EP2410278B1 - Échangeur thermique de type à plaques et dispositif de conditionnement d'air et de réfrigération - Google Patents

Échangeur thermique de type à plaques et dispositif de conditionnement d'air et de réfrigération Download PDF

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Publication number
EP2410278B1
EP2410278B1 EP09841919.5A EP09841919A EP2410278B1 EP 2410278 B1 EP2410278 B1 EP 2410278B1 EP 09841919 A EP09841919 A EP 09841919A EP 2410278 B1 EP2410278 B1 EP 2410278B1
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EP
European Patent Office
Prior art keywords
hole
plate
inlet
inlet hole
outlet
Prior art date
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EP09841919.5A
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German (de)
English (en)
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EP2410278A1 (fr
EP2410278A4 (fr
Inventor
Daisuke Ito
Satoru Yanachi
Takehiro Hayashi
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of EP2410278A4 publication Critical patent/EP2410278A4/fr
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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
    • F28D9/0031—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
    • 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

Definitions

  • This invention relates to a plate heat exchanger as defined in the preamble of claim 1.
  • WO 2005/098334 A1 discloses such a plate heat exchanger.
  • Patent Document 1 discusses a plate heat exchanger in which a fluid inlet hole and a fluid outlet hole are elliptically shaped. Patent Document 1 also discusses a plate heat exchanger in which the diameter of a fluid inlet hole and the diameter of a fluid outlet hole are identical in size.
  • Patent Document 2 discusses a plate heat exchanger in which the diameter of a fluid inlet hole and the diameter of a fluid outlet hole are different in size. Patent Document 2 also discusses a plate heat exchanger which includes reinforcement members for a fluid inlet hole and a fluid outlet hole, thereby providing enhanced strength.
  • This invention aims to enhance the strength of a plate heat exchanger while maintaining the heat exchange capability of the plate heat exchanger, for example.
  • a plate heat exchanger according to this invention is, defined in claim 1.
  • the plate heat exchanger according to this invention provides enhanced strength.
  • Figs. 1 to 6 are diagrams describing a plate heat exchanger 20 according to a first embodiment.
  • Fig. 1 is a side view of the plate heat exchanger 20.
  • Fig. 2 is a front view of a reinforcement side plate 1.
  • Fig. 3 is a front view of a second plate 2.
  • Fig. 4 is a front view of a first plate 3.
  • Fig. 5 is a front view of a reinforcement side plate 4.
  • Fig. 6 is an exploded perspective view of the plate heat exchanger 20.
  • the plate heat exchanger 20 includes a plurality of stacked plates 2 and 3.
  • the plate heat exchanger 20 also includes the reinforcement side plates 1 and 4 stacked at the forefront (an A side in Fig. 1 ) and the rear end (a B side in Fig. 1 ), respectively.
  • each of the plates 2 and 3 is formed as a plate of an approximately rectangular shape.
  • Each of the plates 2 and 3 includes a first inlet hole 5 near one edge (an upper side) in a long-side (longitudinal) direction of the approximately rectangular shape.
  • Each of the plates 2 and 3 includes a first outlet hole 6 near another edge (a lower side) in the longitudinal direction opposite from the first inlet hole 5.
  • Each of the plates 2 and 3 includes a second inlet hole 7 near the same edge (the lower side) in the longitudinal direction as the first outlet hole 6.
  • Each of the plates 2 and 3 includes a second outlet hole 8 near the same edge (the upper side) in the longitudinal direction as the first inlet hole 5.
  • Each of the plates 2 and 3 includes the first inlet hole 5 and the first outlet hole 6 near the same edge (a left side) in a short-side (lateral) direction of the approximately rectangular shape.
  • Each of the plates 2 and 3 includes the second inlet hole 7 and the second outlet hole 8 near another edge (a right side) in the lateral direction opposite from the first inlet hole 5 and the first outlet hole 6.
  • first inlet hole 5, the first outlet hole 6, the second inlet hole 7, and the second outlet hole 8 are provided at four corners of each of the plates 2 and 3.
  • the first inlet hole 5 and the first outlet hole 6 will be referred to as first inlet and outlet holes.
  • the second inlet hole 7 and the second outlet hole 8 will be referred to as second inlet and outlet holes.
  • the reinforcement side plates 1 and 4 are also formed as plates in an approximately rectangular shape, as shown in Figs. 2 and 5 .
  • the reinforcement side plate 1 stacked at the forefront includes the first inlet hole 5 (a first inlet duct), the first outlet hole 6 (a first outlet duct), the second inlet hole 7 (a second inlet duct), and the second outlet hole 8 (a second outlet duct) at the same positions as in the plates 2 and 3.
  • the reinforcement side plate 4 stacked at the rear end does not include the first inlet hole 5, the first outlet hole 6, the second inlet hole 7, and the second outlet hole 8.
  • the positions of the first inlet hole 5, the first outlet hole 6, the second inlet hole 7, and the second outlet hole 8 are indicated by dashed lines, but these holes are not actually present in the reinforcement side plate 4.
  • Each of the plates 2 and 3 and the reinforcement side plate 1 are stacked such that the respective first inlet holes 5, first outlet holes 6, second inlet holes 7, and second outlet holes 8 are aligned with one another.
  • the second plate 2 and the first plate 3 are stacked alternately.
