EP2336702B1 - Kühlmittelverdampfer und klimaanlagenvorrichtung damit - Google Patents

Kühlmittelverdampfer und klimaanlagenvorrichtung damit Download PDF

Info

Publication number
EP2336702B1
EP2336702B1 EP09820598.2A EP09820598A EP2336702B1 EP 2336702 B1 EP2336702 B1 EP 2336702B1 EP 09820598 A EP09820598 A EP 09820598A EP 2336702 B1 EP2336702 B1 EP 2336702B1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
tank
tank portion
holes
evaporator
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.)
Not-in-force
Application number
EP09820598.2A
Other languages
English (en)
French (fr)
Other versions
EP2336702A4 (de
EP2336702A1 (de
Inventor
Yasunobu Joboji
Jun Ito
Takamitsu Himeno
Hitoshi Tamaki
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.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
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 Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP2336702A1 publication Critical patent/EP2336702A1/de
Publication of EP2336702A4 publication Critical patent/EP2336702A4/de
Application granted granted Critical
Publication of EP2336702B1 publication Critical patent/EP2336702B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/022—Evaporators with plate-like or laminated elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0207—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions the longitudinal or transversal partitions being separate elements attached to header boxes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels
    • 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
    • F28D2021/0071—Evaporators

Definitions

  • the present invention relates to a refrigerant evaporator provided in a refrigeration cycle, and in particular, to an aluminum-alloy refrigerant evaporator suitable for applying to a vehicle air conditioner and an air conditioner employing the same.
  • refrigerant evaporator employed in a refrigeration cycle of a vehicle air conditioner
  • a refrigerant evaporator which is configured including numerous refrigerant tubes that have refrigerant channels for flowing refrigerant in a vertical direction, that are numerously arranged in parallel in a direction orthogonal to a flow direction of the air flowing outside of the refrigerant channel, and that are also arranged in a plurality of rows, front-to-back, parallel to the flow direction of the air; and a pair of top and bottom tanks that are arranged in a direction orthogonal to the flow direction of the air, that are connected to the numerous refrigerant tubes at both top and bottom ends thereof, and whose interior is partitioned by a partition wall into a first tank portion and a second tank portion in a row direction, corresponding to the plurality of rows of the refrigerant tubes, thereby performing distribution and collection of the refrigerant, wherein the refrigerant that has
  • JP 3637314 B discloses a refrigerant evaporator having the above-described configuration, in which one of the plurality of blocks is a U-turn block portion wherein the refrigerant flows into the first tank portion of the top tank from a direction parallel to the partition wall, flows to the second tank portion from this first tank portion via a side refrigerant channel, and further flows while being distributed to the plurality of refrigerant tubes from the first tank portion and the second tank portion, respectively.
  • a plurality of communication holes are bored in the partition wall to allow the refrigerant collected in the second tank portion of the top tank upon flowing through the plurality of refrigerant tubes to directly flow into the first tank portion separated by the partition wall.
  • JP H06 26780 A discloses a refrigerant evaporator made of aluminum alloy comprising a plurality of refrigerant tubes that have refrigerant channels for flowing refrigerant in a vertical direction, that are arranged in parallel and in a plurality of rows, front-to-back, and a pair of top and bottom tanks that are arranged in the direction orthogonal to the refrigerant tubes and are connected to top and bottom ends of the refrigerant tubes.
  • the top tank is provided with an inlet and with an outlet for the refrigerant.
  • the interior of the top and bottom tanks is partitioned into a plurality of sections by a longitudinal partition wall and by a plurality of transverse partition walls.
  • the wall portions of the partition walls delimiting the sections are either closed or provided with a central elongated hole so as to define a flow pattern for the refrigerant from the inlet through the sections in the top and bottom tanks and through the plurality of refrigerant channels before it flows out from the outlet.
  • liquid refrigerant in the U-turn block portion of the top tank located at the top, liquid refrigerant is prone to flow into the refrigerant tubes on the front side with respect to an inflow direction of the refrigerant due to inertia, and thus, in some cases, the liquid refrigerant that has flowed into the second tank portion from the first tank portion cannot adequately reach the back-most end thereof.
  • the present invention has been conceived in light of the above-described circumstances, and an object thereof is to provide a refrigerant evaporator that is capable of enhancing heat-exchange performance by achieving an even distribution of liquid refrigerant to a plurality of refrigerant tubes connected to a first tank portion and a second tank portion of a U-turn block portion and also capable of ensuring adequate pressure-withstanding strength of the tank portions, as well as an air conditioner employing the same.
  • a refrigerant evaporator of the present invention has the features of claim 1 and an air conditioner employing the same has the features of claim 6.
  • a refrigerant evaporator is a refrigerant evaporator made of aluminum alloy including numerous refrigerant tubes that have refrigerant channels for flowing refrigerant in a vertical direction, that are numerously arranged in parallel in a direction orthogonal to a flow direction of an external fluid that flows outside of the refrigerant channels, and that are arranged in a plurality of rows, front-to-back, parallel to the flow direction of the external fluid; and a pair of top and bottom tanks that are arranged in the direction orthogonal to the flow direction of the external fluid and connected at top and bottom ends of the numerous refrigerant tubes, the interior of which is partitioned in a row direction corresponding to the plurality of rows of the refrigerant tubes into a first tank portion and a second tank portion by a partition wall, and that distribute or collect the refrigerant, the tanks being provided with a refrigerant inlet and a refrigerant outlet, and the refriger
