WO2017004058A1 - Évaporateur distributeur à deux phases - Google Patents

Évaporateur distributeur à deux phases Download PDF

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Publication number
WO2017004058A1
WO2017004058A1 PCT/US2016/039850 US2016039850W WO2017004058A1 WO 2017004058 A1 WO2017004058 A1 WO 2017004058A1 US 2016039850 W US2016039850 W US 2016039850W WO 2017004058 A1 WO2017004058 A1 WO 2017004058A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
manifold
opening
fluid
exchanger according
Prior art date
Application number
PCT/US2016/039850
Other languages
English (en)
Inventor
Abbas A. Alahyari
Richard Rusich
Thomas D. Radcliff
Original Assignee
Carrier Corporation
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 Carrier Corporation filed Critical Carrier Corporation
Priority to ES16739622T priority Critical patent/ES2822826T3/es
Priority to EP16739622.5A priority patent/EP3314191B1/fr
Priority to CN201680038713.4A priority patent/CN107850396A/zh
Priority to US15/580,214 priority patent/US20180156544A1/en
Publication of WO2017004058A1 publication Critical patent/WO2017004058A1/fr

Links

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
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • 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
    • 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
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0275—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple branch pipes
    • 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
    • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing

Definitions

  • This disclosure relates generally to heat exchangers and, more particularly, to a heat exchanger distributor assembly and a method of distributing fluid to a heat exchanger.
  • heat exchangers such as mini-channel, microchannel, plate-fin, and brazed-plate heat exchangers for example, distribution is particularly difficult due to the requirement that the flow be distributed among many layers and small ports.
  • these types of heat exchangers may employ a distributor having a closed-end tube with a series of holes in the side.
  • distributors may not prevent separation of the two-phase fluid under different operating conditions.
  • a heat exchanger including a plurality of parallel stacked plates defining at least one flow passage there between.
  • a manifold having a generally hollow interior is arranged adjacent the plurality of parallel plates.
  • An opening is disposed between adjacent stacked plates. The opening is configured to fluidly couple the hollow interior of the manifold and the at least one flow passage.
  • a distributor assembly including an insert is disposed at least partially within the hollow interior of the manifold.
  • the insert includes a plurality of circumferentially spaced axial flow channels and a plurality of radial connecting channels arranged in fluid communication with the axial flow channels. The radial flow channels are fluidly coupled to the at least one flow passage via the opening.
  • a portion of the manifold is received within at least one of the plurality of plates.
  • the entire manifold is received within the plurality of plates.
  • an edge of the manifold is arranged in contact with an outer edge of the plurality of plates.
  • each of the at least one flow passages is arranged in fluid
  • the opening is defined by at least one of a ridge extending from at least one of the plurality of stacked plates defining the flow passage and a seal surrounding a portion of the manifold adjacent the flow passage fluidly coupled thereto.
  • a fluid within the distributor assembly is supplied to the plurality of axial flow channels substantially equally.
  • the distributor assembly is configured to supply a fluid to each opening at a substantially identical azimuthal angle.
  • the distributor assembly is configured to supply a fluid to each opening at a different azimuthal angle.
  • the distributor assembly further comprises a nozzle arranged upstream from the plurality of axial flow channels, the nozzle being configured to create a homogeneous distribution of a fluid.
  • the nozzle includes a constriction configured to produce a pressure drop in the fluid.
  • FIG. 1 is an example of a conventional vapor compression system
  • FIG. 2 is a exploded view of an example of a parallel flow brazed plate heat exchanger
  • FIGS. 2a-2c are cross-sectional views of various manifold configurations
  • FIG. 3 is a cross-sectional view of a portion of the parallel flow heat exchanger of FIG. 2;
  • FIG. 4 is a perspective view of a distributor configured for use in a manifold of a heat exchanger according to an embodiment of the present disclosure
  • FIG. 5 is a cross-sectional view of the distributor of FIG. 4 according to an embodiment of the present disclosure.
  • FIG. 6 is a front view of a plate of a plate-fin heat exchanger and an adjacent distribution channel fluidly coupled thereto according to another embodiment of the present disclosure.
  • refrigerant flow maldistribution may occur in the heat exchanger when a homogeneous two-phase mixture is allowed to phase separate in the manifold.
  • a vapor phase of the two-phase mixture has significantly different properties and is subjected to different effects of internal forces than a liquid phase. This can contribute to phase separation if the velocity of the homogeneous two-phase mixture is reduced (e.g., as the flow area expands entering the manifold).
