WO2010013608A1 - Échangeur de chaleur à plaque utilisé comme évaporateur ou condenseur - Google Patents

Échangeur de chaleur à plaque utilisé comme évaporateur ou condenseur Download PDF

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Publication number
WO2010013608A1
WO2010013608A1 PCT/JP2009/062943 JP2009062943W WO2010013608A1 WO 2010013608 A1 WO2010013608 A1 WO 2010013608A1 JP 2009062943 W JP2009062943 W JP 2009062943W WO 2010013608 A1 WO2010013608 A1 WO 2010013608A1
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WIPO (PCT)
Prior art keywords
heat exchange
heat transfer
exchange chamber
plate
heat
Prior art date
Application number
PCT/JP2009/062943
Other languages
English (en)
Japanese (ja)
Inventor
淳一 中村
健司 楠
稔 松下
光弘 渡邊
磐雄 澤田
博 深田
誠子 土肥
Original Assignee
株式会社ササクラ
株式会社日阪製作所
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Application filed by 株式会社ササクラ, 株式会社日阪製作所 filed Critical 株式会社ササクラ
Priority to JP2010502108A priority Critical patent/JPWO2010013608A1/ja
Publication of WO2010013608A1 publication Critical patent/WO2010013608A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—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
    • F28D9/0056—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 with U-flow or serpentine-flow inside conduits; with centrally arranged openings on the plates
    • 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
    • F28D9/02—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 heat-exchange media travelling at an angle to one another
    • 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
    • F28F3/044—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 pontual, e.g. dimples
    • 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
    • F28F3/083—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning capable of being taken apart
    • 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
    • F28F3/10—Arrangements for sealing the margins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/108—Particular pattern of flow of the heat exchange media with combined cross flow and parallel flow

Definitions

  • the present invention generates steam in a plate-type heat exchange device in which a plurality of rectangular heat transfer plates are laminated so that first heat exchange chambers and second heat exchange chambers are alternately formed therebetween.
  • the present invention relates to a plate-type heat exchange device that is used as an evaporator or as a condenser that condenses steam.
  • Patent Document 1 as a prior art describes that the plate type heat exchange device having the above configuration is configured as described below when used as an evaporator.
  • a steam outlet from the first heat exchange chamber is connected to one of the left and right corners on the upper side of the heat transfer plate, and the steam outlet of the left and right corners on the lower side of the heat transfer plate.
  • One of the corners is provided with an evaporating liquid inlet to each of the first heat exchange chambers, and the second heat is provided at the other of the left and right corners on the upper side of the heat transfer plate.
  • a heating fluid inlet to the exchange chamber is provided at the other of the left and right corners on the lower side of the heat transfer plate, respectively. It is configured as follows.
  • the liquid to be evaporated supplied to one corner of the first heat exchange chamber mainly has a direction in which the pressure loss is lowest, that is, while boiling and evaporating in the first heat exchange chamber.
  • the heating fluid supplied to one corner of the second heat exchange chamber mainly has the lowest pressure loss while flowing substantially linearly in the direction toward the one corner and the diagonal corner.
  • the fluid flows widely throughout the first and second heat exchange chambers by flowing in a substantially linear direction in the second direction, that is, in a direction toward the one corner and the diagonal corner. Since it cannot be dispersed and the entire surface of the heat transfer plate cannot be used effectively for heat exchange, the evaporation capacity per unit heat transfer area is low.
  • the said patent document 1 uses the plate type heat exchange apparatus of the said structure as a condenser, “The vapor outlet is a vapor inlet, the liquid to be evaporated is a condensed liquid outlet, the heating fluid inlet is a cooling fluid inlet, and the heating fluid outlet is a cooling fluid outlet.”
  • the structure is as follows.
  • the fluid flows widely in the first and second heat exchange chambers by flowing the fluid mainly in the diagonal direction in the first and second heat exchange chambers.
  • the entire surface of the heat transfer plate cannot be used effectively for heat exchange, so the condensation capacity per unit heat transfer area is low.
  • the present inventors have proposed a plate-type heat exchange device that can be used as an evaporator or a condenser as described in Patent Document 2 in the prior invention.
  • the “plate heat exchanger used as an evaporator or condenser” of the invention of the prior application is “A plurality of rectangular heat transfer plates are laminated so that a plurality of first heat exchange chambers and a plurality of second heat exchange chambers are alternately formed between them.