  • liquid refrigerant in gas-liquid two-phase refrigerant that has flowed into the first tank portion or the second tank portion from a direction parallel to the partition wall can be flowed into both of the first tank portion and the second tank portion of the U-turn block portion substantially evenly over the entire region thereof in the refrigerant inflow direction, while being sequentially distributed into the other tank portion by the plurality of refrigerant-distribution holes provided in the direction parallel to the length direction of the partition walls, it becomes possible to substantially evenly distribute the liquid refrigerant to the plurality of refrigerant tubes connected to the first tank portion and the second tank portion.
  • the liquid refrigerant which mainly contributes to the cooling of the external fluid, is more evenly distributed, thereby making it possible to enhance the heat-exchange performance of the refrigerant evaporator.
  • the inter-hole distance between the plurality of refrigerant-distribution holes can be set to a size that makes it possible to satisfy at least 3.3 MPa or greater break-down pressure. Therefore, it is possible to readily further increase the pressure-withstanding strength of the tank portions against the internal pressure by optimizing various sizes of the refrigerant-distribution holes.
  • the inter-hole distance between the plurality of refrigerant-distribution holes can be set to a size that makes it possible to satisfy at least 4.5 MPa or greater break-down pressure, even if the variability thereof is taken into consideration. Therefore, it is possible to readily and assuredly ensure the pressure-withstanding strength of the tank portions against the internal pressure by optimizing various sizes of the group of refrigerant-distribution holes.
  • the refrigerant-distribution holes are elongated holes made longer in a direction orthogonal to the hole-row direction of the refrigerant-distribution holes.
  • the refrigerant-distribution holes are elongated holes made longer in the direction orthogonal to the hole-row direction of the refrigerant-distribution holes, it is possible to set the opening area of the refrigerant-distribution holes to a size allowing passage of the refrigerant without increasing the pressure loss thereof, while ensuring the pressure-withstanding strength of the tank portions by making a/b of the plurality of refrigerant-distribution holes small. Therefore, the pressure-withstanding strength of the tank portions can be increased while eliminating the influence on the heat-exchange performance by suppressing an increase in pressure loss of the refrigerant due to the refrigerant-distribution holes.
  • a refrigerant evaporator is a refrigerant evaporator made of aluminum alloy including numerous refrigerant tubes that have refrigerant channels for flowing refrigerant in a vertical direction, that are numerously arranged in parallel in a direction orthogonal to a flow direction of an external fluid that flows outside of the refrigerant channels, and that are arranged in a plurality of rows, front-to-back, parallel to the flow direction of the external fluid; and a pair of top and bottom tanks that are arranged in the direction orthogonal to the flow direction of the external fluid and connected at top and bottom ends of the numerous refrigerant tubes, the interior of which is partitioned in a row direction corresponding to the plurality of rows of the refrigerant tubes into a first tank portion and a second tank portion by a partition wall, and that distribute or collect the refrigerant, the tanks being provided with a refrigerant inlet and a refrigerant outlet,
  • liquid refrigerant in gas-liquid two-phase refrigerant that has flowed into the first tank portion or the second tank portion from a direction parallel to the partition wall can be flowed into both of the first tank portion and the second tank portion of the U-turn block portion substantially evenly over the entire region thereof in the refrigerant inflow direction, while being sequentially distributed into the other tank portion by the plurality of refrigerant-distribution holes provided in the direction parallel to the length direction of the partition walls, it becomes possible to substantially evenly distribute the liquid refrigerant to the plurality of refrigerant tubes connected to the first tank portion and the second tank portion.
  • the liquid refrigerant which mainly contributes to the cooling of the external fluid, is more evenly distributed, thereby making it possible to enhance the heat-exchange performance of the refrigerant evaporator. Furthermore, because the refrigerant-distribution holes are elongated holes made longer in the direction orthogonal to the hole-row direction of the refrigerant-distribution holes, it is possible to set the inter-hole distance of the plurality of refrigerant distribution holes to a size that satisfies adequate pressure-withstanding pressure or break-down pressure, while setting the opening area of the plurality of refrigerant-distribution holes to a size allowing passage of the refrigerant without increasing the pressure loss thereof.
  • the elongated holes be elliptical holes or elongated circular holes.
  • the elongated holes are elliptical holes or elongated circular holes, it is possible to set the inter-hole distance of the refrigerant distribution holes to a size that satisfies adequate pressure-withstanding pressure or break-down pressure, while setting the opening area of the plurality of refrigerant-distribution holes to a size allowing passage of the refrigerant without increasing the pressure loss thereof. Therefore, it is possible to readily increase the pressure-withstanding strength of the tank portions against the internal pressure by optimizing the hole shape of the refrigerant-distribution holes, while eliminating the influence on the heat-exchange performance by suppressing an increase in pressure loss of the refrigerant due to the refrigerant-distribution holes.
  • any one of the above-described refrigerant evaporators is employed as a refrigerant evaporator provided in a refrigeration cycle.
  • the refrigerant evaporator provided in the refrigeration cycle is one of the above-described refrigerant evaporators
  • the performance of the air conditioner can be enhanced by performance enhancement of the refrigerant evaporator, and, simultaneously, the reliability of the air conditioner can be enhanced by increasing the pressure-withstanding strength of the refrigerant evaporator.
