WO2019025963A1 - Distributeur de fluide amélioré - Google Patents

Distributeur de fluide amélioré Download PDF

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Publication number
WO2019025963A1
WO2019025963A1 PCT/IB2018/055719 IB2018055719W WO2019025963A1 WO 2019025963 A1 WO2019025963 A1 WO 2019025963A1 IB 2018055719 W IB2018055719 W IB 2018055719W WO 2019025963 A1 WO2019025963 A1 WO 2019025963A1
Authority
WO
WIPO (PCT)
Prior art keywords
fluid
distributor assembly
openings
fluid distributor
inlet
Prior art date
Application number
PCT/IB2018/055719
Other languages
English (en)
Inventor
Paolo PITRELLI
Paolo DONELLO
Original Assignee
Provides Metalmeccanica S.R.L.
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 Provides Metalmeccanica S.R.L. filed Critical Provides Metalmeccanica S.R.L.
Publication of WO2019025963A1 publication Critical patent/WO2019025963A1/fr

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Classifications

    • 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
    • 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
    • F25B39/028—Evaporators having distributing means
    • 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
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components

Definitions

  • the present invention relates to the field of aeraulic systems, in particular of conditioning systems.
  • the present invention more specifically, relates to a fluid distributor assembly suitable for use in a heat exchanger, in particular an evaporator.
  • Heat exchangers used in conditioning systems are devices that, in the most general terms, comprise a casing - or mantle - inside which is housed a tube bundle. Within the tube bundle, a service fluid flows to exchange heat with a process fluid at a different temperature.
  • the service fluid is typically an evaporating refrigerant fluid that circulates inside the tube bundle and cools the process fluid.
  • the latter passes externally to the tube bundle housed within the mantle, passing through the heat exchanger.
  • a supply pipe feeds the heat exchanger with refrigerant fluid, engaging it at a head unit - or manifold - thereof.
  • the exchanger is generally equipped with a dedicated distributor device.
  • the known distributor devices typically provide a plurality of fed conduits each engaging a respective tubular element of the tube bundle. Solutions of this type however have the drawback of being constructively complex due to expensive and sophisticate mechanical machining of the fed conduits connecting structure in order to maintain desired outlet conditions while conveying the fluid in each tube of the bundle.
  • the technical problem placed and solved by the present invention is then to provide a fluid distributor assembly, in particular a refrigerant fluid, within the tube bundle of a heat exchanger that allows to overcome the above-illustrated drawbacks with reference to the prior art.
  • the fluid distributor assembly according to present invention is structurally simple and economical to be realized, due to the presence of a lamination unit housed in a seat of the head unit in such a way that, a mixing chamber of refrigerant fluid that feeds the latter is defined.
  • the fluid distributor assembly comprises direction means provided with an impact surface and configured so as to direct the fluid outflowing from said lamination unit along a substantially orthogonal direction with respect to a fluid inlet direction into apertures of the tube plate engaging the tube bundle of the exchanger.
  • direction means allows to create fluid agitation conditions in the mixing chamber prior to its entry into the tube bundle.
  • said orthogonal flow to the fluid inlet direction into the tube plate is generated so as to sequentially lick the tube plate apertures and to allow each tube to suck the required amount of refrigerant, according to a kind of dynamical "self-regulation".
  • FIG. 1 shows an exploded view of a preferred embodiment of a fluid distributor assembly according to the present invention
  • FIG. 2 shows an enlarged view of a section of figure 1 , wherein a first component - the lamination unit - of the distributor assembly is partially housed in the latter;
  • figure 3 shows a side view of a portion of the distributor assembly according to the present invention shown in figure 1 ;
  • figure 4 shows a front view of the distributor assembly of figure 1 ;