  • the plates 2 and 3 and the reinforcement side plates 1 and 4 are formed approximately identically in an approximately rectangular shape.
  • each of the plates 2 and 3 has a plurality of V-shaped concave portions and convex portions (corrugations 9) arranged in longitudinal arrays.
  • the corrugations 9 have ends 13 at both sides in the lateral direction.
  • the corrugations 9 are formed in the shape of a V having turning points 12, each turning point 12 being longitudinally misaligned with respect to the corresponding ends 13 at both sides.
  • the pitch (width) of the corrugations 9 is indicated as W in Fig. 4 .
  • the corrugations 9 are provided such that the direction thereof is reversed between the second plate 2 and the first plate 3.
  • the corrugations 9 are formed in the shape of a V with each turning point 12 positioned lower than the corresponding ends 13 at both sides.
  • the corrugations 9 are formed in the shape of a V (a reversed V) with each turning point 12 positioned higher than the corresponding ends 13 at both sides.
  • the V-shaped corrugations 9 are formed in the plates 2 and 3 by reversing the direction of the V shape between the plates 2 and 3.
  • flow paths with high heat transfer efficiency are defined between the plates 2 and 3. That is, as shown in Fig. 6 , a first flow path is defined between the back surface of the second plate 2 and the front surface of the first plate 3 such that a first fluid entered from the first inlet hole 5 flows to the first outlet hole 6.
  • a second flow path is defined between the back surface of the first plate 3 and the front surface of the second plate 2 such that a second fluid entered from the second inlet hole 7 flows to the second outlet hole 8.
  • the first fluid flowing through the first flow path is heat-exchanged with the second fluid flowing through the second flow path via the plates 2 and 3.
  • Fig. 7 is a diagram showing dimensions of the plates 2 and 3 of the plate heat exchanger 20.
  • a length L1 indicates a length of the plates 2 and 3 in the longitudinal direction.
  • a length L2 indicates a length of the plates 2 and 3 in the lateral direction.
  • a length L3 indicates a length from the first inlet hole 5 to a plate edge proximate to the first inlet hole 5 in the lateral direction.
  • a length 4 indicates a length from the first outlet hole 6 to a plate edge proximate to the first outlet hole 6 in the lateral direction.
  • a length L5 indicates a length from the second inlet hole 7 to a plate edge proximate to the second inlet hole 7 in the lateral direction.
  • a length L6 indicates a length from the second outlet hole 8 to a plate edge proximate to the second outlet hole 8 in the lateral direction.
  • Fig. 8 is a diagram depicting the relationship between stress and the ratio (length ratio) of the longitudinal length and the lateral length of the plates 2 and 3.
  • the horizontal axis in Fig. 8 depicts the ratio (length ratio) between the longitudinal length and the lateral length of the plates 2 and 3. That is, the horizontal axis in Fig. 8 depicts the ratio of the longitudinal length L1 of the plates 2 and 3 to the lateral length L2 of the plates 2 and 3.
  • the vertical axis in Fig. 8 depicts the stress applied to the edges (periphery) of the plates 2 and 3.
  • stress is expressed as a stress ratio.
  • the reference value of the stress ratio is a value indicated by the second point from the right, namely, a point P, in Fig. 8 .
  • Each point in Fig. 8 represents a calculated value of a stress ratio relative to a length ratio.
  • the line in Fig. 8 represents values calculated from each point by using a least-square method.
  • the length L2 should preferably be as short as possible relative to the length L1. Specifically, the length L2 should preferably be shortened such that the length L1 is 4 or more times the length L2. However, due to limitations on the manufacture of the plate heat exchanger 20, the length L2 cannot be shortened significantly. Accordingly, the length L2 should preferably be shortened such that the length L1 is approximately from 4 to 6.5 times the length L2.
  • the lengths L3, L4, L5, and L6 should preferably be set to not more than 6 percent of the lateral length L2 of the plates 2 and 3.
  • the lengths L3, L4, L5, and L6 may be set to not more than 5.6 mm, irrespective of the lateral length L2 of the plates 2 and 3.
  • the lengths L3, L4, L5, and L6 cannot be shortened significantly.
  • the lengths L3, L4, L5, and L6 should preferably be set to between not less than 3 percent and not more than 6 percent of the lateral length L2 of the plates 2 and 3.
  • the lengths L3, L4, L5, and L6 should preferably be set to not less than 3 mm and not more than 5.6 mm
  • Fig. 9 is a diagram depicting the relationship between the ratio of the longitudinal length and the lateral length of the plates 2 and 3 and the weight of the plate heat exchanger 20. Specifically, Fig. 9 depicts the extent to which the weight of the plate heat exchanger 20 can be reduced by shortening the lateral length of the plates 2 and 3 without changing the longitudinal length of the plates 2 and 3.
  • the horizontal axis in Fig. 9 depicts the ratio (length ratio) of the longitudinal length and the lateral length of the plates 2 and 3.
  • the vertical axis in Fig. 9 depicts the reduction ratio of the weight of the plate heat exchanger 20.
  • the reduction ratio of the weight of the plate heat exchanger 20 is a value calculated based on the weight of the plate heat exchanger 20 manufactured with the length ratio selected as the reference value of the stress ratio in Fig. 8 (the value indicated by the second point from the right, namely, the point P).
