EP2878911B1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
EP2878911B1
EP2878911B1 EP13806526.3A EP13806526A EP2878911B1 EP 2878911 B1 EP2878911 B1 EP 2878911B1 EP 13806526 A EP13806526 A EP 13806526A EP 2878911 B1 EP2878911 B1 EP 2878911B1
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EP
European Patent Office
Prior art keywords
distribution
fluid
channels
heat exchanger
partition wall
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Active
Application number
EP13806526.3A
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German (de)
English (en)
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EP2878911A4 (fr
EP2878911A1 (fr
Inventor
Daisuke Ito
Takashi Okazaki
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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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
    • 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
    • F28F9/0273—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 holes
    • 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
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
    • 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
    • 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

Definitions

  • the present invention relates to a heat exchanger.
  • Plate heat exchangers include a plurality of stacked heat transfer plates each having corrugated projections and depressions formed in a plurality of arrays. First channels and second channels are alternately formed between pairs of the heat transfer plates, respectively. Further, heat is exchanged between a first fluid flowing through a first channel and a second fluid flowing through a second channel.
  • a plate heat exchanger disclosed in Patent Literature 1 is intended to distribute a refrigerant evenly through a distribution tube having a large number of distribution holes, which is provided in a lower space communicating to an inlet side of each of a plurality of refrigerant channels.
  • JP 08-504027 A WO2010005676A2 discloses a heat exchanger includes heat exchange tubes, a manifold, and a distribution insert incorporating orifices that communicate a fluid into the manifold for distribution into the heat exchange tubes .
  • a design characteristic of the distribution insert and another design characteristic of at least one of the distribution insert, the manifold and the heat exchange tubes are employed to determine an essential design relationship.
  • the essential design relationship defines a design parameter, the value of which falls within a determined range of values.
  • US2005132744A1 discloses a flat-tube evaporator and a refrigeration system including a flat-tube evaporator.
  • the flat-tube evaporator can include an inlet manifold, an outlet manifold separated a distance from the inlet manifold, a distributor tube positioned within the inlet manifold and fluidly connected to the common distributor, and a plurality of flat tubes positioned to fluidly connect the inlet manifold and the outlet manifold.
  • the distributor tube can include a plurality of orifices, each of the plurality of orifices positioned to direct the refrigerant into the inlet manifold in a first direction.
  • Each of the plurality of flat tubes can be positioned to direct the refrigerant from the inlet manifold to the outlet manifold in a second direction, the second direction being substantially opposite the first direction.
  • JP2002062082A discloses a heat exchanger for improving heat transfer performance by preventing generation of channeling in gas-liquid two-phase refrigerant in a plate heat-exchanger.
  • Simple provision of the distribution tube having the distribution holes in the lower space communicating to the inlet side of each of the plurality of refrigerant channels may not achieve even distribution of the refrigerant under various conditions of the flow rate of the refrigerant.
  • the even distribution of the refrigerant very probably may not be able to achieve.
  • the heat exchanger functions as an evaporator, a refrigerant in a gas-liquid two phase state is caused to flow into the distribution tube.
  • the refrigerant in the gas phase is caused to flow in the vicinity of a tube axis, whereas the refrigerant in the liquid phase is caused to flow in an annular pattern around the refrigerant in the gas phase. In this manner, the gas-liquid separation state occurs in a radial direction.
  • the refrigerant is caused to flow at a relatively low flow rate or low flow velocity, on the other hand, a large amount of refrigerant in the liquid phase tends to flow toward a deep side of the distribution tube due to an inertial force.
  • a large amount of refrigerant in the liquid phase exists on a lower side of the distribution tube, whereas a large amount of refrigerant in the gas phase exists on an upper side of the distribution tube.
