EP3314191B1 - Verdampfer mit zweiphasigem verteiler - Google Patents

Verdampfer mit zweiphasigem verteiler Download PDF

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Publication number
EP3314191B1
EP3314191B1 EP16739622.5A EP16739622A EP3314191B1 EP 3314191 B1 EP3314191 B1 EP 3314191B1 EP 16739622 A EP16739622 A EP 16739622A EP 3314191 B1 EP3314191 B1 EP 3314191B1
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EP
European Patent Office
Prior art keywords
heat exchanger
manifold
fluid
opening
exchanger according
Prior art date
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Active
Application number
EP16739622.5A
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English (en)
French (fr)
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EP3314191A1 (de
Inventor
Abbas A. Alahyari
Richard Rusich
Thomas D. Radcliff
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Carrier Corp
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Carrier Corp
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Publication of EP3314191A1 publication Critical patent/EP3314191A1/de
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Publication of EP3314191B1 publication Critical patent/EP3314191B1/de
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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
    • 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
    • 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
    • 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
    • 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.
  • WO 2006/043864 discloses a plate heat exchanger for two phase refrigerant having the features in the preamble of claim 1.
  • DE 199 45 978 A1 discloses a plate heat exchanger.
  • a heat exchanger is provided.
  • the heat exchanger is for two-phase refrigerant and includes 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 distribution flow paths comprising 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.
  • the distribution flow paths are sized to maintain the velocity of the two-phase fluid so as to limit separation.
  • a portion of the manifold may be received within at least one of the plurality of plates.
  • the entire manifold may be received within the plurality of plates.
  • An edge of the manifold may be arranged in contact with an outer edge of the plurality of plates.
  • Each of the at least one flow passages may be arranged in fluid communication with the hollow interior of the manifold via exactly one opening.
  • the opening may be 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 seal may completely surrounding the manifold adjacent the flow passage fluidly coupled thereto.
  • the seal may comprise an aperture defining the opening.
  • a fluid within the distributor assembly may be supplied to the plurality of axial flow channels substantially equally.
  • the distributor assembly may be configured to supply a fluid to each opening at a substantially identical azimuthal angle.
  • the distributor assembly may be configured to supply a fluid to each opening at a different azimuthal angle.
  • the distributor assembly may further comprise 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 may include a constriction configured to produce a pressure drop in the fluid.
  • 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 downstream into a condenser 24.
  • the refrigerant passes through the expansion device 26 into an inlet refrigerant pipe 30 leading to the evaporator 28.
  • the refrigerant is returned to the compressor 22 to complete the closed-loop refrigerant circuit.
  • 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 microchannel 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 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 longitudinally elongated, generally hollow, closed end cylinders having a circular cross-section.
  • 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 fluidly 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. Accordingly, 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 fluidly 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 corresponding connecting channels 78.
  • 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.

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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)

Claims (13)