  • the length L2 shorter By making the length L2 shorter, the size of the plate heat exchanger 20 is reduced, so that the weight of the plate heat exchanger 20 can be reduced.
  • the length L2 shorter not only the weight can be reduced due to the reduced overall size, but also the thickness of the plates 2 and 3 and the thickness of the reinforcement side plates 1 and 4 can be reduced, so that the weight can be reduced further. That is, by making the length L2 shorter, the strength of the plate heat exchanger 20 is enhanced. Accordingly, the thickness of the plates 2 and 3 and the thickness of the reinforcement side plates 1 and 4 can be reduced, so that the weight of the plate heat exchanger 20 can be reduced.
  • the weight of the plate heat exchanger 20 can be reduced more than by the weight reduction due to reduction in overall size.
  • the lateral length L2 of the plates 2 and 3 is shortened relative to the longitudinal length L1 of the plates 2 and 3, so that the strength of the plate heat exchanger 20 is enhanced.
  • the lengths between the inlet or outlet holes 5, 6, 7, and 8 and the plate edge are also shortened, so that the strength of the plate heat exchanger 20 is enhanced.
  • the weight of the plate heat exchanger 20 can be reduced.
  • a fluid entered from the first inlet hole 5 or the second inlet hole 7 is also facilitated to spread in the lateral direction.
  • the enhanced strength of the plate heat exchanger 20 also eliminates the need to provide reinforcement members around the inlet holes (the first inlet hole 5, the second inlet hole 7).
  • press working of the plates 2 and 3 is simplified. Accordingly, the cost of manufacturing the plate heat exchanger 20 can be reduced. Variation in height of the corrugations 9 can also be reduced. That is, the plate heat exchanger 20 of stable quality can be manufactured.
  • the plate heat exchanger 20 according to the first embodiment is effective not only when the fluid is water but also for other types of fluid which have a tendency to drift due to a small density and a high pressure loss (e.g., a hydrocarbon refrigerant or a low-GWP refrigerant). With a chlorofluorocarbon. refrigerant, effectiveness is also provided for preventing accumulation of refrigerant oil in the heat exchanger. This permits power consumption to be reduced in an apparatus using the plate heat exchanger 20 according to the first embodiment.
  • the plate heat exchanger 20 in which the diameters of the first inlet and outlet holes are smaller than the diameters of the second inlet and outlet holes. That is, in the second embodiment, there will be described the plate heat exchanger 20 in which the opening areas of the first inlet and outlet holes are smaller than the opening areas of the second inlet and outlet holes.
  • Fig. 10 is a diagram showing the plates 2 and 3 in which the diameters of the first inlet and outlet holes are smaller than the diameters of the second inlet and outlet holes.
  • the plate heat exchanger 20 when used to exchange heat between a liquid such as water and a refrigerant such as chlorofluorocarbon, there is a risk that the plates may wear out (become thinner) due to erosion at an inlet hole for the liquid (the second inlet hole 7 here). For this reason, the diameters of the inlet and outlet holes for the liquid (the second inlet hole 7, the second outlet hole 8) need to be sufficiently large. However, there is no need to make the diameters of the inlet and outlet holes for the refrigerant (the first inlet hole 5, the first outlet hole 6) as large as the diameters of the inlet and outlet holes for the liquid (the second inlet hole 7, the second outlet hole 8).
  • the diameters of the first inlet hole 5 and the first outlet hole 6 may be smaller than the diameters of the second inlet hole 7 and the second outlet hole 8.
  • the lateral length of the plates 2 and 3 can be correspondingly shortened.
  • the strength of the plate heat exchanger 20 is enhanced, and the weight of the plate heat exchanger 20 can be reduced, as described in the first embodiment.
  • the refrigerant is not limited to chlorofluorocarbon, and may also be a hydrocarbon refrigerant or a low-GWP refrigerant.
  • a CO2 refrigerant requires the plate heat exchanger 20 to be strong due to a high working pressure.
  • the CO2 refrigerant is especially effective to configure the inlet and outlet holes for the refrigerant to be smaller than the inlet and outlet holes for the liquid. Since the CO2 refrigerant has a higher density and a smaller pressure loss compared to the chlorofluorocarbon refrigerant, the diameters of the first inlet hole 5 and the first outlet hole 6 can be further reduced.
  • Fig. 11 is a diagram showing the plate heat exchanger 20 configured such that the nearer each of the plates 2 and 3 is to the reinforcement side plate 1, the smaller the diameter of the first inlet hole 5.
  • the plate heat exchanger 20 shown in Fig. 11 is configured such that not only the diameters of the first inlet and outlet holes are smaller than the diameters of the second inlet and outlet holes, but also the nearer each of the stacked plates 2 and 3 is to the reinforcement side plate 1, the smaller the diameter of the first inlet hole 5. That is, the nearer each of the stacked plates 2 and 3 is to the reinforcement side plate 1 than to the reinforcement side plate 4 , the smaller the diameter of the first inlet hole 5. In other words, the nearer each of the stacked plates 2 and 3 is to the entrance side of the first fluid, the smaller the diameter of the first inlet hole 5. Specifically, the first inlet hole 5 is extremely small like a fine nozzle in the plates 2 and 3 stacked near the reinforcement side plate 1.