  • a gas-liquid separation state occurs in a vertical direction.
  • the gas-liquid separation state is different between the flow at a high flow rate and the flow at a low flow rate.
  • the refrigerant is difficult to distribute evenly into the plurality of channels.
  • the present invention has been made in view of the above, and it is therefore an object thereof to provide a heat exchanger capable of distributing a heat exchange fluid evenly into a plurality of channels under various conditions of the flow rate of the heat exchange fluid, in particular, even in a case of a flow at a low flow rate.
  • a heat exchanger including: a channel forming section having a plurality of arrayed fluid channels; a distribution path forming section having a distribution path to which inlets of the plurality of arrayed fluid channels communicate; and a cylindrical partition wall provided in the distribution path forming section, the cylindrical partition wall defining an introduction path on an inner side of the cylindrical partition wall, the distribution path being positioned on an outer side of an outer periphery of the cylindrical partition wall, in which the cylindrical partition wall has a plurality of distribution holes each communicating the introduction path and the distribution path to each other, and in which the following expression is satisfied: L/d' ⁇ (d/2) ⁇ 2> ⁇ 2S, where S represents a channel sectional area of the introduction path, d represents a channel diameter of the introduction path, ⁇ represents a sum of areas ( ⁇ ) of the plurality of distribution holes, L represents a length of array of the plurality of distribution holes, and d' represents a
  • the present invention it is possible to distribute the heat exchange fluid evenly into the plurality of channels under the various conditions of the flow rate of the heat exchange fluid, in particular, even in the case of the flow at the low flow rate.
  • FIG. 1 is a perspective view illustrating components of a plate heat exchanger according to this embodiment
  • FIG. 2 is a side view illustrating the plate heat exchanger
  • FIG. 3A to 3D each is a view illustrating plates, which are main components of the plate heat exchanger.
  • a plate heat exchanger 1 includes a front reinforcement side plate 3, a rear reinforcement side plate 5, and a plurality of front heat transfer plates 7 and a plurality of rear heat transfer plates 9, which are stacked between the reinforcement side plates.
  • a first fluid inlet 11 a first fluid outlet 13
  • a second fluid inlet 15 a second fluid outlet 17
  • four through-holes that is, a first fluid advancing hole 19, a first fluid returning hole 21, a second fluid advancing hole 23, and a second fluid returning hole 25 are formed.
  • the plate heat exchanger 1 is used as an evaporator. It is assumed that the first fluid is a refrigerant and the second refrigerant is water. Specifically, as illustrated in FIG. 1 , the refrigerant indicated by the arrow A is caused to flow into the plate heat exchanger 1 through the first fluid inlet 11, then caused to flow through a plurality of the first fluid advancing holes 19 and a plurality of the first fluid returning holes 21, and is caused to flow out of the plate heat exchanger 1 through the first fluid outlet 13.
  • the water indicated by the arrow B is caused to flow into the plate heat exchanger 1 through the second fluid inlet 15, then caused to flow through a plurality of the second fluid advancing holes 23 and a plurality of the second fluid returning holes 25, and is caused to flow out of the plate heat exchanger 1 through the second fluid outlet 17.
  • first channels and second channels are alternately formed between pairs of the front heat transfer plates 7 and the rear heat transfer plates 9, respectively. Therefore, the refrigerant serving as the first fluid is supplied to the plurality of first channels in a distributed manner while flowing in a lower space including the plurality of first fluid advancing holes 19 (in a strict sense, flowing out through a large number of distribution holes of a distribution tube as described later), and is caused to flow upward in a meandering manner as indicated by the arrow A1. Then, the refrigerant is collected in an upper space including the plurality of first fluid returning holes 21, and is caused to flow out through the first fluid outlet 13.
  • the water serving as the second fluid is supplied to the plurality of second channels in a distributed manner while flowing in a lower space including the plurality of second fluid advancing holes 23, and is caused to flow upward in a meandering manner as indicated by the arrow B1. Then, the water is collected in an upper space including the plurality of second fluid returning holes 25, and is caused to flow out through the second fluid outlet 17.