  • the flow may stratify due to deceleration in the manifold such that the flow to each passage of the heat exchanger may not be properly apportioned.
  • FIG. 1 An example of a basic refrigerant system 20 is illustrated in FIG. 1 and includes a compressor 22, condenser 24, expansion device 26, and evaporator 28.
  • the compressor 22 compresses a fluid, such as refrigerant for example, and delivers it
  • the refrigerant passes through the expansion device 26 into an inlet refrigerant pipe 30 leading to the evaporator 28. From the evaporator 28, the refrigerant is returned to the compressor 22 to complete the closed-loop refrigerant circuit.
  • FIG. 2 an example of a heat exchanger 40, for example configured for use as the evaporator 28 of the system 20, is illustrated in more detail.
  • the heat exchanger 40 of the present disclosure may be configured for use in a plurality of other processes, such as pumped refrigerant loops, Rankin cycles, or other industrial heat exchange applications.
  • the heat exchanger 40 is a brazed plate heat exchanger; however, other types of heat exchangers, such as raicrochannel heat exchangers and plate fin heat exchangers for example, are within the scope of the present disclosure.
  • the heat exchanger 40 comprises a plurality of corrugated plates 42a, 42b disposed along substantially parallel plates and being stacked in an alternating arrangement.
  • the plates 42a, 42b may be made of stainless steel, sheet metal clad, or are otherwise coated with a thin layer of braze material (not shown) that provides a joining interface at contact points between adjacent plates 42a, 42b.
  • braze material not shown
  • plates 42a, 42b are temporarily clamped together and heated to permanently braze plates 42a, 42b together to create alternating layers of a plurality of primary passages 44 and a plurality of secondary passages 46 between adjacent plates 42a, 42b.
  • the brazing operation hermetically seals an outer peripheral edge of the plates 42a, 42b.
  • the actual design of the plates 42a, 42b may vary to provide an infinite number of configurations with any number of passes and flow patterns, such as including ridges for example.
  • the patterns may be formed such as by stamping, etching, engraving, extruding, molding and embossing for example.
  • the heat exchanger 40 is shown having a first fluid inlet manifold 48, a first fluid outlet manifold 50, a second fluid inlet manifold 52, and a second fluid outlet manifold 54.
  • Each plate 42a, 42b includes a first fluid supply opening 48a, 48b, a first fluid return opening 50a, 50b a second fluid supply opening 52a, 52b and a second fluid return opening 54a, 54b, respectively.
  • a seal (not shown) may surround a portion of the manifold 48, 50, 52, and 54 adjacent a flow passage to form the openings 48a, 48b, 50a, 50b, 52a, 52b, 54a, 54b.
  • FIG. 2 Although the plurality of manifolds 48, 50, 52, and 54 illustrated in FIG. 2 are shown as being substantially encased by a portion of the plates 42a, 42b, other configurations where only a portion of one or more of the manifolds 48, 50, 52, and 54 is received within plates 42a, 42b (FIG. 2a) or where the manifolds 48, 50, 52, and 54 are separate from but arranged in a fluid communication with an edge of the plates 42a, 42b are within the scope of the disclosure FIG. 2b).
  • a portion of one of the manifolds 48, 50, 52, and 54 may be arranged in contact with an inner edge of one of the plurality of plates 42, and arranged in contact with an outer edge of another of the plurality of plates 42.
  • the manifolds 48, 50, 52, and 54 comprise
  • manifolds having other configurations, such as a semi-circular, semi- elliptical, square, rectangular, or other cross-section for example, are within the scope of the present disclosure.
  • the manifolds can extend from opposite end plates of the heat exchanger 40.
  • a relatively cool refrigerant enters the heat exchanger 40 through the first fluid supply openings 48a, 48b. Openings 48a, deliver the refrigerant to passages 44, which convey refrigerant in a zig-zag or other configuration between adjacent plates 42a, 42b to refrigerant return openings 50a, 50b. Openings 50a and 50b then direct the refrigerant to outlet manifold 50 to recycle the refrigerant through the system.
  • a second fluid to be cooled enters the heat exchanger 40 through inlet manifold 52 and flows through the openings 52a, 52b.
  • Openings 52b of the heat exchanger 40 deliver the second fluid to passages 46, which convey the second fluid in a zig-zag or other configuration between adjacent plates 42a, 42b to the second fluid return openings 54a, 54b.
  • the refrigerant in the adjacent passages 44 cools the second fluid.
  • openings 54a, 54b direct the chilled second fluid to the second fluid outlet manifold 54, where it is then provided to an environment to be conditioned.
  • FIGS. 3- 6 a longitudinally elongated distributor assembly 70 configured for use within the interior volume of an inlet manifold, such as refrigerant inlet manifold 48 of heat exchanger 40, is illustrated. Although illustrated within a horizontally arranged manifold 48, the distributor assembly 70 may also be used in any or non-horizontal orientation (e.g., a vertical orientation). The distributor assembly 70 extends over at least a portion, if not the entire length of the inlet manifold 52. In addition, the distributor assembly 70 may be centered within the manifold 48, or alternatively, may be off-center, such as skewed towards a wall of the manifold 48 opposite the plates 42a, 42b for example.