  • the first inlet hole 5 is extremely small in the plates 2 and 3 stacked near the reinforcement side plate 1, the first fluid can flow at high speed even when a large number of the plates 2 and 3 are stacked. This also facilitates distribution of the first fluid toward the plates 2 and 3 stacked near the reinforcement side plate 4.
  • each of the stacked plates 2 and 3 is to the reinforcement side plate 4, the larger the diameter of the first inlet hole 5 is. This facilitates an even distribution of the first fluid through the first flow path defined by each pair of the plates 2 and 3.
  • the plate heat exchanger 20 in which the inlet and outlet holes are positioned not only nearer to the edges of each plate in the lateral direction, but also nearer to the edges of each plate in the longitudinal direction. That is, in the third embodiment, there will be described the plate heat exchanger 20 in which the inlet and outlet holes are positioned nearer to the four corners of the plates 2 and 3.
  • Fig. 12 is a diagram showing dimensions of the plates 2 and 3 in which the inlet and outlet holes are positioned nearer to the four corners of each plate.
  • a length L7 indicates a length from the first inlet hole 5 to a plate edge proximate to the first inlet hole 5 in the longitudinal direction.
  • a length L8 indicates a length from the first outlet hole 6 to a plate edge proximate to the first outlet hole 6 in the longitudinal direction.
  • a length L9 indicates a length from the second inlet hole 7 to a plate edge proximate to the second inlet hole 7 in the longitudinal direction.
  • a length L10 indicates a length from the second outlet hole 8 to a plate edge proximate to the second outlet hole 8 in the longitudinal direction.
  • the lengths L7, L8, L9, and L10 are approximately equivalent to the lengths L3, L4, L5, and L6 shown in Fig. 7 , respectively. In this way, by making the lengths L7, L8, L9, and L10 shorter, the stress applied to the periphery of each plate can be further reduced.
  • the diameters of the first inlet and outlet holes are smaller than the diameters of the second inlet and outlet holes. Accordingly, the centers of the first inlet and outlet holes are positioned nearer to the corners of the plates 2 and 3 relative to the centers of the second inlet and outlet holes.
  • the distance from the first inlet hole 5 to the first outlet hole 6 is increased. That is, the length of the first flow path is increased. Accordingly, the heat transfer area is increased, and the heat exchange capability of the plate heat exchanger 20 is enhanced.
  • Fig. 13 is a diagram describing a flow of the first fluid on the first plate 3 in which the inlet and outlet holes are positioned nearer to the four corners of the plate.
  • Fig. 13 only applies to the first plate 3 instead of the plates 2 and 3. This is because a sealing portion 11 is shown in Fig. 13 . That is, the sealing portion 11 is provided at different locations between the second plate 2 and the first plate 3.
  • an entrance region 10 for the first flow path can be provided near the first inlet hole 5.
  • the entrance region 10 is a narrow region between the plate edge and the sealing portion 11. This means that the width of the entrance region 10 (a length L11 from the plate edge to the sealing portion 11) is narrower than the lateral width (the length L2) of the first plate 3.
  • the first fluid entered from the first inlet hole 5 passes through the narrow entrance region 10, then spreads in the lateral direction of the plate heat exchanger 20, and flows to the first outlet hole 6.
  • the sealing portion 11 is a wall which prevents the first fluid entered from the first inlet hole 5 from flowing to the second outlet hole 8.
  • the sealing portion 11 is formed as a protrusion raised in the stacking direction of the plates 2 and 3.
  • the sealing portion 11 is normally provided around the second outlet hole 8 in a circular shape.
  • the sealing portion 11 is provided here, starting from near the edge (the upper side) in the longitudinal direction where the first inlet hole 5 and the second outlet hole 8 are located and extending toward the edge (the lower side) in the longitudinal direction where the second inlet hole 7 and the second outlet hole 8 are located in such a manner as to gradually curve toward the edge (the right side) in the lateral direction near the second outlet hole 8.
  • the sealing portion 11 is formed to gradually curve to the right in a downward direction.
  • the sealing portion 11 facilitates the first fluid which has flowed through the entrance region 10 to spread toward the edge (the right side) in the lateral direction near the second outlet hole 8. That is, the entrance region 10 and the sealing portion 11 provide a guiding effect for guiding the first fluid toward the edge (the right side) in the lateral direction near the second outlet hole 8.
  • This guiding effect can prevent the first fluid from stagnating around the sealing portion 11 or near the periphery of the plates 2 and 3, thereby enhancing the heat exchange capability.
  • This guiding effect can also reduce the pressure loss of the first fluid. That is, the plate heat exchanger 20 with enhanced performance can be provided.
  • the sealing portion 11 When the sealing portion 11 is provided around the second outlet hole 8 in a circular shape, as is normally done, it is necessary to provide a distribution facilitating member around the first inlet hole 5 so as to prevent the first fluid from drifting.
  • the distribution facilitating member is formed, for example, in a complex shape such as a radial shape.
  • the plate heat exchanger 20 according to the third embodiment simply includes the sealing portion 11 which is curved, and thus is simple to manufacture. For this reason, the plate heat exchanger 20 according to the third embodiment is highly suitable for mass production.
  • Fig. 14 is a diagram describing the corrugations 9 in the first plate 3 in which the inlet and outlet holes are positioned nearer to the four corners.
  • Fig. 15 is a diagram showing the corrugations 9 in the second plate 2 in which the inlet and outlet holes are positioned nearer to the four corners.
