flow diagram of the refrigerant can be achieved, ie with which flow path the refrigerant through the plurality of stacked Cooling tubes 2 of the refrigerant condenser assembly 1 flows. This in Fig.
  • the illustrated flow pattern serves only to illustrate the flow path of the refrigerant through the cooling tubes 2 and does not represent a geometric orientation of the cooling tubes 2 to each other in the refrigerant capacitor assembly 1.
  • a first intermediate flow passage 20, a second intermediate flow passage 22, a third intermediate flow passage 24 and a first sub-cooling intermediate flow passage 15th , what a Fig. 3 are shown are thus formed within the manifolds 5 of the flow guide plates, not shown.
  • the refrigerant condenser assembly 1 constitutes a heat exchanger for transferring heat from the refrigerant to air surrounding and circulating around the refrigerant condenser assembly 1.
  • the heat exchanger is essentially formed by the cooling tubes 2 and the two manifolds 5.
  • the heat exchanger as part of the refrigerant condenser assembly 1 in this case has an inlet opening 9 through which gaseous refrigerant is passed from a compressor, not shown, to the refrigerant condenser assembly 1.
  • the gaseous refrigerant is at an overheating region 11 to a saturation temperature cooled, ie at the saturation temperature occurs according to the existing pressure, a condensation of the refrigerant.
  • condensation region 12 follows, in which the refrigerant is condensed and thus liquefied.
  • the refrigerant liquefied in the condensation region 12 is supplied as liquid to the subcooling region 13 and cooled in the subcooling region 13 below the boiling temperature of the refrigerant.
  • condensation region 12 and subcooling region 13 may differ slightly during operation of an automotive air conditioning system, so that, for example, in a modification of the illustration in FIG Fig. 3 the overheating region 11 is slightly larger and thereby the condensation region 12 becomes smaller, so that, for example, a second parallel section 21 also partially forms the overheating region 11.
  • the overheating region and the condensation region may be arranged in exactly one parallel section.
  • the overheating region 11 is formed by the first parallel section 19.
  • the first parallel section 19 has eleven cooling tubes which are connected in parallel or flow through in a fluid-conducting or hydraulic manner. After flowing out of the refrigerant from the eleven cooling tubes 2 of the first parallel section 19, the refrigerant is introduced into the first intermediate flow passage 20 and introduced from the first intermediate flow passage 20 into the second parallel section 21.
  • the second parallel section 21 has eight cooling tubes 2, through which the refrigerant flows simultaneously in parallel. The refrigerant flowing out of the second parallel section 21 is introduced into the second intermediate flow passage 22 and introduced therefrom into the third parallel section 23 with likewise eight cooling tubes 2.
  • the refrigerant flowing out of the third parallel section 23 is introduced into the third intermediate flow passage 24, and is then supplied to the subcooling section 13 of the refrigerant condenser assembly 1.
  • the subcooling region 13 comprises a first subcooling parallel section 14 and a second subcooling parallel section 16.
  • the two subcooler parallel sections 14, 16 each have six cooling tubes 2.
  • the first sub-cooling parallel section 14 is connected to the second sub-cooling parallel section 16 through the first sub-cooling intermediate flow passage 15.
  • the parallel sections 19, 21 and 23 and the subcooler parallel sections 14, 16 are fluidly connected in series and the cooling tubes 2 at the parallel sections 19, 21 and 23 and at the subcool parallel sections 14, 16 and 18 are hydraulically or fluidly parallel connected.