  • liquid refrigerant in gas-liquid two-phase refrigerant that has flowed in from a direction parallel to the partition wall can be flowed into both of the first tank portion and the second tank portion of the U-turn block portion formed in the top tank, nearly evenly distributed over the entire region thereof in the refrigerant inflow direction, the liquid refrigerant is more evenly distributed to the plurality of refrigerant tubes connected to the first tank portion and the second tank portion, thereby making it possible to enhance the heat-exchange performance of the evaporator.
  • the refrigerant evaporators of the present invention by configuring the refrigerant-distribution holes provided in the partition walls as elongated holes made longer in the direction orthogonal to the hole-row direction of the refrigerant-distribution holes, it is possible to set the inter-hole distance of the plurality of refrigerant distribution holes to a size that satisfies adequate pressure-withstanding pressure or break-down pressure, while setting the opening area of the plurality of refrigerant-distribution holes to a size allowing passage of the refrigerant without increasing the pressure loss thereof; therefore, it is possible to readily increase the pressure-withstanding strength of the tank portions against the internal pressure by optimizing the hole shape of the refrigerant-distribution holes while suppressing the increase in pressure loss of the refrigerant in the partition walls, which have restricted configurations.
  • the performance of the air conditioner can be enhanced by enhancing the performance of the refrigerant evaporator, and, simultaneously, the reliability of the air conditioner can be enhanced by increasing the pressure-withstanding strength of the refrigerant evaporator.
  • Fig. 1 shows a perspective view of a refrigerant evaporator 1 according to the first example
  • Fig. 2 shows an exploded perspective view thereof
  • Figs. 3A and 3B show a front view and a right side view thereof
  • Fig. 4 shows a side view of a partition wall to be provided inside tanks.
  • the refrigerant evaporator 1 is provided with numerous refrigerant tubes 2 having a plurality of refrigerant channels 2A parallel to the length direction.
  • These refrigerant tubes 2 can be formed of aluminum-alloy flat tubes that are manufactured, for example, by extrusion molding or pultrusion molding, or that are manufactured by molding a plate material into an elliptical tube-shape into which inner fins are inserted to be installed therein.
  • the refrigerant tubes 2 are numerously arranged in parallel in a stack in a direction orthogonal to the flow direction of an external fluid (air) A flowing outside thereof.
  • the refrigerant tubes 2 are arranged in a plurality of rows (two rows) front-to-back relative to the flow direction of the air A.
  • heat-conducting fins 3, which are formed by applying corrugation molding to aluminum-alloy thin plates to impart a wave shape thereto, are interposed between the numerous refrigerant tubes 2 that are numerously arranged in parallel in a stack in the direction orthogonal to the flow direction of the air A, and are bonded to external surfaces of the refrigerant tubes 2 by brazing using a known method.
  • top tank 4 and a bottom tank 5 are bonded thereto by brazing.
  • These top tank 4 and bottom tank 5 are formed of top members 4A and 5A and bottom members 4B and 5B that are split into two vertically; partition walls 4C and 5C which partition the inside of the top tank 4 and the bottom tank 5 into a first tank portion 5 and a second tank portion 7 and a first tank portion 8 and a second tank portion 9, respectively, in the row direction corresponding to the plurality of rows of the refrigerant tubes 2; and cap members 4D and 4E and 5D and 5E which close off the two ends of the top tank 4 and the bottom tank 5, respectively.
  • the top members 4A and 5A, the bottom members 4B and 5B, the partition walls 4C and 5C, and the cap members 4D, 5D, 4E, and 5D are formed of press molded pieces of aluminum alloy and are integrally bonded by brazing using a known method.
  • numerous tube insertion holes 4F and 5F are provided corresponding to the rows of the refrigerant tubes 2 in order for the ends of the numerous refrigerant tubes 2 to be inserted thereinto for bonding by brazing.
  • the cap member 5E of the bottom tank 5 is provided with a refrigerant inlet 5G, which communicates with the first tank portion 8, and a refrigerant-inlet header 10 is bonded thereto by brazing so as to communicate with the refrigerant inlet 5G of the cap member 5E.
  • the cap member 4E of the top tank 4 is provided with a refrigerant outlet 4G, which communicates with the second tank portion 7, and a refrigerant-outlet header 11 is bonded thereto by brazing so as to communicate with the refrigerant outlet 4G of the cap member 4E.
  • the refrigerant-inlet header 10 and the refrigerant-outlet header 11 are connected to a refrigerant-inlet pipe 12 and a refrigerant-outlet pipe 13, respectively.
  • Partition plates 4H and 5H that respectively partition the second tank portion 7 of the top tank 4 and the first tank portion 8 of the bottom tank 5 into two regions on the right and left in a direction parallel to the direction orthogonal to the flow direction of the air A (length direction of the tanks) are provided in the top tank 4 and the bottom tank 5.
  • the partition plates 4H and 5H are provided at positions where the ratio of the number of the refrigerant tubes 2 in the left region and the right region of the two regions separated into left and right in the figure is about 1:2.
  • two throttle plates 5I and 5J having throttle holes 5K and 5L that gradually narrow toward the end with the cap member 5E are provided at two appropriate locations in the length direction of the tank in the right region in the figure, separated by a predetermined gap therebetween.
  • the partition walls 4C and 5C of the top tank 4 and the bottom tank 5 have a plurality of refrigerant-distribution holes 4M and 5M, which communicate between the first tank portion 6 and the second tank portion 7 of the top tank 4 and between the first tank portion 8 and the second tank portion 9 of the bottom tank 5, respectively, provided in the length direction of the partition walls 4C and 5C.
  • the refrigerant-distribution holes 4M and 5M have a function of causing the liquid refrigerant in a gas-liquid two-phase refrigerant flowing into the first tank portion 6 of the top tank 4 parallel to the length direction of the partition wall 4C from the right region to the left region in the figure to flow in while distributing the refrigerant nearly evenly in the length direction of the left region of the second tank portion 7 in the figure.