  • a steam outlet or a steam outlet for the first heat exchange chamber is provided at one corner of a lower side of each heat transfer plate, and a liquid inlet or a condensed water outlet for the first heat exchange chamber is provided,
  • a heating fluid inlet and a heating fluid outlet or a cooling fluid inlet and a cooling fluid outlet for the second heat exchange chamber are provided side by side on one side of the left and right sides of each heat transfer plate,
  • a fluid passage extending from the heating fluid inlet or the cooling fluid inlet to the heating fluid outlet or the cooling fluid outlet is formed in a folded shape in the left-right direction.
  • the bottom A distribution fluid passage extending in the horizontal direction along the left and right sides and communicating with both of the vaporized liquid inlets, and the steam outlet along a pair of heat transfer plates forming the first heat exchange chamber from the distribution fluid passage.
  • a plurality of first tunnel-like fluid passages configured to extend in the vertical direction toward the left and right are formed at appropriate intervals in the left-right direction, and further, the second fluid passage in the second heat exchange chamber has the second fluid passage.
  • a plurality of second tunnel-like fluid passages configured to extend in the left-right direction along a pair of heat transfer plates forming the heat exchange chamber are formed at appropriate intervals in the vertical direction. It was the composition.
  • the liquid to be evaporated entering the first heat exchange chamber from the inlet of the liquid to be evaporated on the lower side is a fluid distribution passage extending laterally at the bottom of the liquid.
  • the steam that has entered the first heat exchange chamber from the horizontally long steam outlet is distributed to a plurality of first tunnel fluid passages, and the inside of the first tunnel fluid passages. , It is condensed by cooling when it flows downward, and this condensed liquid is collected in a fluid distribution passage extending laterally at the bottom, and then flows out from both condensed liquid outlets on the lower side, and enters the second heat exchange chamber
  • the cooling fluid flows in the second tunnel-shaped fluid passage in the folded fluid passage in the left-right direction toward the cooling fluid outlet, thereby allowing the steam and the cooling fluid to pass through the first heat exchange chamber and Since the entire second heat exchange chamber can be spread, effective use of the heat transfer area can be achieved.
  • a fresh water generator (a device that produces fresh water from seawater by combining an evaporator and a condenser), which is a suitable application of a heat exchange device, or a part of a concentrator, etc. It was necessary to improve the performance.
  • the target fluid in the fresh water generator is seawater and is corrosive. In addition, it must be able to withstand the holding pressure of the system in order to connect to a fluid system such as sea water in the ship.
  • the fluid to be handled is not corrosive and the working pressure is not particularly high, it is possible to use a low-grade material and manufacture it with thick plates according to the required pressure resistance, in which case there is no pattern. However, it can be used economically without any problem in terms of pressure resistance.
  • the thickness of the heat transfer plate made of an expensive material is made as thin as possible, and the pressure resistance of the thin heat transfer plate is increased.
  • a pattern is provided on the heat transfer plate so as to contact the adjacent heat transfer plate at many points to support the pressure received by the heat transfer plate, and the heat transfer performance is improved by effectively using the pattern. It is essential to reduce the required area or number of sheets as much as possible.
  • the inventors of the present invention repeated trial manufactures with various heat transfer plates, and found a heat transfer plate having a pattern that is optimal for corrosive fluids such as seawater and high pressure, that is, unevenness.
  • claim 1 of the present invention provides: “A plurality of rectangular heat transfer plates are laminated so that a plurality of first heat exchange chambers and a plurality of second heat exchange chambers are alternately formed between them. , A vapor outlet from the first heat exchange chamber is provided in a horizontally long shape along the upper side, and an evaporating liquid inlet communicating with the first heat exchange chamber is provided at least one of the lower sides of the heat transfer plate A heating fluid inlet and a heating fluid outlet communicating with the second heat exchange chamber are arranged vertically on one side of the left and right sides of the heat transfer plate.
  • a fluid passage extending from the heating fluid inlet to the heating fluid outlet is formed in a folded shape in the left-right direction by a partition member
  • the heat transfer plate has first raised portions formed by bulging and deforming the heat transfer plate into the shape of a cone so as to protrude into the first heat exchange chamber, and arranged at appropriate intervals in the vertical and horizontal directions.
  • a plurality of the first raised portions are in the shape of a truncated cone having a flat top, and the top flat surfaces are in contact with each other in the first heat exchange chamber.