  • the distributor assembly 70 includes an insert 72 having a cross-sectional shape including, but not limited to, round, elliptical, and rectangular for example.
  • the size and shape of the insert 72 is generally complementary to the manifold 48.
  • the insert 72 has a plurality of distribution flow paths 74 formed therein such that the refrigerant provided at an inlet of the manifold 52, such as from line 30 of the vapor refrigerant circuit 20 for example, is distributed substantially equally between the flow paths 74.
  • the refrigerant flow paths 74 extend from an internal cavity of the distributor insert 72 to the flow passage 44 formed between adjacent heat exchanger plates 42a, 42b.
  • the distribution flow paths 74 are sized to maintain the velocity of the two-phase mixture (e.g., so as to limit phase separation) and may be any shape such as round, rectangular, oval, or any other shape for example.
  • the distribution flow paths 74 may take any path, such as a helical path, or a linear path with a metered bend for example.
  • each of the plurality of distribution flow paths 74 is formed having an appropriately small diameter, for example between about 0.2 mm and 5 mm, redistribution of the phases of the flow is unlikely to occur because the slip between the velocity of the liquid portion and the vapor portion of the refrigerant is minimized.
  • the plurality of distribution flow paths 74 have equal diameters (excepting for normal manufacturing variation in dies or other manufacturing tools due to imprecision in the tool construction or wear). In another embodiment, the diameter of each flow paths 74 is selected to reduce the variation in flow resistance between different flow circuits of the heat exchanger (to nearly match pressure drop characteristics of each flow path between the manifold inlet to the manifold outlet of the heat exchanger).
  • each of the plurality of distribution flow paths 74 includes a first portion or flow channel 76 extending axially over at least a portion of the length of the insert 72.
  • the axial flow channels 76 may be parallel to and circumferentially spaced about a central axis of the insert 72, such as in an equidistantly spaced configuration for example.
  • the plurality of axial flow channels 76 may vary in length to provide a fluid flow to one or more corresponding passages 44 via refrigerant supply openings 48a, 48b.
  • Variation in the lengths of the axial flow channels 76 may additionally be used to equalize the pressure drop of the fluid, and therefore the flow between the plurality of axial flow channels 76.
  • the plurality of axial flow passages 76 may be substantially identical in length, such as extending over the full length of the insert 72, as shown in FIG. 5 for example.
  • the distribution flow paths 74 additionally include a plurality of axially spaced connecting channels 78, each of which is configured to fiuidly couple at least one of the axial flow channels 76 to a refrigerant supply opening 48a, 48b and one or more of the passages 44 formed between adjacent plates 42a, 42b.
  • At least one connecting channel 78 is arranged in fluid communication with each of the plurality of axial flow channels 76. As shown in FIG. 3, each of the plurality of connecting channels 78 extends radially outward from an axial flow channel 76 to a distribution hole 80 formed in an outer surface 82 of the insert 72. In such embodiments, the connecting channels 78 are at least partially integrally formed with the insert 72.
  • One or more of the plurality of connecting channels 78 may additionally extend at least partially around a circumference of the insert 72.
  • the circumferential portion of the plurality of connecting channels 78 may be integrally formed as a portion of the heat exchanger plates 42a, 42b (FIG. 6).
  • the circumferential portion of the plurality of connecting channels 78 may be formed in one or both of the exterior surface 82 of the insert 72 and an inner surface 49 of the manifold 48.
  • the distributor assembly 70 may additionally include an outer sleeve 84, as shown in FIGS. 4 and 5, arranged in an overlapping configuration with the insert 72 and being configured to define a portion of the connecting channels 78 to retain fluid therein.
  • a distributor assembly 70 having circumferentially extending connecting channels 78 and an outer sleeve 84 is described in more detail in U.S. Patent Publication No. US2014/0345837, filed on May 23, 2013, the entire contents of which are incorporated herein by reference.
  • a plurality of distribution holes 80 may be formed in either the outer surface 82 of the insert 72 or in an outer sleeve 84 positioned about the insert 72 and are fiuidly connected to not only the distribution flow paths 74 but also the openings 48a, 48b connected to passages 44.
  • the plurality of distribution holes 80 may ⁇ be replaced by one or more continuous slots.
  • each distribution hole 80 may be connected to one or more
  • a plurality of distribution holes 80 may be configured to receive a fluid flow from a single connecting channel 78.