  • a refrigerant flow pathway in the refrigerant evaporator 1 is divided into three blocks, that is, a first block 14, a second block (U-turn block) 15, and a third block 16, to be described below.
  • the first block 14 is a block that causes the refrigerant that flows into the first tank portion 8 of the bottom tank 5 from the refrigerant-inlet header 10 to flow to the first tank portion 6 of the top tank 4 via the plurality of refrigerant tubes 2 connected in the right region with respect to the partition plate 5H.
  • the second block (U-turn block) 15 which is also referred to as a U-turn block, is a block that causes the refrigerant that flows into the first tank portion 6 of the top tank 4 to flow along the partition wall 4C toward the left region in the figure, from where it is distributed nearly evenly to the left region with respect to the partition plate 4H of the second tank portion 7 parallel to the length direction thereof via the plurality of refrigerant-distribution holes 4M, and then causes the refrigerant to flow down through the plurality of refrigerant tubes 2 from both the first tank portion 6 and the second tank portion 7 to the first tank portion 8 and the second tank portion 9 of the bottom tank 5.
  • the refrigerant that has flowed down to the first tank portion 8 and the second tank portion 9 of the bottom tank 5 is collected in the second tank portion 9 via the refrigerant-distribution holes 5M.
  • the third block 16 is a block that causes the refrigerant collected in the second tank portion 9 to flow toward the right region along the partition wall 5C, and then causes it to flow to the second tank portion 7 of the top tank 4 via the plurality of refrigerant tubes 2.
  • the refrigerant that has flowed to the second tank portion 7 of the top tank 4 in this third block 16 flows out to the refrigerant-outlet pipe 13 via the outlet header 11.
  • the plurality of refrigerant-distribution holes 4M and 5M provided in the above-described partition walls 4C and 5C are constituted of elongated holes 4m and 5m, which are elliptical holes or elongated circular holes, etc. made longer in a direction orthogonal to the hole-row direction, so that it is possible to ensure an adequate opening area to prevent an increase in pressure loss of the flowing refrigerant, and so that it is also possible to ensure adequate pressure-withstanding strength by alleviating stress concentration due to internal pressure.
  • the elongated holes 4m and 5m are configured as follows in order to enhance the pressure-withstanding strength of the top tank 4 and the bottom tank 5.
  • Fig. 7 shows analysis results based on experiments and FEM regarding the relationship between the break-down pressure P [MPa] of the tank partition portions (vertical axis) and the ratio a/b (horizontal axis) when the thickness t of the partition walls 4C and 5C are set at 1 mm, 1.3 mm, and 2 mm
  • Fig. 8 shows a graph in which the thickness t of the partition walls 4C and 5C is set as the horizontal axis and a/b as the vertical axis, and the graph shown in Fig.
  • the partition walls 4Ca and 5C are clad materials, whose core material is A3003-H14 and whose surface material is A4343, and the plate thickness t is normally set between 1 and 2 mm because too low a thickness causes deficient strength and too high a thickness increases the tank size in the thickness direction or decreases the channel area in the tank.
  • the gas-liquid two-phase refrigerant that has flowed into the first tank 8 of the bottom tank 5 from the refrigerant-inlet pipe 12 via the refrigerant-inlet header 10 undergoes heat exchange with the air A via the heat-conducting fins 3 while flowing in the plurality of refrigerant tubes 2 in the first block 14 toward the first tank portion 6 of the top tank 4, and thus part of the refrigerant evaporates.
  • the refrigerant collected in the first tank portion 6 of the top tank 4 flows through the first tank portion 6 to the left region thereof to enter the second block (U-turn block) 15.
  • the gas-liquid two-phase refrigerant that has flowed into the second block (U-turn block) 15 is evenly distributed to the second tank portion 7 by the refrigerant-distribution holes 4M constituted of the elongated holes 4m provided in the partition wall 4C.
  • the refrigerant evenly distributed to the first tank portion 6 and the second tank portion 7 of the top tank 4 in the second block (U-turn block) 15 further evaporates upon undergoing heat exchange with the air A via the heat-conducting fins 3 while flowing down the plurality of refrigerant tubes 2 in the second block (U-turn block) 15 toward the first tank portion 8 and the second tank portion 9 of the bottom tank 5.
  • the refrigerant that has flowed down to the first tank portion 8 and the second tank portion 9 of the bottom tank 5 is collected in the second tank portion 9 by the refrigerant-distribution holes 5M (the elongated holes 5m) provided in the partition wall 5C and flows through the second tank portion 9 to the right region thereof to enter the third block 16.
  • This refrigerant rises through the plurality of refrigerant tubes 2 in the third block 16 toward the second tank portion 7 of the top tank 4, during which heat exchange with the air A occurs, thereby being entirely gasified and collected in the second tank portion 7.
  • the air A cooled by the heat exchange with the refrigerant is supplied to the vehicle interior to be used for air conditioning, whereas the gasified refrigerant is sucked into a compressor from the outlet header 11 via the refrigerant-outlet pipe 13, thereby being circulated in the refrigeration cycle.
  • the gas-liquid two-phase refrigerant that has flowed into the first tank portion 6 of the top tank 4 along the partition wall 4C is sequentially distributed to the second tank portion 7 from the front side by the plurality of refrigerant-distribution holes 4M constituted of the elongated holes 4m made longer in the longitudinal direction and provided in the length direction of the partition wall 4C; therefore, it is possible to make the liquid refrigerant flow into the second tank portion 7 nearly evenly over the entire region in the length direction thereof. Accordingly, it is possible to nearly evenly distribute the liquid refrigerant to the plurality of refrigerant tubes 2 connected to the first tank portion 6 and the second tank portion 7 in the second block.