  • the entire refrigerant passed through the refrigerant condenser assembly 1 thus flows through the respective parallel sections 19, 21 and 23 and the subcooler parallel sections 14, 16.
  • the subcooler parallel sections 14, 16 have a smaller number of cooling tubes 2 than the parallel sections 19, 21 and 23.
  • the flow cross-sectional area of the cooling tubes 2 of the subcooler parallel sections 14, 16 smaller than the flow cross-sectional area of the cooling tubes 2 of the parallel sections 19, 21 and 23, because the width of the cooling tubes 2 as flat tubes 3 at the parallel sections 19, 21, 23 1.8 mm and the width of Cooling tubes 2 at the subcooler parallel sections 14, 16 is 1.3 mm.
  • the distance between the cooling tubes 2 in the sub-cooling parallel sections 14, 16 with 6 mm smaller than the distance between the cooling tubes of the parallel sections 19, 21, 23 with 8 mm, so that the height of the corrugated fins 4 at the parallel sections 19, 21, 23 with 8 mm is greater than the height of the corrugated fins 4 at the sub-cooling parallel sections 14, 16 with 6 mm.
  • the width of the cooling tubes 2 in this case represents the expansion in a cross section of the cooling tubes 2 and the length of the cooling tubes 2 in the cross section corresponds to the depth of the refrigerant condenser assembly 1 to the cooling tubes 2, ie the expansion in the flow direction of the air passing through between the cooling tubes 2 the refrigerant condenser assembly 1 flows.
  • the refrigerant at the subcooler parallel sections 14, 16 Due to the fluid-conducting or hydraulic circuit of the refrigerant condenser assembly 1 is thus the refrigerant at the subcooler parallel sections 14, 16 a much smaller flow cross-sectional area than at the parallel sections 19, 21 and 23, because the cooling tubes 2 have different flow cross-sectional areas and further the number of cooling tubes. 2 is preferably smaller at the subcooler parallel sections 14, 16 than at the parallel sections 19, 21, and 23. As a result, the flow velocity is adjusted according to the density change.
  • the heat transfer from the refrigerant to the air in the subcooling region 13 can be increased, thereby transferring more heat from the refrigerant to the air flowing around the refrigerant condenser assembly 1
  • the refrigerant in the subcooling 13 are cooled more below the boiling temperature of the refrigerant, for example, be cooled by 14 K below the boiling temperature of the refrigerant. This can be increased advantageously the COP of a refrigerant circuit.
  • the pressure drop in the refrigerant condenser assembly 1 is not or only very slightly increased, so that the high pressure at the inlet opening 9 only slightly increases and thus the performance increase of the refrigeration circuit due to the greater cooling at the subcooling region 13 is substantially greater than the power reduction due to the possible increase of the high pressure at the inlet opening 9 is.
  • the overheating and condensation region 11, 12 may have only one or two parallel sections 19, 21.
  • the volume flow at the subcooling region 13 is greatly increased due to the smaller flow cross sectional area of the cooling tubes 2 in the subcooling region 13, and preferably because of the predetermined flow diagram, so that a stronger subcooling or cooling of the refrigerant can be achieved at the subcooling region 13 without the refrigerant condenser assembly 1 more Required space or surface, because due to the larger volume flow, the heat transfer from the refrigerant per surface unit of the refrigerant condenser assembly 1, in particular to the cooling tubes 2, the corrugated fins 4 or the manifolds 5 as a heat exchanger of the refrigerant condenser assembly 1, is increased.
  • the COP of a refrigeration circuit with the refrigerant condenser assembly 1 can be increased without requiring additional space for the refrigerant condenser assembly 1.
  • the reduction in COP due to the use of the refrigerant R1234yf can be at least partially compensated.