  • Fig. 16 is a diagram showing the corrugations 9 in the first plate 3 in which the inlet and outlet holes are positioned nearer to the four corners.
  • each of the plates 2 and 3 includes the corrugations 9 arranged in a plurality of longitudinal arrays, the corrugations 9 having the ends 13 at both sides in the lateral direction and also having the turning points 12 longitudinally misaligned with respect to the corresponding ends 13 at both sides, so that the corrugations 9 are V-shaped.
  • the turning points 12 of the corrugations 9 in the plates 2 and 3 shown in Figs. 3 and 4 are positioned at the lateral center. That is, the corrugations 9 are formed in a bilaterally symmetrical manner.
  • the diameters of the first inlet and outlet holes are smaller than the diameters of the second inlet and outlet holes. That is, in Fig. 14 , the diameters of the first inlet hole 5 and the first outlet hole 6 are smaller than the diameters of the second inlet hole 7 and the second outlet hole 8. For this reason, if the turning points 12 are positioned at the lateral center as in the plates 2 and 3 shown in Figs. 3 and 4 , this will create regions where the corrugations 9 are not formed near the first inlet hole 5 and the first outlet hole 6.
  • the corrugations 9 are formed by shifting the positions of the turning points 12 of the corrugations 9 nearer to the first inlet hole 5 and the first outlet hole 6, respectively. That is, as shown in Fig. 14 , a line 15 linking the turning points 12 of the corrugations 9 is defined in a gradual curve, curving toward the first inlet hole 5 and the first outlet hole 6, respectively, from a center line 14 at the lateral center.
  • the corrugations 9 can also be formed in the regions near the first inlet hole 5 and the first outlet hole 6, so that the heat transfer area is increased. Accordingly, the heat exchange capability of the plate heat exchanger 20 is enhanced.
  • the plates 2 are joined with the respective adjacent plates 3 at portions where the corrugations 9 are formed. Generally speaking, the plates 2 and 3 are prone to separation from one another in regions near the inlet and outlet holes. However, by forming the corrugations 9 also in the regions near the inlet and outlet holes, the joining points between the plates 2 and 3 are increased in number, so that the plates 2 and 3 can be prevented from separating from one another.
  • each turning point 12 of the corrugations 9 gradually moves from the first inlet hole 5 toward the lateral center and from the lateral center toward the first outlet hole 6. This makes it possible to smoothly transfer the first fluid entered from the first inlet hole 5 to the lateral center and from the lateral center to the first outlet hole 6. Accordingly, the pressure loss of the first fluid can be reduced.
  • the corrugations 9 are also formed in the second plate 2 by shifting the positions of the turning points 12 nearer to the first inlet hole 5 and the first outlet hole 6 in the regions near the first inlet hole 5 and the first outlet hole 6 having smaller diameters, respectively, as shown in Fig. 16 .
  • Figs. 17 to 19 are diagrams showing the plates 2 and 3 in which the first inlet and outlet holes are shaped differently from the second inlet and outlet holes while maintaining required opening areas.
  • the first inlet and outlet holes and the second inlet and outlet holes are formed in approximately elliptical shapes different from each other.
  • a circle is divided into two such that one of the two portions is the first inlet or outlet hole and the other portion is the second outlet or inlet hole.
  • Fig. 19 an approximately rectangular shape is divided into two such that one of the two portions is the first inlet or outlet hole and the other portion is the second outlet or inlet hole.
  • the diameters of the first inlet and outlet holes are smaller than the diameters of the second inlet and outlet holes.
  • Fig. 20 is a diagram comparing a case in which the first inlet and outlet holes and the second inlet and outlet holes are identical in shape, and a case in which the first inlet and outlet holes and the second inlet and outlet holes are different in shape.
  • Fig. 20 shows the longitudinal side of the plates 2 and 3 where the first outlet hole 6 and the second inlet hole 7 are located.
  • Fig. 20(a) shows the plates 2 and 3 in which the first outlet hole 6 and the second inlet hole 7 are both circularly shaped.
  • Fig. 20(b) shows the plates 2 and 3 in which a circle is divided into two such that one of the two portions is the first inlet or outlet hole and the other portion is the second outlet or inlet hole, as shown in Fig. 18 .
  • the diameters of the first inlet and outlet holes are smaller than the diameters of the second inlet and outlet holes.
  • the first outlet hole 6 shown in Fig. 20(a) is a circle having a diameter of"12 mm
  • the second inlet hole 7 is a circle having a diameter of "28 mm”.
  • the distance between the first outlet hole 6 and the second inlet hole 7 is "3 mm”. Accordingly, the opening area of the first outlet hole 6 is “36 ⁇ m 2 ", and the opening area of the second inlet hole 7 is “196 ⁇ m 2 ".
  • the length from the edge of the first outlet hole 6 to the edge of the second inlet hole 7 is "43 mm".
  • the first outlet hole 6 shown in Fig. 20(b) is a quarter of a circle having a diameter of "24 mm”
  • the second inlet hole 7 is three-quarters of a circle of "31 mm”.
  • the distance between the first outlet hole 6 and the second inlet hole 7 is "3 mm”.
  • the opening area of the first outlet hole 6 is "36 ⁇ m 2 "
  • the opening area of the second inlet hole 7 is "192 ⁇ m 2 ".