  • the distribution holes 80 are arranged along a horizontal axis such that the position of each hole 80 about the circumference of the housing distributor assembly 70 is substantially identical. As a result, the refrigerant flow is delivered to each of the refrigerant supply openings 48a, 48b at the same azimuthal angle. In another embodiment (FIG. 3), the distribution holes 80 are positioned at different circumferential angles relative to one another.
  • the distributor 70 may also include a nozzle or orifice 90 arranged generally upstream from the plurality of axial flow channels 76.
  • the nozzle 90 may be a separate component positioned adjacent an end of the insert 72, or alternatively, may be located within a hollow region of the insert 72.
  • the nozzle 90 is fluidly coupled to line 30 of the vapor refrigerant circuit 20 (FIG. 1) such that substantially all of the refrigerant from the expansion device 26 is configured to flow directly into the insert 72 via the nozzle 90.
  • the nozzle 90 includes an orifice that restricts the cross- sectional area of the fluid inlet path and is configured to increase the velocity of the fluid flowing there through.
  • Increasing the velocity 14 advantageously provides a substantially uniform, homogeneous mixture of fluid 14.
  • the orifice of the nozzle 90 comprises a venturi portion to reduce the pressure drop of the fluid passing there through.
  • the homogenous two-phase refrigerant mixture may be output from the nozzle 90 in a generally conical shape and is supplied to the plurality of distribution flow paths 74 formed in the insert 72 (see FIG. 5).
  • the distributor assembly 70 as disclosed herein is configured to provide more uniform distribution to a plurality of flow passages of a heat exchanger 40, particularly a heat exchanger configured as an evaporator, and even more particularly a brazed plate heat exchanger. This homogenized distribution will result in improved performance over a wider range of flow conditions. As a result, a refrigerant system 20 including the heat exchanger 40 will have an increased coefficient of performance and reduced power consumption.
  • Embodiment 1 A heat exchanger is provided including a plurality of parallel stacked plates defining at least one flow passage there between.
  • a manifold having a generally hollow interior is arranged adjacent the plurality of parallel plates.
  • An opening is disposed between adjacent stacked plates. The opening is configured to fluidly couple the hollow interior of the manifold and the at least one flow passage.
  • a distributor assembly including an insert is disposed at least partially within the hollow interior of the manifold.
  • the insert includes a plurality of circumferentially spaced axial flow channels and a plurality of radial connecting channels arranged in fluid communication with the axial flow channels. The radial flow channels are fluidly coupled to the at least one flow passage via the opening.
  • Embodiment 2 The heat exchanger according to embodiment 1, wherein a portion of the manifold is received within at least one of the plurality of plates.
  • Embodiment 3 The heat exchanger according to either embodiment 1 or 2, wherein the entire manifold is received within the plurality of plates.
  • Embodiment 4 The heat exchanger according to either embodiment 1 or 2, wherein an edge of the manifold is arranged in contact with an outer edge of the plurality of plates.
  • Embodiment 5 The heat exchanger according to any of the preceding embodiments, further comprising a plurality of axially spaced circumferential connecting channels fluidly coupling the radial connecting channels to the at least one flow passage via the opening.
  • Embodiment 6 The heat exchanger according to any of the preceding embodiments, wherein each of the at least one flow passages is arranged in fluid
  • Embodiment 7 The heat exchanger according to any of the preceding embodiments, wherein the opening is defined by at least one of a ridge extending from at least one of the plurality of stacked plates defining the flow passage and a seal surrounding a portion of the manifold adjacent the flow passage fluidly coupled thereto.
  • Embodiment 8 The heat exchanger of any of embodiments 1-6, comprising a seal completely surrounding the manifold adjacent the flow passage fluidly coupled thereto, and wherein the seal comprises an aperture defining the opening.
  • Embodiment 9 The heat exchanger according to any of the preceding embodiments, wherein a fluid within the distributor assembly is supplied to the plurality of axial flow channels substantially equally.
  • Embodiment 10 The heat exchanger according to any of the preceding embodiments, wherein the distributor assembly is configured to supply a fluid to each opening at a substantially identical azimuthal angle.
  • Embodiment 11 The heat exchanger according to any of the preceding embodiments, wherein the distributor assembly is configured to supply a fluid to each opening at a different azimuthal angle.
  • Embodiment 12 The heat exchanger according to any of the preceding embodiments, wherein the distributor assembly further comprises a nozzle arranged upstream from the plurality of axial flow channels, the nozzle being configured to create a
  • Embodiment 13 The distributor according to embodiment 11, wherein the nozzle includes a constriction configured to produce a pressure drop in the fluid.