  • FIG. 5 and 6 show a section of a portion of a side view of the distributor assembly of figure 1 respectively in a uncoupled and coupled condition
  • FIG. 7 and 8 respectively show an exploded view of a further embodiment of a fluid distributor assembly according to the present invention and a section of a portion of a side view of the distributor assembly of figure 7 in a coupled condition;
  • FIGS. 9 and 10 respectively show an exploded view of a further embodiment of a fluid distributor assembly according to the present invention and a section of a portion of a side view of the distributor assembly of figure 9 in a coupled condition.
  • FIG 1 an exploded view of a preferred embodiment of a fluid distributor assembly 1 , in particular a refrigerant fluid, according to the present invention is illustrated by way of example and not for limitative purposes.
  • the distributor assembly 1 of the present invention is intended for a preferred use in heat exchangers, preferably evaporators, such as direct evaporators.
  • the distributor assembly 1 is shown in association with a tube plate 100, the latter being an element to which the distributor assembly 1 is intended to be coupled.
  • the tube plate 100 is a plate with a circular geometry, exemplifying the tubular plates used in the considered technical field.
  • the tube plate 100 shown is not limitative for the purposes of the present invention.
  • the distributor assembly 1 comprises a head unit 10 - or manifold - configured to receive the refrigerant fluid inletting the heat exchanger and is intended to be coupled to the tube plate 100 at a coupling surface - denoted with reference A - thereof.
  • the head unit 10 therefore comprises at least one inlet 1 1 port, in fluid communication with the inlet refrigerant fluid flow, which allows the latter to enter said head unit 10.
  • the head unit 10 is thus a hollow element, that is an element in which is defined a transit region 12 through which the inlet fluid flow passes towards the tube plate 100.
  • the inlet 1 1 in the head unit 10 are intended to be two, however, in other embodiments, said inlet can be different in numbers, for example one or four, depending on the operating modes of the exchanger in which the distributor assembly according to the present invention will be mounted.
  • the coupling surface A - also with reference to the shown examples - is a peripheral region of the head unit 10 and of the respective tube plate 100, shaped so as to flange the above-mentioned two elements together.
  • this peripheral region defines a circular crown, however, different coupling geometries are possible.
  • the tube plate 100 of a heat exchanger comprises a zone having a plurality of apertures - or housings 101 - configured to put in fluid communication said head inlet 1 1 and tubes of the exchanger.
  • each aperture of said plurality is suitable for coupling with respective tubular elements (not shown in the figures) within which, in use, the refrigerant fluid flows.
  • the plurality of housings 101 - which in the examples are a plurality of through holes 101 a of the plate 100 - are configured to allow the refrigerant fluid inletting the head unit 10 passing towards tubular elements which typically engage with their terminal end the plate 100 at said housings, and which form the tube bundle housed within the exchanger's casing.
  • housings 101 are obtained only on a portion of the plate 100, particularly on the portion corresponding to one of the two inlet 1 1 of the head unit 10.
  • the distributor assembly 1 can be coupled with a tube plate 100 having a housings distribution different from that one illustrated.
  • the head unit 10 is further provided with a seat 13 adapted to receive a lamination unit 20, in particular of a plate-shaped geometry, which lamination unit 20 is positioned in said seat 13 so as to divide the transit region 12 of the head unit 10 in a first collecting chamber 14 and in an outlet region 15 of the refrigerant fluid.
  • the plate-shaped lamination unit 20 comprises an inlet surface 21 , an outlet surface 22 and one or more openings 23 to allow the fluid entering the head unit 10 to pass there through.
  • the first collecting chamber 14 is comprised between the inlet 1 1 adapted to receive the fluid entering the head unit 10 and said inlet surface 21 .
