EP3039372B1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
EP3039372B1
EP3039372B1 EP14749833.1A EP14749833A EP3039372B1 EP 3039372 B1 EP3039372 B1 EP 3039372B1 EP 14749833 A EP14749833 A EP 14749833A EP 3039372 B1 EP3039372 B1 EP 3039372B1
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EP
European Patent Office
Prior art keywords
transfer device
heat transfer
material flow
tube
tubes
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
EP14749833.1A
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German (de)
English (en)
Other versions
EP3039372A1 (fr
Inventor
Peter Geskes
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
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Publication of EP3039372A1 publication Critical patent/EP3039372A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
    • F02M26/32—Liquid-cooled heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/422—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element with outside means integral with the tubular element and inside means integral with the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like 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
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/044—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being pontual, e.g. dimples
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations
    • 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
    • F28F9/0282—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry of conduit ends, e.g. by using inserts or attachments for modifying the pattern of flow at the conduit inlet or outlet

Definitions

  • the invention relates to a heat exchanger according to the preamble of claim 1. It further relates to an exhaust gas cooler with such a heat exchanger.
  • exhaust gas coolers are used in this context, which are thermally loaded to a high degree by the introduced combustion exhaust gases. The latter can have temperatures of up to 700 ° C. during operation of the internal combustion engine.
  • the flow guide element has a planar ground plane extending in the main flow longitudinal direction, wherein at least partially lateral boundary structures rise above the ground plane to form at least one flow path.
  • the at least one flow path has an upstream first distance of the lateral limiting structures and a downstream second distance of the lateral limiting structures, wherein the Distances are so different that a pressure loss of the fluid associated with the flow path from a location associated with the upstream first distance to a location associated with the downstream second distance is other than a pressure loss of an imaginary flow path having substantially equally spaced confining structures.
  • From the EP 1 985 953 A1 is a heat exchanger with a substantially fluid-tight housing for directing a first stream of material, in particular a coolant, and at least one extending in the housing heat-permeable pipe for conducting a second material flow, for example, a combustion exhaust gas known.
  • the housing and the outer surfaces of the at least one tube thereby form parallel flow paths for the first material flow, which are delimited by a bottom in which the at least one tube is gripped.
  • the invention is therefore based on the object to provide an improved heat exchanger, which - especially in the context of exhaust gas cooling - reliably avoids the occurrence of so-called hotspots.
  • Another object of the invention is to provide a corresponding exhaust gas cooler.
  • the invention is therefore based on the basic principle of a tube heat exchanger (RWÜ), through the so-called tube space, a second stream, such as exhaust gas of an internal combustion engine, pumped or otherwise promoted.
  • the at least one tube forming the tube space in this case runs in a so-called jacket space which is bounded by a fluid-tight housing and which is separated from a first material flow, for example coolant, is flowed through, and is provided according to the invention with elevations on its outer surface, which accumulate the / the tube (s) flowing around the first material flow, so for example, the coolant to a small extent and thereby steer.
  • the housing and the outer surfaces of the at least one tube form parallel flow paths for the first material flow, which are frontally limited by a bottom in which the at least one tube is taken. Via a connection, the first material flow in the region of the bottom, preferably orthogonal to the second material flow, is introduced into the housing.
  • the elevations on the outer surfaces of the tubes are designed such that the first material flow is distributed substantially uniformly in the region of the bottom after entry into the housing and is divided substantially evenly on the flow paths.
  • the elevations on the outer surfaces of the tubes accumulate the first material flow in some areas at least slightly, thereby diverting it to other, less well-flowed and boiling areas at risk, or increase the volume flow there.
  • this modification of the heat exchanger proves to be advantageous.
  • the described surveys of the pipe surfaces namely reduce the risk of the formation of so-called dead spaces or hotspots within the exhaust gas cooler, which are insufficiently flowed through by coolant and thus exposed to a particularly intense thermal load.
  • the coolant circuit is often operated with a low flow rate for the purpose of saving energy
  • the configuration of the heat exchanger according to the invention thus contributes to considerably reduce the risk of overheating phenomena such as local boiling of the refrigerant, resulting in adverse chemical reactions and to significantly increase the overall service life of the exhaust gas cooler in this way.
  • the porosity factor F thus increases in the heat exchanger at the tubes from the top downwards from the connection.
  • said elevations are formed by means of a suitable forming technique in a sheet comprising the outer surface, for example a thin sheet.
  • a suitable forming technique in a sheet comprising the outer surface, for example a thin sheet.
  • an established pressure forming method is recommended, in particular the stamping of the elevation into a flat region of the outer surface.
  • Suitable forming tool such as embossing machines or pressing is familiar to the skilled worker and proven under production-practical aspects.
  • the shape of the surveys a variety of possible variants is available, ranging from a simple nub on the outer surface to the embossing of the survey by a bead of the opposite inner surface of the sheet.
  • the latter option opens up a wide range of different shaping alternatives and angles of attack to a person skilled in the art in view of the availability of various bead rolls.
  • the execution of the surveys as beads additionally not only reduces the degradation of any stress peaks in the sheet metal of the pipes due to the embossing process, but advantageously also contributes to the stiffening of the entire heat exchanger.