  • each of the front heat transfer plate 7 and the rear heat transfer plate 9 has corrugated projections and depressions formed in a plurality of arrays, and the first channel and the second channel are formed by such projections and depressions 27.
  • the heat exchanger of the present invention includes a channel forming section, a distribution path forming section, and a cylindrical partition wall. Now, the channel forming section, the distribution path forming section, and the cylindrical partition wall are described.
  • FIG. 4 is a view illustrating a region in the vicinity of the first fluid inlet of the above-mentioned plate heat exchanger
  • FIG. 5 is a sectional view taken along the line V-V of FIG. 4 .
  • FIG. 5 schematically illustrates the structure for clarity of the description.
  • FIG. 6 is a perspective view illustrating the cylindrical partition wall
  • FIG. 7 is a sectional view taken along the line VII-VII of FIG. 6 .
  • a channel forming section 51 is a section having a plurality of arrayed fluid channels. Regions having an upward flow of the fluid in the front heat transfer plates 7 and the rear heat transfer plates 9 described above function as the channel forming section 51. That is, the plurality of first channels arrayed in a stacking direction of the front heat transfer plates 7 and the rear heat transfer plates 9 and the plurality of second channels arrayed similarly in the stacking direction correspond to the plurality of arrayed fluid channels.
  • a distribution path forming section 53 is a section having a distribution path 57 to which inlets 55 of the plurality of fluid channels communicate. Regions having a lateral flow (flow passing through each of the first fluid advancing holes 19 and the second fluid advancing holes 23) of the fluid in the front heat transfer plates 7 and the rear heat transfer plates 9 function as the distribution path forming section 53.
  • a cylindrical partition wall 59 is provided in the distribution path forming section 53.
  • the cylindrical partition wall 59 corresponds to a cylindrical distribution tube 61 inserted into the plurality of first fluid advancing holes 19 or the plurality of second fluid advancing holes 23.
  • the distribution path 57 is formed into an annular shape on an outer side of an outer periphery of the distribution tube 61.
  • an introduction path 63 defined by an inner surface of the distribution tube 61 is formed on an inner side of the distribution tube 61.
  • a plurality of distribution holes 65 are formed in the distribution tube 61.
  • the plurality of distribution holes 65 each communicate the introduction path 63 and the distribution path 57 to each other.
  • the plurality of distribution holes 65 are arrayed along an extending direction of the distribution tube 61, that is, along the stacking direction of the front heat transfer plates 7 and the rear heat transfer plates 9.
  • all of the plurality of distribution holes 65 are circular through-holes, which are formed at substantially the same size. Further, the plurality of distribution holes 65 are arranged at regular intervals. In addition, as illustrated in FIG. 5 , dimensions h of the fluid channels in an array direction are set equal to each other.
  • the inlets 55 of the plurality of fluid channels communicate to the distribution path 57 at positions above the cylindrical partition wall 59.
  • 60% or more of the plurality of distribution holes 65 are formed in a downward orientation in the cylindrical partition wall 59. That is, assuming that the upper side, on which the inlets 55 of the plurality of fluid channels exist, is 0° with respect to the distribution tube 61, the plurality of distribution holes 65 are formed at 180°-positions on the lower side opposite to the inlets 55.
  • a diameter d' of each of the plurality of distribution holes 65 is set to 40% to 100% of the dimension h of each of the fluid channels in the array direction. Further, the respective related portions are formed so that the following expression is satisfied: L / d ′ ⁇ ⁇ d / 2 ⁇ 2 > ⁇ ⁇ 2 ⁇ S
  • S represents a channel sectional area of the introduction path 63 (in a cross section taken in a direction perpendicular to the array direction of the fluid channels)
  • d represents a channel diameter of the introduction path 63
  • ⁇ represents a sum of areas o of the plurality of distribution holes 65
  • L represents a length of array of the plurality of distribution holes 65 (length between an upstream edge portion of the distribution hole at the end of the upstream side and a downstream edge portion of the distribution hole at the end of the downstream side)
  • d' represents a diameter of each of the distribution holes 65.