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)

Claims (9)

  1. Ensemble de condenseur de fluide frigorigène (1) pour un système de climatisation d'un véhicule automobile, ledit ensemble de condenseur comprenant :
    - des tubes de refroidissement (2) servant à la circulation d'un fluide frigorigène,
    - deux tubes collecteurs (5) servant à la communication fluidique des tubes de refroidissement (2),
    - de préférence un réservoir collecteur (6) comprenant au moins une ouverture de trop-plein au moyen de laquelle le réservoir collecteur (6) est en communication fluidique avec les tubes de refroidissement (2) et / ou avec le tube collecteur (5),
    - les tubes de refroidissement (2) présentent, considérées comme au moins une partie parallèle (19, 21, 23), une zone de surchauffe (11) servant au refroidissement du fluide frigorigène à l'état de vapeur, une zone de condensation (12) servant à la condensation du fluide frigorigène, et présentent, considérée comme une partie parallèle de surrefroidissement, une zone de surrefroidissement (13) servant au refroidissement du fluide frigorigène liquide,
    caractérisé
    en ce que les surfaces de section d'écoulement des tubes de refroidissement (2) de la zone de surrefroidissement (13) sont inférieures au produit de 0,9 ou de 0,7 ou de 0,5, et des surfaces de section d'écoulement des tubes de refroidissement (2) de la zone de surchauffe (11) et de la zone de condensation (12).
  2. Ensemble de condenseur de fluide frigorigène selon la revendication 1, caractérisé en ce que, dans la zone de surrefroidissement (13), au moins deux tubes de refroidissement (2) considérés comme première partie parallèle de surrefroidissement (14), acheminant du fluide, sont alimentés parallèlement en fluide frigorigène, en ce que le fluide frigorigène sortant de la première partie parallèle de surrefroidissement (14) débouche dans un premier conduit d'écoulement intermédiaire de surrefroidissement (15), et le premier conduit d'écoulement intermédiaire de surrefroidissement (15) débouche dans au moins deux tubes de refroidissement (2) considérés comme deuxième partie parallèle de surrefroidissement (16), et en ce que, de préférence dans la zone de surrefroidissement (13), la deuxième partie parallèle de surrefroidissement (16) débouche dans un deuxième conduit d'écoulement intermédiaire de surrefroidissement, et le deuxième conduit d'écoulement intermédiaire de surrefroidissement débouche dans au moins deux tubes de refroidissement (2) considérés comme troisième partie parallèle de surrefroidissement.
  3. Ensemble de condenseur de fluide frigorigène selon la revendication 1 ou 2, caractérisé en ce qu'une partie parallèle de surrefroidissement (14, 16) ou la zone de surrefroidissement (13) présente chacune entre deux ou huit tubes de refroidissement (2) alimentés parallèlement et / ou la surface des tubes de refroidissement (2) et, de préférence, des tubes collecteurs (5) de la zone de surrefroidissement (13), est inférieure à 50 %, à 40 %, à 35 %, à 30 %, à 25 % ou à 15 % de la surface de l'échangeur de chaleur de l'ensemble de condenseur de fluide frigorigène (1), et l'échangeur de chaleur se compose en particulier des tubes de refroidissement (2) et, de préférence, des tubes collecteurs (5).
  4. Ensemble de condenseur de fluide frigorigène selon l'une quelconque ou plusieurs des revendications précédentes, caractérisé en ce que, dans la direction d'écoulement du fluide frigorigène, en amont de la première partie parallèle de surrefroidissement (14), au moins deux tubes de refroidissement (2) considérés comme première partie parallèle (19), acheminant du fluide, sont alimentés parallèlement, en ce que le fluide frigorigène sortant de la première partie parallèle (19) débouche dans un premier conduit d'écoulement intermédiaire (20), et le premier conduit d'écoulement intermédiaire (20) débouche dans au moins deux tubes de refroidissement (2) considérés comme deuxième partie parallèle (21).
  5. Ensemble de condenseur de fluide frigorigène selon la revendication 4, caractérisé en ce que, dans la direction d'écoulement du fluide frigorigène, en amont de la première partie parallèle de surrefroidissement (14), le fluide frigorigène sortant de la deuxième partie parallèle (21) débouche dans un deuxième conduit d'écoulement intermédiaire (22), et le deuxième conduit d'écoulement intermédiaire (22) débouche dans au moins deux tubes de refroidissement (2) considérés comme troisième partie parallèle (23).
  6. Ensemble de condenseur de fluide frigorigène selon la revendication 4 ou 5, caractérisé en ce que la deuxième partie parallèle (21) débouche dans un deuxième conduit d'écoulement intermédiaire (22), et le deuxième conduit d'écoulement intermédiaire (22) débouche dans le réservoir collecteur, ou bien la troisième partie parallèle (23) débouche dans un troisième conduit d'écoulement intermédiaire (24), et le troisième conduit d'écoulement intermédiaire (24) débouche dans le réservoir collecteur.
  7. Ensemble de condenseur de fluide frigorigène selon l'une quelconque ou plusieurs des revendications précédentes, caractérisé en ce que la somme des surfaces de section d'écoulement de la totalité des tubes de refroidissement (2) d'une partie parallèle de surrefroidissement (14, 16, 18) est inférieure au produit de 0,9 ou de 0,7 ou de 0,5 ou de 0,3 ou de 0,1, et de la somme des surfaces de section d'écoulement de la totalité des tubes de refroidissement (2) d'une partie parallèle (19, 21, 23) et / ou les tubes de refroidissement (2) sont configurés comme des tubes plats (3) et des ailettes ondulées (4) sont disposées entre les tubes plats.
  8. Ensemble de condenseur de fluide frigorigène (1) pour un système de climatisation d'un véhicule automobile selon l'une quelconque des revendications précédentes, ledit ensemble de condenseur comprenant :
    - des ailettes ondulées qui sont disposées entre les tubes de refroidissement,
    caractérisé
    en ce que la géométrie des ailettes ondulées de la zone de surrefroidissement (13) se distingue de la géométrie des ailettes ondulées de la zone de surchauffe (11) et / ou de la zone de condensation (12).
  9. Système de climatisation d'un véhicule automobile comprenant :
    - un ensemble de condenseur de fluide frigorigène (1),
    - un évaporateur,
    - un compresseur,
    - de préférence un ventilateur,
    - de préférence un carter servant au logement du ventilateur et de l'évaporateur,
    caractérisé
    en ce que l'ensemble de condenseur de fluide frigorigène (1) est conçu selon l'une quelconque ou plusieurs des revendications 1 à 8.
EP11745804.2A 2010-08-19 2011-08-19 Module de condenseur à réfrigérant Active EP2606291B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010039518A DE102010039518A1 (de) 2010-08-19 2010-08-19 Kältemittelkondensatorbaugruppe
PCT/EP2011/064322 WO2012022807A1 (fr) 2010-08-19 2011-08-19 Module de condenseur à réfrigérant