  • the tubes are preferably provided with winglets, which can significantly increase the turbulence of the first and / or second material flow.
  • winglets can significantly increase the turbulence of the first and / or second material flow.
  • a comparable maximization of the contact surface can be achieved by means of ribs shaped analogously in the metal sheet, for example cooling fins, which at the same time increase the mechanical strength of the heat exchanger at the price of a slight increase in weight and reduce the sound radiation of a corresponding exhaust gas cooler by suppressing surface vibrations.
  • the tubes may be materially connected to the bottom of the housing, so that the resulting atomic or molecular forces support the structural cohesion of the heat exchanger.
  • a material bond can also be achieved by means of soldering, without to exceed the liquidus temperature of the pipe or the ground, accepting the known detrimental consequences for the respective base materials.
  • the tube heat exchanger in the context of exhaust gas cooling, it may prove pragmatic to equip the tube heat exchanger according to the invention with a diffuser oriented at right angles to the connection for introducing the combustion exhaust gases to be cooled.
  • a diffuser oriented at right angles to the connection for introducing the combustion exhaust gases to be cooled.
  • FIG. 1 illustrates the specific nature of a tube 5 of a heat exchanger 1 according to the invention (cf. Fig. 6 ).
  • tube 5 - 10 is to be understood as meaning any substantially fluid-tight hollow body whose length is substantially greater than its diameter and which-for example, in contrast to a tube-is made of a comparatively inflexible material.
  • the tube 5 of FIG. 1 concretely has a rectangular cross-section and thus overall an approximately cuboid shape.
  • Such a design is sometimes referred to as right edge and presently formed by two narrow outer surfaces 12, 13 and two wide outer surfaces 14, 15 of sheet metal, which constitute the lateral walls of the tube 5.
  • the narrow outer surfaces 12, 13 are each provided with a convex elevation 16 orthogonal to its longitudinal axis in the form of a short transverse bead 17 of the corresponding counter surface, while the broad outer surfaces 14, 15 have elevations 16 which are characterized by long transverse corrugations 18 in an analogous manner are.
  • Technical limitations of the forming process used in the manufacturing process mean that at least those from the perspective of the FIG.
  • FIG. 2 is characterized by a survey 16, 19, which is not like the beads 17, 18 channel-shaped, but hump-like in the form of a nearly circular knob 16 is formed.
  • the corresponding pipe 6 has the FIG. 2 star-shaped from the nub 16 continuing so-called winglets 19, which enlarge the wide outer surfaces 14, 15 of the tube 6 and tend to promote turbulence of the guided therein or around material flow 11, 4.
  • pipe 8 shown in cross section FIG. 4 is in addition to the beads 17, 18 provided with further geometric optimizations in the form of ribs 20.
  • FIG. 6 illustrates the benefits of a heat exchanger 1 according to the invention in the context of an exhaust gas cooler 2, which is in fluid communication via a lateral connection 22 with a coolant circuit and via a front side arranged diffuser 23 with an exhaust pipe.
  • an exhaust gas cooler 2 which is in fluid communication via a lateral connection 22 with a coolant circuit and via a front side arranged diffuser 23 with an exhaust pipe.
  • the lateral attachment of the terminal 22 causes a comparison in almost orthogonal entry of the formed by a suitable coolant first material flow 4 in the bounded by the housing 3 shell space of the heat exchanger 1, but formed by the downstream of the terminal 22 in the tubes 5 short and long Elevations 16 / transverse seeding 17, 18 is not insignificantly delayed.
  • the resulting slight backflow of the coolant within the input region of the housing 3 ensures a largely homogeneous volume flow along its entire width along the outer surfaces 12, 13, 14, 15 of the tubes 5, so that overheating, in particular in the regions facing away from the connection 22, in particular in a There in conventional heat exchangers occurring dead space, the housing 3 can be avoided.
  • the number of elevations 16 / beads 17, 18 decreases in the tubes 5 from top to bottom, resulting in a blocking of the flow paths 24 is increasingly reduced.
  • the mutually contacting elevations 16 / beads 17, 18 of adjacent tubes 5 can in turn be permanently connected in order to increase the rigidity of the exhaust gas cooler 2.
  • a ratio a / h between a distance a between the bottom 21 and the elevation 16 / bead 17, 18 and the height h of the bottom 21 is 0.3 ⁇ a / h ⁇ 0.7, preferably 0.4 ⁇ a / h ⁇ 0.6. This allows a particularly uniform temperature distribution can be achieved.
  • the distance a between the bottom 21 and the elevation 16 / bead 17, 18 is about 20 to 60 mm, preferably 30 to 60 mm. This ensures an optimal stowage effect of the first material stream 4, for example of the coolant, and thereby for a particularly equal distribution of the same in the region of Soil 21, which in particular so-called "hotspots", where a boiling of the first stream 4 must be feared, can be avoided.
  • a homogeneous as possible tempered flow field is to be generated, whose temperature is below the boiling temperature of the coolant 4, whereby a local boiling of the same can be avoided with the associated problems.
  • the elevations 16 / beads 17, 18 at individual or at several points in the circumferential direction of the tube 5 - 10 may be arranged.
  • the elevations 16 / beads 17, 18 need not go beyond the entire pipe width beyond, but may also only partially extend over the pipe width.
  • the beads 17, 18 and elevations 16 never completely block the flow paths 24, a part of the first material flow 4 can thus still flow along the tubes 5 - 10 despite the elevations 16 / beads 17, 18.
  • the porosity factor F thus increases in the heat exchanger 1 in the tubes 5 - 10, starting from the terminal 22 from top to bottom.
  • the porosity factor F (degree of opening) thus increases the closer the respective tube 5 - 10 or the respective row of tubes is to the hotspots).
  • the value should be between 60% and 90%, because then the pressure drop does not increase too much.
  • the tubes 5 - 10 along their longitudinal axis may have a plurality of elevations / beads 16, 17, 18 at specific spacings or characteristic combinations of transverse and longitudinal elevations / beads 16, 17, 18.
  • the elevations / beads 16, 17, 18 may be provided only on one side of each tube 5 - 10, but have a relation to the two-sided configuration doubled height.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (11)