  • the first fluid first is caused to flow into the distribution tube 61 serving as the cylindrical partition wall 59 through the first fluid inlet 11, then caused to flow through the introduction path 63, and is caused to flow out of the distribution tube 61 into the distribution path 57 through the plurality of distribution holes 65. Further, the first fluid in the distribution path 57 is caused to flow through the inlets 55 of the respective channels so as to be distributed into the respective fluid channels. Then, flows of the first fluid are caused to flow upward through the respective channels.
  • the relationship between the introduction path and the plurality of distribution holes is set to ⁇ 2S, and thus even distribution of liquid or even distribution of gas and liquid into the respective fluid channels is promoted greatly. That is, a partition wall portion of the distribution tube, which separates the adjacent distribution holes from each other, serves as a resistor so that the pressure distribution of the fluid is equalized and a rectification effect is obtained. As a result, even distribution of the fluid into the respective fluid channels is promoted. Thus, heat is exchanged evenly in the respective channels irrespective of the single phase and the gas-liquid two phases.
  • the first fluid easily forms an annular flow in the distribution tube, or easily forms a homogeneous flow due to the above-mentioned partition wall portion. As a result, even distribution of gas and liquid can be achieved.
  • FIG. 8 is a graph showing a relationship between ⁇ /S and a distribution ratio D.
  • the horizontal axis represents ⁇ /S
  • the vertical axis represents the distribution ratio D.
  • G represents a total flow rate of a fluid of interest
  • G i represents a flow rate of the fluid in each channel
  • n represents the number of channels branched from the distribution path
  • i a number of a channel branched from the distribution path, for indicating a specific position of the channel in an order of from the upstream side toward the downstream side.
  • Y i (G i /G) ⁇ 100. That is, Y i represents a distribution ratio of each flow rate of the fluid with respect to the total flow rate.
  • the change in distribution ratio D is stably suppressed at a low level relative to the change in ⁇ /S. That is, in a range in which ⁇ /S is smaller than 2, the distribution ratio D significantly fluctuates along a curved line relative to the change in ⁇ /S, whereas when ⁇ /S is 2 or more, the change in distribution ratio D is suppressed into a flat change relative to ⁇ /S.
  • the distribution ratio D is significantly high. Further, from the viewpoint of manufacture, it is preferred that the distribution ratio D be set as small as possible. As described above, when ⁇ /S is 2 or more, the fluid can be distributed evenly into the plurality of channels under various conditions of the flow rate of the fluid, in particular, even in the case of the flow at a low flow rate. Note that, in actual use, it is preferred that ⁇ /S be set within a range of from 2 to 3, approximately.
  • FIG. 9 shows advantages of this structure.
  • FIG. 9 is a graph showing the relationship between ⁇ /S and the distribution ratio D similarly to FIG. 8 , and further showing differences caused by the orientation of the distribution holes.
  • the results shown in FIG. 9 reveal that, irrespective of whether the flow rate of the fluid is high, medium, or low, the distribution ratio becomes even lower in the structure in which the distribution holes are formed in the downward orientation (indicated by the dotted lines) than in the structure in which 60% or more of the distribution holes are not formed in the downward orientation (indicated by the solid lines) . In particular, under the condition that the flow rate is lower, it is found that the distribution ratio becomes lower more significantly.
  • the diameter d' of each of the plurality of distribution holes is set to 40% to 100% of the dimension h of each of the fluid channels in the array direction.
  • the resistance of the distribution holes is small, and accordingly there is an advantage in that the even distribution can be maintained even when the flow rate is reduced.
  • the fluid can be distributed evenly into the plurality of channels under various conditions of the flow rate of the fluid.
  • the present invention is also applicable to a refrigeration cycle system including the plate heat exchanger used as an evaporator and a condenser within a refrigeration cycle. Accordingly, it is possible to attain a refrigeration cycle system having excellent heat exchange performance and high reliability.
  • the present invention is not limited to the application to the plate heat exchanger, but is widely applicable to a heat exchanger including a plurality of arrayed heat exchange fluid channels, and a distribution path to which inlets of the fluid channels communicate.
  • the present invention is applicable to a flat-tube heat exchanger.