Publications (2)

Publication Number Publication Date
EP2606291A1 EP2606291A1 (fr) 2013-06-26
EP2606291B1 true EP2606291B1 (fr) 2019-07-31

Family

ID=44630509

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11745804.2A Active EP2606291B1 (fr) 2010-08-19 2011-08-19 Module de condenseur à réfrigérant

Country Status (3)

Country Link
EP (1) EP2606291B1 (fr)
DE (1) DE102010039518A1 (fr)
WO (1) WO2012022807A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013204294A1 (de) * 2013-03-12 2014-10-02 Behr Gmbh & Co. Kg Kondensatorbaugruppe für Kältemittel
CN103438621B (zh) * 2013-08-28 2015-11-18 广东志高空调有限公司 一种可变流路空调冷凝器

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5482112A (en) * 1986-07-29 1996-01-09 Showa Aluminum Kabushiki Kaisha Condenser
DE3843306A1 (de) * 1988-12-22 1990-06-28 Thermal Waerme Kaelte Klima Flachrohrverfluessiger fuer ein kaeltemittel einer fahrzeugklimaanlage
JPH11211277A (ja) * 1998-01-22 1999-08-06 Showa Alum Corp サブクールシステムコンデンサ
JP2003021432A (ja) * 2001-07-09 2003-01-24 Zexel Valeo Climate Control Corp コンデンサ
KR100872468B1 (ko) * 2002-05-24 2008-12-08 한라공조주식회사 다단 기액분리형 응축기
GB0326443D0 (en) * 2003-11-13 2003-12-17 Calsonic Kansei Uk Ltd Condenser
EP1577629A1 (fr) * 2004-03-18 2005-09-21 Behr Lorraine S.A.R.L. Bouchon de fermeture, distributeur et échangeur de chaleur
DE102007018722A1 (de) 2007-03-23 2008-09-25 Modine Manufacturing Co., Racine Kondensator
JP2008281326A (ja) * 2007-04-11 2008-11-20 Calsonic Kansei Corp 冷凍装置及び該冷凍装置に用いる熱交換器
FR2915793B1 (fr) * 2007-05-03 2015-05-01 Valeo Systemes Thermiques Echangeur de chaleur ameliore pour circuit de climatisation de vehicule automobile

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
WO2012022807A1 (fr) 2012-02-23
DE102010039518A1 (de) 2012-02-23
EP2606291A1 (fr) 2013-06-26