  • the outlet surface 22 of the plate-shaped lamination unit 20 faces toward said outlet region 15 of the refrigerant fluid.
  • Said one or more openings 23 are appropriately sized to obtain a pressure drop across the lamination unit 20.
  • the overall configuration of the distributor assembly 1 being such that, in condition of said head unit 10 coupled to the tube plate 100, a second mixing chamber 30 is defined at said outlet region 15 among said coupling surface A, said lamination unit 20 and the tube plate 100, so that the fluid, in use, sequentially crosses the first collecting chamber 14, the one or more openings 23 in the lamination unit 20 and subsequently the second mixing chamber 30.
  • the fluid is so administered into tubes connected to the tube plate 100.
  • the first collecting chamber 14 and the second mixing chamber 30 are preferably consecutive with each other and said outlet region 15 is adjacent to said outlet surface 22.
  • the first collecting chamber 14 and the second mixing chamber 30 are preferably arranged in sequence with respect to a fluid flow direction a as defined by the head inlet 1 1 .
  • the lamination unit 20 thus allows expansion of the refrigerant fluid in the second mixing chamber 30 with respect to the condition in which the fluid is in the first collecting chamber 14.
  • the refrigerant fluid flow F entering the inlet 1 1 of the head unit 10 reaches the lamination unit 20 and crosses said one or more openings 23 of the latter being subjected to a pressure drop causing it to expand into the second mixing chamber 30 and to generate a turbulent flow regime.
  • the presence of said mixing chamber 30 permits to improve the refrigerant fluid flow F' conditions before its inlet into the exchanger tube bundle, namely achieving a uniform mixing of the latter entering the through holes 101 a of the tube plate 100.
  • the lamination unit 20, as shown in the examples, is locked to the seat 13 of the head unit 10 onto shoulders 13a thereof. It is preferably fixed to the latter in a removable manner, by means of fastening means known to the skilled person in the field.
  • a spacer is configured to allow the fastening of the lamination unit 20 to the seat 13, wherein said spacer comprises a first and a second portion.
  • the first portion is internally hollow and configured to engage a through hole 101 a of the tube plate 100 and the second portion remains outside of the tube plate in such a way as to maintain the lamination unit in abutment onto said shoulders 13a of the head unit 10, spaced from the tube plate 100.
  • More than one spacer can be provided, the number of which is function of the operative condition of the distributor.
  • said spacers are provided in a homogeneous chessboard-like distribution.
  • the lamination unit 20 is however secured in such a way as to make the collecting chamber 14 hermetic, to avoid possible undesired fluid leaks towards the second mixing chamber 30.
  • the lamination unit 20 can also be made in a single piece with the head unit 10 at said seat 13.
  • the plate- shaped lamination unit 20 - or at least its outlet surface 22 - lies on a plane substantially parallel to the coupling surface A with the tube plate 100.
  • the fluid F' outflows from the lamination unit 20 at equidistant points from the through holes 101 a of said tube plate 100, further favoring a uniform mixing of the fluid F' entering the latter.
  • said one or more openings of the lamination unit 20 are denoted by reference 23.
  • said openings 23 comprise a plurality of circular geometric through holes, and are apt to put in fluid communication the first collecting chamber 14 with the second mixing chamber 30.
  • At least one of said one or more openings 23 comprise an elongated shape, for examples like a single slot, or through holes of other geometric shapes than the circular shape.
  • Said one or more openings may have, for example, a passageway configured so as to impart a substantially orthogonal direction to the fluid F' outflowing from the outlet surface 22 with respect to the direction of the fluid F inletting the lamination unit 20.
  • the amount and geometry of said one or more openings is a function of the operating conditions of the exchanger and of the desired fluid F pressure drop across the lamination unit 20.