  • the length from the edge of the first outlet hole 6 to the edge of the second inlet hole 7 is "31 mm".
  • the opening area of the first outlet hole 6 shown in Fig. 20(a) and the opening area of the second inlet hole 7 shown in Fig. 20(b) are both “36 ⁇ m 2 " and thus are the same.
  • the opening area of the first outlet hole 6 shown in Fig. 20(a) and the opening area of the second inlet hole 7 shown in Fig. 20(b) are "196 ⁇ m 2 " and "192 ⁇ m 2 ", respectively, and thus are approximately the same.
  • the length from the edge of the first outlet hole 6 to the edge of the second inlet hole 7 is "43 mm" in the plates 2 and 3 shown in Fig. 20(a) , whereas this length is "31 mm" in the plates 2 and 3 shown in Fig.
  • the length from the edge of the first outlet hole 6 to the edge of the second inlet hole 7 is significantly shorter in the plates 2 and 3 shown in Fig. 20(b) than in the plates 2 and 3 shown in Fig. 20(a) .
  • Figs. 21 to 24 are diagrams showing the plates 2 and 3 in which the first inlet and outlet holes and the second inlet and outlet holes are formed in identical non-circular shapes while maintaining the required opening areas.
  • first inlet and outlet holes and the second inlet and outlet holes are formed identically in an approximately elliptical shape.
  • the first inlet and outlet holes and the second inlet and outlet holes are formed identically in a fan-like shape.
  • Fig. 24 the first inlet and outlet holes and the second inlet and outlet holes are formed identically in a star-like shape.
  • the plate heat exchanger 20 can be configured with the plates 2 and 3 of a single type.
  • a heating and hot water system 29 which is a usage example of the plate heat exchanger 20 described in the above embodiments.
  • Fig. 25 is a diagram showing the heating and hot water system 29.
  • the heating and hot water system 29 includes a compressor 21, the plate heat exchanger 20, an expansion valve 22, a heat exchanger 23, a water heater 24, a heater 25, a refrigerant path 26, and a water path 27.
  • the plate heat exchanger 20 here is the plate heat exchanger 20 described in the above embodiments.
  • the compressor 21, the plate heat exchanger 20, the expansion valve 22, the heat exchanger 23, and the refrigerant path 26 constitute a heat exchange system 28.
  • a refrigerant flows through the refrigerant path 26 by circulating sequentially through the compressor 21, the plate heat exchanger 20, the expansion valve 22, and the heat exchanger 23.
  • the compressor 21 compresses the refrigerant.
  • the plate heat exchanger 20 exchanges heat between the refrigerant compressed by the compressor 21 and a fluid (water in this case) flowing through the water path 27.
  • the refrigerant is cooled and the water is warmed by heat exchange in the plate heat exchanger 20.
  • the expansion valve 22 controls expansion of the refrigerant heat-exchanged by the plate heat exchanger 20.
  • the heat exchanger 23 exchanges heat between air and the refrigerant expanded based on control by the expansion valve 22.
  • the refrigerant is warmed and the air is cooled by heat exchange in the heat exchanger 23. Then, the warmed refrigerant enters the compressor 21.
  • the water flows through the water path 27 among the plate heat exchanger 20, the water heater 24, and the heater 25.
  • the water is warmed by heat exchange in the plate heat exchanger 20.
  • the warmed water flows to the water heater 24 or the heater 25.
  • the water for hot-water supply may be different from the water heat-exchanged by the plate heat exchanger 20. That is, the water heater 24 or the like may further exchange heat between the water flowing through the water path 27 and the water for hot-water supply.
  • the plate heat exchanger 20 described in the above embodiments provides enhanced strength, a compact and lightweight structure, and enhanced efficiency.
  • the heat exchange system 28 using the plate heat exchanger 20 described in the above embodiments also provides enhanced efficiency.
  • the heating and hot water system 29 using the heat exchange system 28 also provides enhanced efficiency.
  • a heat exchange system (an air-to-water (ATW) system) has been described, wherein the plate heat exchanger 20 described in the above embodiments heats water by using a compressed refrigerant.
  • a refrigeration cycle (a refrigeration air conditioner) may be configured for exchanging heat by using the plate heat exchanger 20 described in the above embodiments so as to heat or cool a fluid such as air.
  • the plate heat exchanger 20 is configured with a plurality of stacked plates such that flow holes which act as inlets or outlets for a fluid are formed at four corners of each plate, and inlet ducts and outlet ducts are provided in the plurality of stacked plates.
  • the plate heat exchanger 20 is characterized in that the widthwise distance between each of the first and second fluid inlets and outlets and the periphery of the plate is 3 to 6 % of the width (W) of the plate.
  • the plate heat exchanger 20 is configured with a plurality of stacked plates such that flow holes which act as inlets or outlets for a fluid are formed at four corners of each plate, and inlet ducts and outlet ducts are provided in the plurality of stacked plates.
  • the plate heat exchanger 20 is characterized in that the widthwise distance between each of the first and second fluid inlets and outlets and the periphery of the plate is 3 to 5.6 mm.
  • the plate heat exchanger 20 is configured with a plurality of stacked plates such that flow holes which act as inlets or outlets for a fluid are formed at four corners of each plate, and inlet ducts and outlet ducts are provided in the plurality of stacked plates.