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

Abstract

La présente invention concerne un échangeur de chaleur comprenant une pluralité de plaques empilées parallèles définissant au moins un passage d'écoulement entre elles. Un collecteur présentant un intérieur généralement creux est disposé de manière adjacente à la pluralité de plaques parallèles. Une ouverture est disposée entre des plaques empilées adjacentes. L'ouverture est configurée de façon à accoupler de manière fluide l'intérieur creux du collecteur et l'au moins un passage d'écoulement. Un ensemble distributeur comprenant un insert est disposé au moins partiellement dans l'intérieur creux du collecteur. L'insert comprend une pluralité de conduits d'écoulement axiaux disposés à distance sur la circonférence et une pluralité de conduits de raccordement radiaux en communication fluidique avec les conduits d'écoulement axiaux. Les conduits d'écoulement radiaux sont en communication fluidique avec l'au moins un passage d'écoulement par l'intermédiaire de l'ouverture.
PCT/US2016/039850 2015-06-29 2016-06-28 Évaporateur distributeur à deux phases WO2017004058A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
ES16739622T ES2822826T3 (es) 2015-06-29 2016-06-28 Evaporador de distribuidor bifásico
EP16739622.5A EP3314191B1 (fr) 2015-06-29 2016-06-28 Évaporateur distributeur à deux phases
CN201680038713.4A CN107850396A (zh) 2015-06-29 2016-06-28 两相分配器蒸发器
US15/580,214 US20180156544A1 (en) 2015-06-29 2016-06-28 Two phase distributor evaporator

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201562186087P 2015-06-29 2015-06-29
US62/186,087 2015-06-29

Publications (1)