  • Said one or more openings 23 are preferably distributed along a peripheral edge of the plate-shaped lamination unit 20, preferably in such a way as to do not directly face one or more of the through holes 101 a of the tube plate 100, as provided by the embodiment of figures 7 and 8.
  • said one or more openings 23 are arranged laterally with respect to an input fluid flow F having a direction a as imparted by said head inlet 1 1 .
  • the fluid distributor assembly 1 further comprises direction means provided with an impact surface 241 , 26 configured so as to direct the fluid outflowing from said outlet surface 22 along a substantially orthogonal direction with respect to a fluid inlet direction ⁇ into said apertures 101 .
  • Said direction means allow to generate an orthogonal flow F' with respect to the fluid inlet direction ⁇ into the tube plate 100 so as to sequentially lick said apertures 101 .
  • Each tube of the tube bundle of the exchanger is therefore able to suck the required amount of refrigerant, according to a kind of dynamical "self-regulation".
  • said orthogonal flow F' with respect to said direction ⁇ is achieved by providing an antagonistic element positioned downstream the expansion of the flow outflowing the outlet surface 22.
  • the apertures 101 of the tube plate 100 are arranged laterally with respect to a positioning of each of said one or more openings 23 of the lamination unit 20.
  • said direction means comprises an impact surface 26 of the tube plate 100 facing toward said second mixing chamber 30.
  • each of said apertures 101 and each of said one or more openings 23 is such that they do not directly face to each other, namely said one or more openings 23 face directly towards a portion of the tube plate 100 lacking of apertures 101 a.
  • the flow outflowing from the latter collides with the impact surface 26 that is configured to give to the flow F' an orthogonal direction to the fluid inlet direction ⁇ into the apertures 101 .
  • said impact surface 26 of the tube plate 100 comprises said coupling surface A or lies in a plane comprising the latter, as illustrated with reference to the embodiment shown in figure 8.
  • the surface of the tube plate 100 facing toward the second mixing chamber 30 is provided with apertures 101 distributed on opposite sides.
  • said impact surface 26 is positioned in a central region of the tube plate 100, namely between said apertures 101 .
  • the one or more openings 23 of the lamination unit 20 are arranged in such a way as to face said central region of the tube plate 100.
  • the impact surface 26 is arranged along a substantially orthogonal direction with respect to a fluid inlet direction into said apertures 101.
  • the direction of the refrigerator fluid flow entering the apertures 101 is identifiable by a coordinate system of three axes mutually orthogonal to each other, as shown in the figures.
  • the fluid inlet direction ⁇ into the apertures 101 is parallel to axis z that is substantially orthogonal to axis x and y which comprise the plane containing the fluid F' direction, as directed by the impact surface 26.
  • said direction means comprises flow deviation members 24, 25 arranged onto the outlet surface 22 of said lamination unit 20.
  • said flow deviation members comprises a wall 24 configured in such a way as to prevent a direct channeling of the fluid F' into the through holes 101 a of the tube plate 100.
  • said wall 24 protrudes from the outlet surface 22 of the lamination unit 20 in correspondence of its openings 23, specifically it is arranged laterally to said one or more openings 23.
  • the wall 24 comprises said impact surface 241 positioned in front of said one or more openings and in such a way as to hinder the fluid flow - outflowing from said one or more openings 23 - to directly enter into at least one of the through holes 101 .
  • said wall 24 has a "L"-shaped geometry, provided with a proximal lateral portion 242 connected to the impact surface 241.
  • the impact surface 241 is configured as a distal portion of said "L"-shaped geometry facing toward said one or more openings and arranged substantially parallel to and spaced from the outlet surface 22.
  • the flow direction of the fluid F' is forced into a region of the second mixing chamber 30 comprising the openings 23 and only one of the sides of the plane comprised by the x, y axis, as defined by the interception with the proximal lateral portion 242.
  • said proximal lateral portion 242 operates such as a barrier.