  • the plate heat exchanger 20 is characterized in that the diameters of the first inlet and outlet are differently sized from the diameters of the second fluid inlet and outlet.
  • the plate heat exchanger 20 is configured with a plurality of stacked plates such that flow holes which act as inlets or outlets for a fluid are formed at four corners of each plate, and inlet ducts and outlet ducts are provided in the plurality of stacked plates.
  • the plate heat exchanger 20 is characterized in that the centers of the first fluid inlet and outlet are misaligned with the centers of the second fluid inlet and outlet such that the fluid inlets and outlets are shifted nearer to the periphery of the plate.
  • the plate heat exchanger 20 is configured with a plurality of stacked plates such that flow holes which act as inlets or outlets for a fluid are formed at four corners of each plate, and inlet ducts and outlet ducts are provided in the plurality of stacked plates.
  • the plate heat exchanger 20 is characterized in that crest portions formed at turning points of waves are arranged to gradually curve from the center of the plate such that the turning points of the waves are formed in regions near the inlet and outlet.
  • the plate heat exchanger 20 is configured with a plurality of stacked plates such that flow holes which act as inlets or outlets for a fluid are formed at four corners of each plate, and inlet ducts and outlet ducts are provided in the plurality of stacked plates.
  • the plate heat exchanger 20 is characterized in that the centers of the diameters of the first fluid inlet and outlet are misaligned with the centers of the diameters of the second inlet and outlet, and the first inlet and outlet and the second inlet and outlet are formed in a combination of different shapes such as circular shapes or polygonal shapes while maintaining required opening areas according to a processing flow amount of the second fluid.
  • the plate heat exchanger 20 is configured with a plurality of stacked plates such that flow holes which act as inlets or outlets for a fluid are formed at four corners of each plate, and inlet ducts and outlet ducts are provided in the plurality of stacked plates.
  • the plate heat exchanger 20 is characterized in that the first inlet and outlet and the second inlet and outlet are formed in a combination of an identical shape such as a circular shape or a polygonal shape while maintaining required opening areas according to a processing flow amount of the second 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)

Claims (10)

  1. Échangeur de chaleur à plaques configuré avec une pluralité de plaques empilées (2, 3),
    dans lequel chaque plaque de la pluralité de plaques empilées comprend :
    un premier trou d'entrée (5) qui agit en tant qu'orifice d'entrée d'un premier fluide, le premier trou d'entrée étant situé à proximité d'un bord dans une direction longitudinale ;
    un premier trou de sortie (6) qui fait office d'orifice de sortie du premier fluide, le premier trou de sortie étant situé à proximité d'un autre bord opposé au premier trou d'entrée dans la direction longitudinale ;
    un second trou d'entrée (7) qui fait office d'orifice d'entrée d'un second fluide, le second trou d'entrée étant situé à proximité d'un bord dans la direction longitudinale ; et
    un second trou de sortie (8) qui fait office d'orifice de sortie du second fluide, le second trou de sortie étant situé à proximité d'un autre bord opposé au second trou d'entrée dans la direction longitudinale ;
    dans lequel chaque plaque et une plaque adjacente définissent entre elles l'un ou l'autre d'un premier chemin d'écoulement et d'un second chemin d'écoulement, le premier chemin d'écoulement laissant passer le premier fluide entré en provenance du premier trou d'entrée vers le premier trou de sortie de telle sorte que le premier fluide s'étende dans une direction latérale, et le second chemin d'écoulement laissant passer le second fluide entré en provenance du deuxième trou d'entrée vers le second trou de sortie de telle sorte que le second fluide s'étende dans la direction latérale, et chaque plaque d'échange de la chaleur entre le premier fluide qui s'écoule à travers le premier chemin d'écoulement et le second fluide qui s'écoule à travers le second chemin d'écoulement ;
    dans lequel chacune d'une surface d'ouverture du premier trou d'entrée et d'une surface d'ouverture du premier trou de sortie est plus petite que l'une ou l'autre d'une surface d'ouverture du second trou d'entrée et d'une surface d'ouverture du second trou de sortie ;
    dans lequel chaque plaque comprend des parties convexes et des parties concaves en forme de V agencées en une pluralité d'ensembles dans la direction longitudinale, chacune des parties convexes et des parties concaves présentant des extrémités (13) au niveau des deux extrémités dans la direction latérale et présentant également un point de virage (12) désaligné de manière longitudinale par rapport aux extrémités, de telle sorte que les parties convexes et les parties concaves soient formées en une forme de V ; et
    caractérisé en ce que les parties convexes et les parties concaves en forme de V sont agencées de telle sorte que, à proximité d'une partie centrale dans la direction longitudinale, le point de virage soit formé au niveau d'un centre dans la direction latérale, et à proximité au moins de l'un ou l'autre du premier trou d'entrée et du premier trou de sortie, la position du point de virage soit décalée de manière progressive à partir du centre dans la direction latérale au fur et à mesure que la position de chacune des parties convexes et de parties concaves en forme de V se rapproche de l'un ou l'autre du premier trou.
  2. Échangeur de chaleur à plaques selon la revendication 1,
    dans lequel chaque plaque est configurée de telle sorte que la longueur (L1) dans la direction longitudinale soit égale à 4 fois ou plus la longueur (L2) dans la direction latérale.