  1. Échangeur de chaleur (1), en particulier pour un refroidisseur de gaz d'échappement (2), avec
    - un boîtier (3) sensiblement étanche aux fluides pour la conduite d'un premier flux de matière (4), un particulier d'un réfrigérant, et
    - au moins un tube (5-10) perméable à la chaleur s'étendant dans le boîtier (3) pour la conduite d'un deuxième flux de matière (11), en particulier d'un gaz de combustion,
    - dans lequel le boîtier (3) et des surfaces extérieures (12, 13, 14, 15) de l'au moins un tube (5-10) forment des trajets d'écoulement parallèles (24) pour le premier flux de matière (4), qui sont délimités côté frontal par un fond (21), dans lequel l'au moins un tube (5-10) est enchâssé,
    - un raccord (22), par le biais duquel le premier flux de matière (4) peut être introduit dans la zone du fond (21) dans le boîtier (3),
    - dans lequel une surface extérieure (12, 13, 14, 15) de l'au moins un tube (5-10) présente une élévation (16, 17, 18) de sorte que le premier flux de matière (4) après l'entrée dans le boîtier (3) est distribué de manière sensiblement homogène dans la zone du fond (21) et réparti de manière sensiblement homogène sur le trajet d'écoulement (24),
    dans lequel le tube (5-10) comprend une tôle, laquelle présente la surface extérieure (12, 13, 14, 15), et l'élévation (16, 17, 18) est moulée, en particulier estampée, dans la tôle,
    caractérisé en ce
    - qu'un facteur de porosité F des trajets d'écoulement (24) respectifs se situe entre 60 % et 90 %, dans lequel le facteur de porosité F est défini comme suit F = A _ KM 1 − A _ KM 2 / A _ KM 2
    Figure imgb0005
     avec :
    A_KM1 : surface côté réfrigérant, qui est imputable à un des tubes, avec des élévations/moulures (en tant que surface partielle de la section transversale totale)
    A_KM2 : surface côté réfrigérant, qui est imputable à un des tubes, mais bloquée avec des élévations/moulures
    (A_KM1-A_KM2) surface ouverte restante, par laquelle le réfrigérant (KM) peut continuer de s'écouler,
    - que le facteur de porosité F se situe dans la plage de 20 %, pour les tubes (5) plus éloignés des points chauds, en passant par F env. 80 %, pour les tubes (5) se trouvant plus près des points chauds, jusqu'à F = 100 %, pour les tubes (5) se trouvant directement adjacents aux points chauds, dans lequel 100 % signifie une perméabilité complète sans élévations (16)/moulures (17, 18),
    - le facteur de porosité F augmente du haut vers le bas en partant du raccord (22) pour les tubes (5-10) pour l'échangeur de chaleur (1).
  2. Échangeur de chaleur selon la revendication 1,
    caractérisé en ce
    que l'élévation (16, 17, 18) est une nope (16).
  3. Échangeur de chaleur selon la revendication 1,
    caractérisé en ce
    que la tôle présente une surface intérieure avec une moulure (17, 18) située en face de la surface extérieure (12, 13, 14, 15), de sorte que la moulure (17, 18) de la surface intérieure marque l'élévation (16, 17, 18) de la surface extérieure (12, 13, 14, 15).
  4. Échangeur de chaleur selon la revendication 3,
    caractérisé en ce
    - que la moulure (17, 18) s'étend transversalement ou le long du premier flux de matière (4), et/ou
    - que les élévations (16, 17, 18) s'étendent dans la direction circonférentielle au moins en partie sur la surface extérieure (12, 13, 14, 15).