  1. Wärmetauscher für ein Zwei-Phasen-Kältemittel, wobei der Wärmetauscher Folgendes umfasst:
    eine Vielzahl von parallel gestapelten Platten (42a, 42b), die mindestens einen Strömungskanal (44, 46) zwischen sich definieren;
    einen Verteiler (48, 50, 52, 54), der an die Vielzahl von parallelen Platten angrenzend angeordnet ist, wobei der Verteiler einen im Wesentlichen hohlen Innenraum aufweist;
    eine Öffnung (48a, 48b, 50a, 50b, 52a, 52b, 54a, 54b), die zwischen angrenzenden, gestapelten Platten angeordnet ist, wobei die Öffnung dazu konfiguriert ist, den hohlen Innenraum des Verteilers fluidisch und den mindestens einen Strömungskanal zu koppeln; und
    eine Verteilerbaugruppe (70), die ein Einsatzstück (72) beinhaltet, das mindestens teilweise innerhalb des hohlen Innenraums des Verteilers angeordnet ist; dadurch gekennzeichnet, dass das Einsatzstück Verteilungsströmungspfade (74) beinhaltet, die eine Vielzahl von in Umfangsrichtung beabstandeten, axialen Strömungskanälen (76) und eine Vielzahl von radialen Verbindungskanälen (78) umfassen, die in Fluidverbindung mit den axialen Strömungskanälen angeordnet sind, wobei die radialen Strömungskanäle über die Öffnung fluidisch mit dem mindestens einen Strömungskanal gekoppelt sind; wobei die Verteilungsströmungspfade so dimensioniert sind, dass die Geschwindigkeit des Zwei-Phasen-Kältemittels beibehalten wird, um eine Separation zu begrenzen.
  2. Wärmetauscher nach Anspruch 1, wobei ein Teil des Verteilers (48, 50, 52, 54) innerhalb von mindestens einer aus der Vielzahl von Platten (42a, 42b) aufgenommen ist.
  3. Wärmetauscher nach Anspruch 1 oder Anspruch 2, wobei der gesamte Verteiler (48, 50, 52, 54) innerhalb der Vielzahl von Platten (42a, 42b) aufgenommen ist.
  4. Wärmetauscher nach Anspruch 1 oder Anspruch 2, wobei eine Kante des Verteilers (48, 50, 52, 54) in Kontakt mit einer äußeren Kante von der Vielzahl von Platten (42a, 42b) angeordnet ist.
  5. Wärmetauscher nach einem der vorhergehenden Ansprüche, ferner eine Vielzahl von axial beabstandeten, in Umfangsrichtung verlaufenden Verbindungskanälen (78) umfassend, die die radialen Verbindungskanäle (78) über die Öffnung (48a, 48b, 50a, 50b, 52a, 52b, 54a, 54b) fluidisch mit dem mindestens einen Strömungskanal (42a, 42b) koppeln.
  6. Wärmetauscher nach einem der vorhergehenden Ansprüche, wobei jeder des mindestens einen Strömungskanals (44, 46) über exakt eine Öffnung (48a, 48b, 50a, 50b, 52a, 52b, 54a, 54b) in Fluidverbindung mit dem hohlen Innenraum des Verteilers (48, 50, 52, 54) angeordnet ist.
  7. Wärmetauscher nach einem der vorhergehenden Ansprüche, wobei die Öffnung (48a, 48b, 50a, 50b, 52a, 52b, 54a, 54b) durch mindestens eines von Folgendem definiert wird: einen Grat, der sich von mindestens einer aus der Vielzahl von gestapelten Platten (42a, 42b) erstreckt, die den Strömungskanal (44, 46) definieren, und eine Dichtung, die einen Teil des Verteilers (48, 50, 52, 54) umgibt, der an den Strömungskanal angrenzt, der fluidisch damit gekoppelt ist.
  8. Wärmetauscher nach einem der Ansprüche 1-6, eine Dichtung umfassend, die den Verteiler (48, 50, 52, 54) vollständig umgibt, der an den Strömungskanal (44, 46) angrenzt, der fluidisch damit gekoppelt ist, und wobei die Dichtung eine Apertur umfasst, die die Öffnung (48a, 48b, 50a, 50b, 52a, 52b, 54a, 54b) definiert.
  9. Wärmetauscher nach einem der vorhergehenden Ansprüche, wobei der Vielzahl von axialen Strömungskanälen (76) im Wesentlichen gleichmäßig ein Fluid innerhalb der Verteilerbaugruppe (70) bereitgestellt wird.
  10. Wärmetauscher nach einem der vorhergehenden Ansprüche, wobei die Verteilerbaugruppe (70) dazu konfiguriert ist, jeder Öffnung (48a, 48b, 50a, 50b, 52a, 52b, 54a, 54b) ein Fluid in einem im Wesentlichen identischen Seitenwinkel bereitzustellen.
  11. Wärmetauscher nach einem der vorhergehenden Ansprüche, wobei die Verteilerbaugruppe (70) dazu konfiguriert ist, jeder Öffnung (48a, 48b, 50a, 50b, 52a, 52b, 54a, 54b) ein Fluid in einem unterschiedlichen Seitenwinkel bereitzustellen.
  12. Wärmetauscher nach einem der vorhergehenden Ansprüche, wobei die Verteilerbaugruppe (70) ferner eine Düse (90) umfasst, die stromaufwärts von der Vielzahl von axialen Strömungskanälen (76) angeordnet ist, wobei die Düse dazu konfiguriert ist, eine homogene Verteilung eines Fluids zu erzeugen.
  13. Wärmetauscher nach Anspruch 12, wobei die Düse (90) eine Verengung beinhaltet, die dazu konfiguriert ist, einen Druckabfall in dem Fluid zu erzeugen.
EP16739622.5A 2015-06-29 2016-06-28 Verdampfer mit zweiphasigem verteiler Active EP3314191B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201562186087P 2015-06-29 2015-06-29
PCT/US2016/039850 WO2017004058A1 (en) 2015-06-29 2016-06-28 Two phase distributor evaporator

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EP3314191A1 EP3314191A1 (de) 2018-05-02
EP3314191B1 true EP3314191B1 (de) 2020-09-30

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US (1) US20180156544A1 (de)
EP (1) EP3314191B1 (de)
CN (1) CN107850396A (de)
ES (1) ES2822826T3 (de)
WO (1) WO2017004058A1 (de)

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WO2020246412A1 (ja) * 2019-06-05 2020-12-10 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
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US20180156544A1 (en) 2018-06-07
ES2822826T3 (es) 2021-05-05
WO2017004058A1 (en) 2017-01-05
CN107850396A (zh) 2018-03-27
EP3314191A1 (de) 2018-05-02

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