Similar Documents

Publication Publication Date Title
DE112013001863B4 (de) Wärmetauscher und Wärmepumpensystem, das denselben verwendet
DE112015000465B4 (de) Klimaanlagensystem für ein Fahrzeug
DE102007054345A1 (de) Kühlmodul
DE112014001028T5 (de) Stapelwärmetauscher
DE102012215411A1 (de) Verdampfer mit Kältespeicherfunktion
DE112019003711B4 (de) Integrierter Flüssigkeits-/Luftgekühlter Kondensator und Niedertemperatur-Kühler
EP2606292B1 (fr) Module de condenseur à réfrigérant
DE112016000572B4 (de) Ejektor-integrierter Wärmetauscher
DE102012024722A1 (de) Verdampfer und Verfahren zur Luftaufbereitung
DE112014004473T5 (de) Kältespeicher-Wärmetauscher
DE102020202313A1 (de) Wärmeübertrager
EP2612095B1 (fr) Ensemble condenseur de fluide frigorigène
DE102011080673B4 (de) Kältemittelkondensatorbaugruppe
EP2293001A2 (fr) Échangeur de chaleur avec accumulateur de froid integré
WO2011134786A1 (fr) Système d'échangeur de chaleur
EP2606291B1 (fr) Module de condenseur à réfrigérant
DE102020121275B4 (de) Wärmeübertrager eines Kältemittelkreislaufes einer Fahrzeugklimaanlage
DE102020121274A1 (de) Wärmeübertrager eines Kältemittelkreislaufes einer Fahrzeugklimaanlage
EP2795230A2 (fr) Échangeur de chargeur
DE102011007216A1 (de) Kältemittelkondensatorbaugruppe
DE112016002286T5 (de) Wärmetauscher mit Flüssigkeitsbehälter
DE102021213376A1 (de) Wärmeübertrager und Kältemittelkreislauf mit einem Wärmeübertrager
WO2012098261A2 (fr) Module condenseur de fluide frigorigène
EP2818817B1 (fr) Composant de condensateur
DE102005028510A1 (de) Verstellbarer innerer 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: 20130319

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

RIN1 Information on inventor provided before grant (corrected)

Inventor name: KEMLE, ANDREAS

Inventor name: JUNG, MATTHIAS

Inventor name: FOERSTER, UWE

Inventor name: DAVID, GUILLAUME

Inventor name: WALTER, CHRISTOPH

Inventor name: HOFMANN, HERBERT

DAX Request for extension of the european patent (deleted)
RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MAHLE BEHR GMBH & CO. KG

17Q First examination report despatched

Effective date: 20160420

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

Free format text: STATUS: EXAMINATION IS IN PROGRESS

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: 20190220

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: EXAMINATION IS IN PROGRESS

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

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

Inventor name: FOERSTER, UWE

Inventor name: KEMLE, ANDREAS

Inventor name: WALTER, CHRISTOPH

Inventor name: JUNG, MATTHIAS

Inventor name: DAVID, GUILLAUME

Inventor name: HOFMANN, HERBERT

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

INTG Intention to grant announced

Effective date: 20190619

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: CH

Ref legal event code: EP

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1161315

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190815

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: 502011015958

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20190731

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: 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: 20190731

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: 20191202

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: 20190731

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: 20191031

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: 20191031

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: 20190731

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: 20190731

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: 20190731

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

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: 20191130

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: 20190731

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: 20190731

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: 20190731

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: 20190731

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: 20191101

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: 20190731

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

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: 20190731

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: 20190731

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: 20190731

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: 20190731

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: 20190731

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

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: 20190731

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: 20190731

Ref country code: LI

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

Effective date: 20190831

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: 20200224

Ref country code: CH

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

Effective date: 20190831

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: 20190731

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: 20190731

Ref country code: LU

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

Effective date: 20190819

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20190831

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011015958

Country of ref document: DE

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

PG2D Information on lapse in contracting state deleted

Ref country code: IS

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

Ref country code: IE

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

Effective date: 20190819

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: 20191030

26N No opposition filed

Effective date: 20200603

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: 20190831

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: 20190731

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

Effective date: 20191031

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1161315

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190819

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: 20191031

Ref country code: FR

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

Effective date: 20190930

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: 20190819

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: 20190731

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: 20190731

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: 20110819

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: 20190731

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20240521

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

Ref country code: DE

Payment date: 20250820

Year of fee payment: 15