  • the distribution of the liquid refrigerant is enhanced, in particular, between the first tank portion 6 and the second tank portion 7 of the U-turn block 15, thereby making it possible for the liquid refrigerant that contributes to cooling of the air A, which is the external fluid, to be more evenly distributed to the plurality of refrigerant tubes 2; therefore, it is possible to enhance the heat-exchange performance of the refrigerant evaporator by making the heat-conducting area function effectively.
  • the refrigerant-distribution holes 4M and 5M are constituted of the elongated holes 4m and 5m, which are elliptical holes or elongated circular holes, etc. made longer in a direction orthogonal to the hole-row direction, so that it is possible to ensure an adequate opening area to prevent an increase in pressure loss of the flowing refrigerant and to ensure adequate pressure-withstanding strength by alleviating stress concentration due to the internal pressure.
  • the opening area of the refrigerant-distribution holes 4M and 5M elongated holes 4m and 5m
  • the opening area of the refrigerant-distribution holes 4M and 5M elongated holes 4m and 5m
  • the inter-hole distance of the plurality of refrigerant-distribution holes 4M and 5M elongated holes 4m and 5m
  • Fig. 7 shows analysis results regarding the relationship between the break-down pressure P [MPa] of the tank partition portions (vertical-axis) and the above-described a/b (horizontal axis) when the thickness t of the partition walls 4C and 5C is set at 1 mm, 1.3 mm, and 2 mm
  • Fig. 8 shows a graph in which the thickness t of the partition walls 4C and 5C is set as the horizontal axis and a/b as the vertical axis, and the graph shown in Fig. 7 is converted to a polynomial expression that expresses ranges of a/b within which it is possible to ensure the required break-down pressure P of the tank partition portions, taking the thickness t of the partition walls into consideration.
  • the partition walls 4C and 5C which have restrictive conditions, such as the inability to increase the plate thickness because the tank size would be increased, the inability to decrease the number of holes to ensure the function thereof for evenly distributing refrigerant, the need for the opening area to be made large to suppress pressure loss of the refrigerant passing therethrough, etc., it is possible to readily ensure the pressure-withstanding strength of the tank portions against the internal pressure by optimizing various sizes of the refrigerant-distribution holes 4M and 5M (the elongated holes 4m and 5m).
  • ribs 4N and 5N may be integrally molded on surfaces of the top members 4A and 5A of the tanks 4 and 5.
  • individual component parts of the refrigerant evaporator 1 shown in Fig. 2 are not separately joined by brazing, but, as is known, after all component parts are pre-assembled, they can be placed in an oven to be heated and be manufactured into an integrated piece by brazing in the oven.
  • the above-described aluminum-alloy refrigerant evaporator 1 is particularly suitable for a refrigerant evaporator that forms a refrigeration cycle of a vehicle air conditioner where it is necessary to achieve low weight and compactness, and, by applying the refrigerant evaporator 1 thereto, the performance of the air conditioner can be enhanced, and, simultaneously, the reliability of the air conditioner can be enhanced by increasing the pressure-withstanding strength of the refrigerant evaporator 1.
  • This embodiment differs from the first example described above in the manner of providing the refrigerant-distribution holes 4M and 5M (elongated holes 4m and 5m) to be provided in the partition walls 4C and 5C. Because other components are the same as those of the first example, descriptions thereof will be omitted.
  • the plurality of refrigerant-distribution holes 4M and 5M elongated holes 4m and 5m
  • the partition walls 4C and 5C in the second block (U-turn block) 15 are configured to be provided in a plurality in a back-side region within the length L1, excluding a portion of the region on the front side in the refrigerant inflow direction.
  • the above-described back-side-region length L1 is the length from the back-most ends of the first tank portion 6 and the second tank portion 7 to the position of the refrigerant-distribution holes 4M on the front-most side; it is effective to set this length L1 of the back-side region within a range of 0.7 ⁇ L1/L2 ⁇ 0.9, relative to the entire length L2, and it is most preferable that L1/L2 be about 0.8.
  • L1/L2 when L1/L2 becomes less than 0.7, the distribution of liquid refrigerant in a region close to the partition plate 4H in the second tank portion 7 becomes slightly deficient, whereas when L1/L2 exceeds 0.9, conversely, the distribution of liquid refrigerant in a region on the back-most side thereof becomes slightly deficient; and, from this, it is most preferable that L1/L2 be about 0.8.
  • the present invention is not limited to the invention according to the above-described embodiment, and appropriate modifications are permissible.
  • all of the plurality of refrigerant-distribution holes 4M and 5M (elongated holes 4m and 5m) provided in the length direction of the partition walls 4C and 5C are made in equal sizes in the example and embodiment described above, the sizes of the refrigerant-distribution holes 4M and 5M (elongated holes 4m and 5m) may be gradually increased from the front side toward the back side in the refrigerant inflow direction.
  • the liquid refrigerant more of which is readily distributed to the refrigerant-distribution holes 4M (elongated holes 4m) on the front side due to inertia, is sequentially shifted to the larger refrigerant-distribution holes 4M (elongated holes 4m) on the back side, by which the distribution in the refrigerant inflow direction is improved for the liquid refrigerant flowing from the first tank portion 6 to the second tank portion 7, thereby making it possible to distribute the liquid refrigerant nearly evenly over the entire region in the refrigerant inflow direction in the first tank portion 6 and the second tank portion 7; therefore, it is possible to further enhance the heat-exchange performance of the refrigerant evaporator 1 by achieving an even distribution of the liquid refrigerant to the plurality of refrigerant tubes 2.
  • the U-turn block 15 in which the refrigerant flows from the first tank portion 6 to the second tank portion 7 has been described as an example; however, a configuration such as one in which the refrigerant flows in reverse from the second tank portion to the first tank portion 6 is of course also possible.
  • the number of blocks is not limited to three blocks.
  • the inlet and outlet of the refrigerant for the refrigerant evaporator 1 may be provided anywhere at the top, bottom, left, and right.