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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 (6)

  1. Echangeur de chaleur (1) comprenant :
    une section de formation de canal (51) ayant une pluralité de canaux de fluide en réseau ;
    une section de formation de trajectoire de distribution (53) ayant une trajectoire de distribution (57) avec laquelle les entrées (55) de la pluralité de canaux de fluide en réseau communiquent ; et
    une paroi de séparation cylindrique (59) prévue dans la section de formation de trajectoire de distribution (53), la paroi de séparation cylindrique (59) définissant une trajectoire d'introduction (63) sur un côté interne de la paroi de séparation cylindrique (59), la trajectoire de distribution (57) étant positionnée sur un côté externe d'une périphérie externe de la paroi de séparation cylindrique (59),
    la paroi de séparation cylindrique (59) ayant une pluralité de trous de distribution (65) faisant communiquer chacun la trajectoire d'introduction (63) et la trajectoire de distribution (57) entre elles, caractérisé en ce que :
    l'expression suivante est satisfaite : L / d ′ × Π d / 2 ∧ 2 > Σσ ≥ 2 ⁢ S
    Figure imgb0005
     où S représente une surface transversale de canal de la trajectoire d'introduction (63), d représente un diamètre de canal de la trajectoire d'introduction (63), ∑σ représente une somme des surfaces (σ) de la pluralité de trous de distribution (65), L représente une longueur de réseau de la pluralité de trous de distribution (65), et d' représente un diamètre de chacun de la pluralité de trous de distribution (65).
  2. Echangeur de chaleur selon la revendication 1, dans lequel le diamètre (d') de chacun de la pluralité de trous de distribution (65) représente de 40% à 100% d'une dimension (h) de chacun de la pluralité de canaux de fluide en réseau dans une direction de réseau.
  3. Echangeur de chaleur selon la revendication 1 ou 2,
    dans lequel la section de formation de canal (51) comprend une pluralité de plaques de transfert de chaleur (7, 9) empilées, chacune ayant des saillies et des creux formés dans une pluralité de réseaux,
    dans lequel la section de formation de canal (51) définit des premiers canaux et des seconds canaux, qui sont formés de manière alternée entre des paires de la pluralité de plaques de transfert de chaleur (7, 9) empilées,
    dans lequel la section de formation de canal (51) est configurée pour échanger la chaleur entre un premier fluide s'écoulant à travers chacun d'une pluralité de premiers canaux et un second fluide s'écoulant à travers chacun d'une pluralité de second canaux, et
    dans lequel la pluralité de canaux de fluide en réseau comprend la pluralité de premiers canaux.
  4. Echangeur de chaleur selon l'une quelconque des revendications 1 à 3, dans lequel chacun de la pluralité de trous de distribution (65) est formé dans une orientation descendante.
  5. Echangeur de chaleur selon l'une quelconque des revendications 1 à 4, dans lequel la pluralité de trous de distribution (65) sont disposés en réseau le long d'une direction d'extension de la paroi de séparation cylindrique (9).
  6. Système de cycle de réfrigération comprenant l'échangeur de chaleur selon l'une quelconque des revendications 1 à 5.
EP13806526.3A 2012-06-18 2013-06-12 Échangeur de chaleur Active EP2878911B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
PCT/JP2012/065505 WO2013190617A1 (fr) 2012-06-18 2012-06-18 Échangeur de chaleur
PCT/JP2013/066215 WO2013191056A1 (fr) 2012-06-18 2013-06-12 Échangeur de chaleur

Publications (3)

Publication Number Publication Date
EP2878911A1 EP2878911A1 (fr) 2015-06-03
EP2878911A4 EP2878911A4 (fr) 2016-06-01
EP2878911B1 true EP2878911B1 (fr) 2019-08-28

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US (1) US20150168081A1 (fr)
EP (1) EP2878911B1 (fr)
JP (1) JPWO2013191056A1 (fr)
CN (2) CN104380027A (fr)
WO (2) WO2013190617A1 (fr)

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Also Published As

Publication number Publication date
EP2878911A4 (fr) 2016-06-01
JPWO2013191056A1 (ja) 2016-05-26
WO2013191056A1 (fr) 2013-12-27
WO2013190617A1 (fr) 2013-12-27
EP2878911A1 (fr) 2015-06-03
CN104380027A (zh) 2015-02-25
CN203479101U (zh) 2014-03-12
US20150168081A1 (en) 2015-06-18

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