  • the wall 24 is configured so as to confer to the fluid F' a direction substantially parallel to the development direction of the outlet surface 22.
  • said flow deviation members comprise an impact surface provided with one or more connecting portions configured to connect the impact surface to said outlet surface 22 in such a way as to allow the fluid F' outflowing along each of the direction comprised in the x, y plane.
  • the impact surface can be positioned in front of and spaced from the openings 23, in such a way as to cover them entirely.
  • Said impact surface can be connected to the outlet surface 22 by means of two end opposite walls.
  • each of said two end opposite walls develops along a direction parallel to each other and to x axis and/or along an orthogonal direction with respect to the distribution of the openings 23.
  • said impact surface can be connected to the outlet surface 22 by means of said two end opposite walls and by a further wall interposed between them, also in order to confer a structural reinforcement to the connection.
  • the fluid F' is therefore allowed to outflowing from the lamination unit along a substantially orthogonal direction with respect to the fluid inlet direction ⁇ into apertures of the tube plate 100, without being blocked by side walls that narrow its circulation inside the second mixing chamber 30.
  • embodiments may be provided with said wall 24 even though said one or more openings 23 of the lamination unit 20 are arranged such as to do not directly face the through holes 101 a of the tube plate 100 when the distributor assembly 1 is flanged to the latter.
  • said flow deviation members further comprises one or more ridges 25 - or turbo-stroke ridges - embossed on the outlet surface 22 of the lamination unit 20.
  • Said one or more ridges 25 are preferably arranged along an orthogonal transvers direction relative to the direction of fluid outflowing from said one or more openings 23 of the lamination unit 20.
  • Said one or more ridges 25 may protrude from the outlet surface 22 with different heights and have sections with polygonal or curvilinear geometries. Said ridges can also be made in a single piece with the lamination unit 20 or fixed to the latter, the amount of which is function of the desired outlet conditions to be conferred to the fluid flow F'.
  • Said ridges can be also designed for the purpose to gain a structural reinforcement of the lamination unit 20 and eventually can be configured as spacer between the tube plate 100 and the outlet surface 22.
  • ridges 25' are arranged along a longitudinal direction with respect to the flow F'.
  • the flow F' is orthogonal to the fluid inlet direction ⁇ into the tube plate 100 so as to sequentially lick said apertures 101.
  • said ridges 25' are spaced from and parallel to each other in such a way as to define a plurality of lanes 25".
  • Each of said ridges 25' has a length preferably shorter than the length of the lamination unit 20, considering the latter length comprised between the shoulders 13a of the head unit 10 and parallel to the direction of the fluid flow F'.
  • the latter length comprised between the shoulders 13a of the head unit 10 and parallel to the direction of the fluid flow F'.
  • other embodiments may be provided with different numbers of ridges 25' and therefore different number of lanes 25".
  • the ridges 25' allow to divide the second mixing chamber 30 in such a way as to constrain the fluid F', outflowing from said one or more openings 23, in a plurality of delimited regions.
  • Each region of said plurality preferably developing along a main developing direction that is substantially parallel to the direction x, as above defined and also with reference to figure 2 and 10.
  • each of the ridges 25' preferably projects from the outlet surface 22 in such a way as to maintain the latter and the tube plate 100 spaced therebetween.
  • Said spacing advantageously, allows the fluid to reach every tubular member of the tube bundle even in case of a bad distribution upstream of said one or more openings 23.
  • ridges 25' can be configured as spacer between the tube plate 100 and the outlet surface 22. Said spacing can be obtained, for example, by providing a battlement shape along the length of ridges 25' properly dimensioned to contact in selected points the tube plate 100.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Abstract