Claims (6)

  1. Ein Kühlmittelverdampfer (1), der aus einer Aluminiumlegierung hergestellt ist, mit:
    einer Vielzahl von Kühlmittelrohren (2), die Kühlmittelkanäle (2A) für ein Strömen eines Kühlmittels in einer Vertikalrichtung haben, die so parallel angeordnet sind, dass die Kühlmittelrohre (2) in einer Richtung angeordnet sein können, die orthogonal zu einer Strömungsrichtung eines externen Fluids (A) ist, das außerhalb der Kühlmittelkanäle (2A) strömt, und die in einer Vielzahl von Reihen von vorne nach hinten parallel zur Strömungsrichtung des externen Fluids (A) angeordnet sind, und
    einem Paar von oberen und unteren Tanks (4,5), die in der Richtung orthogonal zu der Strömungsrichtung des externen Fluids (A) angeordnet sind und mit oberen und unteren Enden der Vielzahl von Kühlmittelrohren (2) verbunden sind, deren Innenraum in einer Reihenrichtung korrespondierend zu der Vielzahl von Reihen der Kühlmittelrohre (2) innerhalb eines ersten Tankabschnitts (6;8) und eines zweiten Tankabschnitts (7;9) durch eine Trennwand (4C;5C) unterteilt sind, und die ausgestaltet sind, um das Kühlmittel zu verteilen oder zu sammeln,
    wobei die Tanks (4,5) mit einem Kühlmitteleinlass (5G) und einem Kühlmittelauslass (4G) vorgesehen sind, und die Anordnung so ist, dass das Kühlmittel, das von dem Kühlmitteleinlass (5G) einströmte, durch die Kühlmittelrohre (2) von einer Vielzahl von Blöcken (14,15,16) fortlaufend strömt, die durch Trennplatten (4H;5H) unterteilt sind, die an einer Vielzahl von Stellen in den Tanks (4;5) vorgesehen sind, wonach das Kühlmittel von dem Kühlmittelauslass (4G) ausströmt,
    wobei einer von der Vielzahl von Blöcken (14,15,16) ein Wendeblockabschnitt (15) ist, in dem das Kühlmittel in den ersten Tankabschnitt (6) oder den zweiten Tankabschnitt (7) des oberen Tanks (4) von einer zu der Trennwand (4C) parallelen Richtung einströmt und von dort in den anderen Tankabschnitt (7,6) hinein strömt, wodurch dieses jeweils auf die Vielzahl von Kühlmittelrohre (2) von dem ersten Tankabschnitt (6) und dem zweiten Tankabschnitt (7) aufgeteilt wird,
    wobei an den Trennwänden (4C;5C), die die ersten Tankabschnitte (6;8) und die zweiten Tankabschnitte (7;9) der oberen und der unteren Tanks (4,5) in dem Wendeblockabschnitt (15) unterteilen, eine Vielzahl von Kühlmittelverteilungslöcher (4M;5M), welche mit den ersten Tankabschnitten (6;8) und den zweiten Tankabschnitten (7;9) in Verbindung stehen, in der Längenrichtung der Trennwände (4c;5C) vorgesehen sind,
    dadurch gekennzeichnet, dass
    die Vielzahl von Kühlmittelverteilungslöchern (4M;5M) an einem rückseitigen Bereich des Wendeblockabschnitts (15) vorgesehen sind, der einen Abschnitt des Bereichs an der Vorderseite in der Kühlmitteleinströmrichtung ausschließt, wobei eine Länge L1 des rückseitigen Bereichs in der Kühlmitteleinströmrichtung die Länge von den am weitesten rückseitigen Enden des ersten Tankabschnitts (6) und des zweiten Tankabschnitts (7) zu der Position des Kühlmittelverteilungslochs (4M) an einer am weitesten vorderen Seite ist und die Länge L1 innerhalb eines Bereichs von 0,7 < L1/L2 < 0,9 relativ zu der gesamten Länge L2 des Wendeblockabschnitts (15) in der Kühlmitteleinströmrichtung ist, und in dem die Kühlmittelverteilungslöcher (4M;5M) längliche Löcher (4m;5m) sind, die in einer zu der Lochreihenrichtung der Kühlmittelverteilungslöcher (4M;5M) orthogonalen Richtung länger ausgebildet sind.
  2. Ein Kühlmittelverdampfer (1) gemäß Anspruch 1, wobei, wenn für die Kühlmittelverteilungslöcher (4M;5M) die Distanz zwischen der Vielzahl von Löchern als b, die Lochlänge in der Lochreihenrichtung als a und die Dicke der Trennwand (4C;5C) als t angenommen wird, a/b auf a/b <= -0,0697 * t<2> * 0,3274 * t + 0,4594 festgelegt ist, wobei t = 1 bis 2 mm.
  3. Ein Kühlmittelverdampfer (1) gemäß Anspruch 2, wobei a/b des Kühlmittelverteilungslochs (4M;5M) auf a/b <= -0,0744 * t<2> + 0,3577 * t + 0,3786 festgelegt ist, wobei t = 1 bis 2 mm.
  4. Ein Kühlmittelverdampfer (1) gemäß Anspruch 2, wobei a/b für das Kühlmittelverteilungsloch (4M;5M) auf a/b <= -0,0763 * t<2> + 0,3810 * t + 0,2847 festgelegt ist, wobei t = 1 bis 2 mm.
  5. Ein Kühlmittelverdampfer (1) gemäß einem der Ansprüche 1 bis 4, wobei die länglichen Löcher (4m;5m) elliptische Löcher oder länglich kreisförmige Löcher sind.
  6. Eine Klimaanlage mit einem Kühlmittelverdampfer (1) gemäß einem der Ansprüche 1 bis 5, der als ein Kühlmittelverdampfer eingesetzt wird, der in einem Kühlmittelkreislauf vorgesehen ist.
EP09820598.2A 2008-10-16 2009-10-14 Kühlmittelverdampfer und klimaanlagenvorrichtung damit Not-in-force EP2336702B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2008267478A JP5408951B2 (ja) 2008-10-16 2008-10-16 冷媒蒸発器およびそれを用いた空調装置
PCT/JP2009/067780 WO2010044420A1 (ja) 2008-10-16 2009-10-14 冷媒蒸発器およびそれを用いた空調装置