  3. Échangeur de chaleur à plaques selon la revendication 1,
    dans lequel chacune de la longueur (L3) à partir du premier trou d'entrée vers un bord de plaque à proximité du premier trou d'entrée dans la direction latérale, de la longueur (L4) à partir du premier trou de sortie vers un bord de plaque à proximité du premier trou de sortie dans la direction latérale, de la longueur (L5) à partir du second trou d'entrée vers un bord de plaque à proximité du second trou d'entrée dans la direction latérale, et de la longueur (L6) à partir du second trou de sortie vers un bord de plaque à proximité du second trou de sortie dans la direction latérale, n'est pas supérieure à 6 pour cent de la longueur (L2) dans la direction latérale.
  4. Échangeur de chaleur à plaques selon la revendication 1,
    dans lequel chacune de la longueur (L3) à partir du premier trou d'entrée vers un bord de plaque à proximité du premier trou d'entrée dans la direction latérale, de la longueur (L4) à partir du premier trou de sortie vers un bord de plaque à proximité du premier trou de sortie dans la direction latérale, de la longueur (L5) à partir du second trou d'entrée vers un bord de plaque à proximité du second trou d'entrée dans la direction latérale, et de la longueur (L6) à partir du second trou de sortie vers un bord de plaque à proximité du second trou de sortie dans la direction latérale, n'est pas supérieure à 5,6 mm.
  5. Échangeur de chaleur à plaques selon la revendication 1,
    dans lequel le centre du premier trou d'entrée et le centre du premier trou de sortie sont positionnés plus près d'un bord de plaque que le centre du second trou d'entrée et le centre du second trou de sortie.
  6. Échangeur de chaleur à plaques selon la revendication 1,
    dans lequel une première plaque (3) et une deuxième plaque (2) sont empilées de manière alternée, dans lequel le premier trou d'entrée et le second trou de sortie sont positionnés à proximité d'un même bord dans la direction longitudinale ; et
    dans lequel la première plaque comprend une partie étanchéité (11) destinée à empêcher un fluide qui a pénétré à partir du premier trou d'entrée de s'écouler vers le second trou de sortie, la partie étanchéité étant formée sous la forme d'une saillie relevée dans la direction d'empilement de la pluralité de plaques empilées de telle sorte que la partie étanchéité s'étend à partir de la proximité du bord où le premier trou d'entrée et le second trou de sortie se situent vers un bord opposé dans la direction longitudinale, de façon à s'approcher de manière progressive vers un bord dans la direction transversale à proximité du second trou de sortie.
  7. Échangeur de chaleur à plaques selon la revendication 1,
    dans lequel la pluralité de plaques empilées sont empilées de telle sorte que le premier trou d'entrée de chaque plaque est aligné avec les premiers trous d'entrée des autres plaques, de telle sorte que le premier fluide s'écoule de manière séquentielle à partir du premier trou d'entrée de chaque plaque empilée au niveau d'un côté de la direction d'empilement dans le premier trou d'entrée de chaque plaque empilée au niveau d'un autre côté de la direction d'empilement ; et
    dans lequel plus chaque plaque de la pluralité de plaques empilées se rapproche du côté à partir duquel le premier fluide pénètre, plus le diamètre du premier trou d'entrée est petit.
  8. Échangeur de chaleur à plaques selon la revendication 1,
    dans lequel le premier trou d'entrée et le second trou de sortie sont formés à proximité d'un même bord dans la direction longitudinale, et le second trou d'entrée et le premier trou de sortie sont formés à proximité d'un même bord dans la direction longitudinale ; et
    dans lequel la forme du premier trou d'entrée est différente de la forme du second trou de sortie, et la forme du second trou d'entrée est différente de la forme du premier trou de sortie.
  9. Échangeur de chaleur à plaques selon la revendication 8,
    dans lequel le premier trou d'entrée et le second trou de sortie sont formés en divisant un trou de forme circulaire, elliptique ou polygonale en deux trous ; et
    dans lequel le second trou d'entrée et le premier trou de sortie sont formés en divisant un trou de forme circulaire, elliptique ou polygonale en deux trous.
  10. Climatiseur de réfrigération comprenant l'échangeur de chaleur à plaques selon la revendication 1.
EP09841919.5A 2009-03-18 2009-12-21 Échangeur thermique de type à plaques et dispositif de conditionnement d'air et de réfrigération Active EP2410278B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009065826A JP5106453B2 (ja) 2009-03-18 2009-03-18 プレート式熱交換器及び冷凍空調装置
PCT/JP2009/071230 WO2010106717A1 (fr) 2009-03-18 2009-12-21 Échangeur thermique de type à plaques et dispositif de conditionnement d'air et de réfrigération

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EP2410278A1 EP2410278A1 (fr) 2012-01-25
EP2410278A4 EP2410278A4 (fr) 2013-01-09
EP2410278B1 true EP2410278B1 (fr) 2014-12-10

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US20120012291A1 (en) 2012-01-19
CN102356295B (zh) 2015-10-14
WO2010106717A1 (fr) 2010-09-23
EP2410278A1 (fr) 2012-01-25
CN102356295A (zh) 2012-02-15
JP2010216754A (ja) 2010-09-30
EP2410278A4 (fr) 2013-01-09
JP5106453B2 (ja) 2012-12-26

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