Ensemble de distribution de fluide, notamment de fluide frigorigène, destiné à être utilisé dans un échangeur de chaleur comprenant : une unité de tête couplée à une plaque de tube et comprenant une entrée configurée pour recevoir le fluide introduit dans l'échangeur ; une unité de stratification en forme de plaque comprenant une ou plusieurs ouvertures pour permettre au fluide d'entrée de passer à travers celle-ci, l'unité de tête étant pourvue d'un siège conçu pour recevoir ladite unité de stratification, de telle sorte que le fluide traverse séquentiellement une première chambre de collecte et une seconde chambre de mélange, et des moyens de direction pourvus d'une surface d'impact étant configurés de façon à diriger le fluide sortant de l'unité de stratification le long d'une direction sensiblement orthogonale par rapport à une direction d'entrée de fluide dans des ouvertures de la plaque de tube.
PCT/IB2018/055719 2017-08-01 2018-07-31 Distributeur de fluide amélioré WO2019025963A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP17184287.5A EP3438596B1 (fr) 2017-08-01 2017-08-01 Distributeur de fluide amélioré
EP17184287.5 2017-08-01

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WO2019025963A1 true WO2019025963A1 (fr) 2019-02-07

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Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112033048B (zh) * 2020-08-31 2022-09-16 青岛海尔空调电子有限公司 干式蒸发器

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL7901817A (nl) * 1978-06-30 1980-01-03 Schwermasch Liebknecht Veb K Stromingsgeleidingslichaam voor warmteoverdraagin- richtingen en werkwijze voor het bevestigen daarvan.
US5465783A (en) * 1994-03-04 1995-11-14 Fedco Automotive Components Company, Inc. Sacrificial erosion bridge for a heat exchanger
JPH1089885A (ja) * 1996-09-11 1998-04-10 Calsonic Corp 熱交換器用金属製タンクと金属製入口管との接合部
JP2003065696A (ja) * 2001-08-24 2003-03-05 Honda Motor Co Ltd ラジエータ
US20080296003A1 (en) * 2007-05-29 2008-12-04 Showa Denko K.K. Heat exchanger
AT507552A4 (de) * 2009-05-22 2010-06-15 Siemens Vai Metals Tech Gmbh Verfahren und vorrichtung zur beeinflussung von strömungscharakteristika in einem fluidstrom
WO2010083978A2 (fr) * 2009-01-21 2010-07-29 Basf Se Réacteur à faisceau tubulaire pour des réactions non catalysées ou de catalyse homogène
US20130112381A1 (en) * 2010-07-16 2013-05-09 Alfa Laval Corporate Ab Heat exchange device with improved system for distributing coolant fluid
US20150136366A1 (en) * 2012-07-09 2015-05-21 Sumitomo Precision Products Co., Ltd. Heat exchanger
US20160076822A1 (en) * 2014-09-16 2016-03-17 Delphi Technologies, Inc. Heat exchanger distributor with intersecting streams
US20170092382A1 (en) * 2015-09-28 2017-03-30 Ge-Hitachi Nuclear Energy Americas Llc Modular systems and methods for energetic fluid flow distribution

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL7901817A (nl) * 1978-06-30 1980-01-03 Schwermasch Liebknecht Veb K Stromingsgeleidingslichaam voor warmteoverdraagin- richtingen en werkwijze voor het bevestigen daarvan.
US5465783A (en) * 1994-03-04 1995-11-14 Fedco Automotive Components Company, Inc. Sacrificial erosion bridge for a heat exchanger
JPH1089885A (ja) * 1996-09-11 1998-04-10 Calsonic Corp 熱交換器用金属製タンクと金属製入口管との接合部
JP2003065696A (ja) * 2001-08-24 2003-03-05 Honda Motor Co Ltd ラジエータ
US20080296003A1 (en) * 2007-05-29 2008-12-04 Showa Denko K.K. Heat exchanger
WO2010083978A2 (fr) * 2009-01-21 2010-07-29 Basf Se Réacteur à faisceau tubulaire pour des réactions non catalysées ou de catalyse homogène
AT507552A4 (de) * 2009-05-22 2010-06-15 Siemens Vai Metals Tech Gmbh Verfahren und vorrichtung zur beeinflussung von strömungscharakteristika in einem fluidstrom
US20130112381A1 (en) * 2010-07-16 2013-05-09 Alfa Laval Corporate Ab Heat exchange device with improved system for distributing coolant fluid
US20150136366A1 (en) * 2012-07-09 2015-05-21 Sumitomo Precision Products Co., Ltd. Heat exchanger
US20160076822A1 (en) * 2014-09-16 2016-03-17 Delphi Technologies, Inc. Heat exchanger distributor with intersecting streams
US20170092382A1 (en) * 2015-09-28 2017-03-30 Ge-Hitachi Nuclear Energy Americas Llc Modular systems and methods for energetic fluid flow distribution

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Publication number Publication date
EP3438596B1 (fr) 2020-04-08
EP3438596A1 (fr) 2019-02-06

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