Publications (3)

Publication Number Publication Date
EP2336702A1 EP2336702A1 (de) 2011-06-22
EP2336702A4 EP2336702A4 (de) 2014-04-09
EP2336702B1 true EP2336702B1 (de) 2019-07-03

Family

ID=42106583

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09820598.2A Not-in-force EP2336702B1 (de) 2008-10-16 2009-10-14 Kühlmittelverdampfer und klimaanlagenvorrichtung damit

Country Status (4)

Country Link
US (1) US20110113823A1 (de)
EP (1) EP2336702B1 (de)
JP (1) JP5408951B2 (de)
WO (1) WO2010044420A1 (de)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014149131A (ja) * 2013-02-01 2014-08-21 Mitsubishi Electric Corp 室外機及び冷凍サイクル装置
KR102170312B1 (ko) * 2014-02-07 2020-10-26 엘지전자 주식회사 열교환기
JP6358848B2 (ja) * 2014-05-15 2018-07-18 株式会社ケーヒン・サーマル・テクノロジー エバポレータ
CN105066518B (zh) * 2015-08-04 2018-01-05 广东美的制冷设备有限公司 一种双排平行流蒸发器及其具有该蒸发器的空调装置
US10378429B2 (en) * 2015-10-28 2019-08-13 Hyundai Motor Company Hybrid intercooler system and control method thereof
CA3031201A1 (en) * 2016-07-22 2018-01-25 Evapco, Inc. Ultra narrow channel ultra low refrigerant charge evaporative condenser
JP6862777B2 (ja) * 2016-11-11 2021-04-21 富士通株式会社 マニホールド及び情報処理装置
JP6842915B6 (ja) * 2016-12-28 2021-04-14 マーレベーアサーマルシステムズジャパン株式会社 エバポレータ
US20210140691A1 (en) * 2019-11-13 2021-05-13 Samsung Electronics Co., Ltd. Heat exchanger and air conditioner having the same

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007129851A1 (en) * 2006-05-09 2007-11-15 Korea Delphi Automotive Systems Corporation Heat exchanger for automobile and fabricating method thereof