Publication Number Publication Date
WO2017004058A1 true WO2017004058A1 (fr) 2017-01-05

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ID=56418605

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2016/039850 WO2017004058A1 (fr) 2015-06-29 2016-06-28 Évaporateur distributeur à deux phases

Country Status (5)

Country Link
US (1) US20180156544A1 (fr)
EP (1) EP3314191B1 (fr)
CN (1) CN107850396A (fr)
ES (1) ES2822826T3 (fr)
WO (1) WO2017004058A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9655281B2 (en) * 2015-06-26 2017-05-16 Seagate Technology Llc Modular cooling system
US11371788B2 (en) * 2018-09-10 2022-06-28 General Electric Company Heat exchangers with a particulate flushing manifold and systems and methods of flushing particulates from a heat exchanger
JP7122469B2 (ja) * 2019-06-05 2022-08-19 株式会社日阪製作所 プレート式熱交換器、及びプレート式熱交換器用の分配器
CN112648867A (zh) * 2020-11-30 2021-04-13 合肥通用机械研究院有限公司 一种强化传热的一体化扩散焊热交换器

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19945978A1 (de) * 1999-09-24 2001-08-30 Univ Stuttgart Lehrstuhl Und I Fluidverteilungsrahmen für Mehrkammerstacks
WO2006043864A1 (fr) * 2004-10-21 2006-04-27 Alfa Laval Corporate Ab Echangeur thermique à plaques et module de plaque
EP2806244A1 (fr) * 2013-05-23 2014-11-26 Hamilton Sundstrand Corporation Ensemble et procédé de distribution d'un échangeur thermique
WO2015023347A1 (fr) * 2013-08-12 2015-02-19 Carrier Corporation Échangeur de chaleur et répartiteur de débit

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IL107850A0 (en) * 1992-12-07 1994-04-12 Multistack Int Ltd Improvements in plate heat exchangers
CN1110682C (zh) * 1996-01-16 2003-06-04 奥里恩机械株式会社 热交换器
US20030010483A1 (en) * 2001-07-13 2003-01-16 Yasuo Ikezaki Plate type heat exchanger
US7331195B2 (en) * 2004-10-01 2008-02-19 Advanced Heat Transfer Llc Refrigerant distribution device and method
US7806171B2 (en) * 2004-11-12 2010-10-05 Carrier Corporation Parallel flow evaporator with spiral inlet manifold
US7967060B2 (en) * 2005-08-18 2011-06-28 Parker-Hannifin Corporation Evaporating heat exchanger
EP2227668B1 (fr) * 2007-11-14 2018-12-26 SWEP International AB Conduite de distribution
CN101509732A (zh) * 2009-03-12 2009-08-19 华南理工大学 一种流量均匀分配的微通道蒸发器
CN101788243B (zh) * 2009-04-03 2011-09-28 三花丹佛斯（杭州）微通道换热器有限公司 用于热交换器的制冷剂分配器和热交换器
CN102384692A (zh) * 2010-09-01 2012-03-21 珠海格力电器股份有限公司 集流管及具有该集流管的换热器
US20160025420A1 (en) * 2014-07-22 2016-01-28 Hamilton Sundstrand Space Systems International, Inc. Flow distributor for heat transfer plate

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19945978A1 (de) * 1999-09-24 2001-08-30 Univ Stuttgart Lehrstuhl Und I Fluidverteilungsrahmen für Mehrkammerstacks
WO2006043864A1 (fr) * 2004-10-21 2006-04-27 Alfa Laval Corporate Ab Echangeur thermique à plaques et module de plaque
EP2806244A1 (fr) * 2013-05-23 2014-11-26 Hamilton Sundstrand Corporation Ensemble et procédé de distribution d'un échangeur thermique
WO2015023347A1 (fr) * 2013-08-12 2015-02-19 Carrier Corporation Échangeur de chaleur et répartiteur de débit

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US20180156544A1 (en) 2018-06-07
ES2822826T3 (es) 2021-05-05
EP3314191A1 (fr) 2018-05-02
EP3314191B1 (fr) 2020-09-30
CN107850396A (zh) 2018-03-27

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