  5. Échangeur de chaleur selon la revendication 3 ou 4,
    caractérisé en ce
    que la surface intérieure présente en outre au moins un winglet (19) et/ou au moins une nervure (20).
  6. Échangeur de chaleur selon l'une quelconque des revendications 1 à 5,
    caractérisé en ce
    que l'au moins un tube (5-10) est un tube rectangulaire (5) avec deux surfaces extérieures étroites (12, 13) et deux surfaces extérieures larges (14, 15).
  7. Échangeur de chaleur selon l'une quelconque des revendications 1 à 6,
    caractérisé en ce
    que le fond (21) est relié par matière à l'au moins un tube (5-10), en particulier brasé ou soudé.
  8. Échangeur de chaleur selon l'une quelconque des revendications 1 à 7,
    caractérisé en ce
    que l'élévation (16, 17, 18) présente une hauteur entre 0,5 mm et 3 mm, de préférence inférieure à 1,5 mm.
  9. Échangeur de chaleur selon l'une quelconque des revendications 1 à 8,
    caractérisé en ce
    que le rapport suivant s'applique
    0,3 < a/h < 0,7 de préférence 0,4 < a/h < 0,6
    avec a : distance entre le fond (21) et l'élévation (16, 17, 18)
    h : hauteur du fond (21).
  10. Échangeur de chaleur selon la revendication 9,
    caractérisé en ce
    que la distance a entre le fond (21) et l'élévation (16, 17, 18) est d'environ 20 à 60 mm, de préférence 30 à 60 mm.
  11. Refroidisseur de gaz d'échappement (2) avec
    - un raccord (22) relié à une conduite de réfrigérant pour l'introduction d'un premier flux de matière (4), en particulier d'un réfrigérant, dans le refroidisseur de gaz d'échappement (2) et
    - un diffuseur (23) relié à une conduite de gaz d'échappement pour l'introduction d'un deuxième flux de matière (11) d'un gaz de combustion dans le refroidisseur de gaz d'échappement (2),
    - dans lequel le raccord (22) et le diffuseur (23) sont agencés l'un par rapport à l'autre de sorte que le premier flux de matière (4) est introduit sensiblement perpendiculairement au deuxième flux de matière (11),
    caractérisé par
    un échangeur de chaleur (1) selon l'une quelconque des revendications 1 à 10 pour le transfert de chaleur du deuxième flux de matière (11) au premier flux de matière (4).
EP14749833.1A 2013-08-19 2014-08-08 Échangeur de chaleur Not-in-force EP3039372B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013216408.4A DE102013216408A1 (de) 2013-08-19 2013-08-19 Wärmeübertrager
PCT/EP2014/067103 WO2015024802A1 (fr) 2013-08-19 2014-08-08 Échangeur de chaleur

Publications (2)

Publication Number Publication Date
EP3039372A1 EP3039372A1 (fr) 2016-07-06
EP3039372B1 true EP3039372B1 (fr) 2019-05-01

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EP14749833.1A Not-in-force EP3039372B1 (fr) 2013-08-19 2014-08-08 Échangeur de chaleur

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US (1) US20160208746A1 (fr)
EP (1) EP3039372B1 (fr)
DE (1) DE102013216408A1 (fr)
WO (1) WO2015024802A1 (fr)

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KR102371237B1 (ko) * 2017-05-11 2022-03-04 현대자동차 주식회사 수냉식 이지알 쿨러, 및 이의 제조방법
DE102017212237A1 (de) * 2017-07-18 2019-01-24 Mahle International Gmbh Wärmeübertrager

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EP3039372A1 (fr) 2016-07-06
US20160208746A1 (en) 2016-07-21
DE102013216408A1 (de) 2015-02-19
WO2015024802A1 (fr) 2015-02-26

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