Family Cites Families (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0626780A (ja) * 1992-07-13 1994-02-04 Nippondenso Co Ltd 熱交換器
JP3719453B2 (ja) * 1995-12-20 2005-11-24 株式会社デンソー 冷媒蒸発器
US5680897A (en) * 1996-09-12 1997-10-28 General Motors Corporation Plate type heat exchanger with integral feed pipe fixturing
JP3629900B2 (ja) * 1997-07-04 2005-03-16 株式会社デンソー 熱交換器
JPH11287587A (ja) * 1998-04-03 1999-10-19 Denso Corp 冷媒蒸発器
US6449979B1 (en) * 1999-07-02 2002-09-17 Denso Corporation Refrigerant evaporator with refrigerant distribution
JP3391339B2 (ja) * 1999-07-02 2003-03-31 株式会社デンソー 冷媒蒸発器
JP4254015B2 (ja) * 2000-05-15 2009-04-15 株式会社デンソー 熱交換器
DE10056074B4 (de) * 2000-11-07 2017-03-23 Mahle International Gmbh Wärmeübertrager
TW552382B (en) * 2001-06-18 2003-09-11 Showa Dendo Kk Evaporator, manufacturing method of the same, header for evaporator and refrigeration system
CN100348941C (zh) * 2001-10-17 2007-11-14 昭和电工株式会社 蒸发器和设置有具有该蒸发器的制冷循环的车辆
US7318470B2 (en) * 2001-12-21 2008-01-15 Behr Gmbh & Co. Kg Device for exchanging heat
JP3637314B2 (ja) 2002-01-10 2005-04-13 三菱重工業株式会社 積層型蒸発器
KR100638490B1 (ko) * 2002-05-29 2006-10-25 한라공조주식회사 열교환기
JP2004144395A (ja) * 2002-10-24 2004-05-20 Denso Corp 冷媒蒸発器
EP1579166A4 (de) * 2002-12-31 2008-06-25 Modine Korea Llc Verdampfer
AU2004284339A1 (en) * 2003-10-29 2005-05-06 Showa Denko K.K. Heat exchanger
WO2005108899A1 (en) * 2004-05-11 2005-11-17 Showa Denko K.K. Heat exchangers
JP4281634B2 (ja) * 2004-06-28 2009-06-17 株式会社デンソー 冷媒蒸発器
US8037929B2 (en) * 2004-12-16 2011-10-18 Showa Denko K.K. Evaporator
US7523781B2 (en) * 2005-01-24 2009-04-28 Halls Climate Control Corporation Heat exchanger
JP4613645B2 (ja) * 2005-03-09 2011-01-19 株式会社デンソー 熱交換器
US20100270012A1 (en) * 2006-09-25 2010-10-28 Korea Delphi Automotive Systems Corporation Automotive heat exchanger to the unification of header and tank and fabricating method thereof
JP5046771B2 (ja) * 2007-07-27 2012-10-10 三菱重工業株式会社 冷媒蒸発器
US8353330B2 (en) * 2007-11-02 2013-01-15 Halla Climate Control Corp. Heat exchanger

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007129851A1 (en) * 2006-05-09 2007-11-15 Korea Delphi Automotive Systems Corporation Heat exchanger for automobile and fabricating method thereof

Also Published As

Publication number Publication date
EP2336702A4 (de) 2014-04-09
US20110113823A1 (en) 2011-05-19
JP5408951B2 (ja) 2014-02-05
JP2010096423A (ja) 2010-04-30
EP2336702A1 (de) 2011-06-22
WO2010044420A1 (ja) 2010-04-22

Similar Documents

Publication Publication Date Title
EP2336702B1 (de) Kühlmittelverdampfer und klimaanlagenvorrichtung damit
US7398820B2 (en) Evaporator
US9759492B2 (en) Heat exchanger having additional refrigerant channel
US8413715B2 (en) Refrigerant evaporator with U-turn block and refrigerant-distributing holes
KR100532053B1 (ko) 증발기
US7886812B2 (en) Heat exchanger having a tank partition wall
US7886811B2 (en) Evaporator and process for fabricating same
US9518788B2 (en) Heat exchanger
US20080023183A1 (en) Heat exchanger assembly
EP3220093B1 (de) Wärmetauscher
US10168083B2 (en) Refrigeration system and heat exchanger thereof
JP5768480B2 (ja) 蓄冷熱交換器
US11624565B2 (en) Header box and heat exchanger
US10337808B2 (en) Condenser
US20170219298A1 (en) Header of heat exchanger
EP3971508B1 (de) Wärmetauscher
WO2015046275A1 (ja) 熱交換器及びそれを用いた空気調和機
JP2013139998A (ja) 熱交換器
EP2031334A1 (de) Wärmetauscher
KR20120129417A (ko) 축냉 증발기
AU2017444848B2 (en) Heat exchanger and refrigeration cycle device
CN111780459A (zh) 换热器及换热系统
KR20170022015A (ko) 축냉 증발기
CN111527356B (zh) 热交换器以及制冷循环装置
CN114729795A (zh) 热交换器

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: 20101119

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): 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 SE SI SK SM TR

AX Request for extension of the european patent

Extension state: AL BA RS

DAX Request for extension of the european patent (deleted)
A4 Supplementary search report drawn up and despatched

Effective date: 20140306

RIC1 Information provided on ipc code assigned before grant

Ipc: F28D 1/053 20060101ALI20140228BHEP

Ipc: F28F 9/02 20060101AFI20140228BHEP

Ipc: F25B 39/02 20060101ALI20140228BHEP

Ipc: F28D 21/00 20060101ALI20140228BHEP

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

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20180604

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: 20190107

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

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

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): 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 SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

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: 1151536

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190715

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602009059025

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20190703

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 1151536

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190703

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

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: 20191104

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: 20190703

Ref country code: AT

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: 20190703

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: 20190703

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: 20191003

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: 20190703

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: 20190703

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: 20190703

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: 20191003

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: 20190703

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

Ref country code: DE

Payment date: 20191016

Year of fee payment: 11

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: 20191103

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: 20191004

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: 20190703

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: 20190703

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: 20190703

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: 20190703

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: 20190703

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: 20190703

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: 20190703

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: 20190703

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

Ref country code: GB

Payment date: 20191023

Year of fee payment: 11

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

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: 20190703

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: 20190703

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: 20190703

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

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602009059025

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: LI

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

Effective date: 20191031

Ref country code: CH

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

Effective date: 20191031

Ref country code: LU

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

Effective date: 20191014

26N No opposition filed

Effective date: 20200603

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20191031

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: 20190703

Ref country code: BE

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

Effective date: 20191031

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: 20191031

Ref country code: IE

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

Effective date: 20191014

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602009059025

Country of ref document: DE

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: 20190703

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

Effective date: 20201014

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

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: 20091014

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: 20190703

Ref country code: DE

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

Effective date: 20210501

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: 20201014

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: 20190703