  • the heat transfer plate has a second raised portion formed by bulging and deforming a portion between the first raised portions of the heat transfer plate into a cone shape so as to protrude into the second heat exchange chamber,
  • a plurality of second ridges are provided in the vertical and horizontal directions at appropriate intervals.
  • the second ridges are in the shape of truncated cones with the tops being flat, and the top planes are mutually connected in the second heat exchange chamber. It is a structure to touch. " It is characterized by that.
  • Claim 2 of the present invention includes: “A plurality of rectangular heat transfer plates are laminated so that a plurality of first heat exchange chambers and a plurality of second heat exchange chambers are alternately formed between them. , A steam inlet to the first heat exchange chamber is formed in a horizontally long shape along the upper side, and a condensed liquid outlet communicating with the first heat exchange chamber is provided at least at one corner of the lower side of the heat transfer plate. The cooling fluid inlet and the cooling fluid outlet that communicate with the second heat exchange chamber are provided side by side on one side of the left and right sides of the heat transfer plate.
  • a fluid passage extending from the cooling fluid inlet to the cooling fluid outlet is formed by folding in the left-right direction with a partition member,
  • the heat transfer plate has first raised portions formed by bulging and deforming the heat transfer plate into the shape of a cone so as to protrude into the first heat exchange chamber, and arranged at appropriate intervals in the vertical and horizontal directions.
  • a plurality of the first raised portions are in the shape of a truncated cone having a flat top, and the top flat surfaces are in contact with each other in the first heat exchange chamber.
  • the heat transfer plate has a second raised portion formed by bulging and deforming a portion between the first raised portions of the heat transfer plate into a cone shape so as to protrude into the second heat exchange chamber,
  • a plurality of second ridges are provided in the vertical and horizontal directions at appropriate intervals.
  • the second ridges are in the shape of truncated cones with the tops being flat, and the top planes are mutually connected in the second heat exchange chamber. It is a structure to touch. " It is characterized by that.
  • Claim 3 of the present invention provides: “In the description of claim 1, the communication with the first heat exchange chamber at the inlet of the liquid to be evaporated is configured to communicate through a small hole.” It is characterized by that.
  • Claim 4 of the present invention provides: “In the first or second aspect of the present invention, the first ridge and the second ridge are a regular quadrilateral or an array substantially close to a regular quadrilateral, and the regular quadrilateral has a diagonal up and down. It is a regular quadrilateral with direction and horizontal direction. " It is characterized by that.
  • Claim 5 of the present invention provides: “In the description of any one of the first to fourth aspects, the partition member is formed by forming a string-like body made of a soft elastic body and is sandwiched between the two heat transfer plates. A plurality of plate-like pieces bonded to one of the heat transfer plates are integrally provided at a plurality of locations along the longitudinal direction. It is characterized by that.
  • Claim 6 of the present invention provides: “In the description of claim 5, a part of the string-like body in the diametrical direction is fitted in a recessed groove provided in one of the heat transfer plates.” It is characterized by that.
  • claim 1 is a case of using as an evaporator.
  • each first heat exchange chamber the liquid to be evaporated such as water entering from the inlet of the liquid to be evaporated in the lower part rises while boiling and evaporating by heating by heat transfer from each second heat exchange chamber and becomes steam. After the state change, the steam flows from the bottom to the top in the first heat exchange chambers, such as going out from the horizontally long steam outlet.
  • the plurality of first raised portions protruding into the first heat exchange chambers are in the shape of truncated cones and arranged in the vertical and horizontal directions, so that the first heat exchange chambers are directed upward.
  • the steam that flows through the first ridges is divided into two left and right flows every time it hits the lower surface of the first ridges, and the steam that flows in the left and right directions repeats. Since the steam flow can be greatly expanded in a direction perpendicular to the steam flow direction, the steam flow can be reliably dispersed in the entire width direction of the first heat exchange chamber.
  • the first bulges support the pressure from the fluid in the second heat exchange chamber, which is usually at a higher pressure, by providing them at appropriate intervals. Deformation can be prevented.
  • the first ridges provided at appropriate intervals not only disperse the fluid flow properly, but also give a moderate turbulence in spite of a slight increase in pressure loss, and the heat transfer coefficient is reduced. It turns out that it improves significantly.
  • herringbone As the heat exchange plate pattern, the most commonly used shape, herringbone, has a pressure loss that is too high, which has the adverse effect of suppressing evaporation and is not only inefficient but also poorly distributed. I could't omit it either.
  • the first heat exchange chamber that is, the evaporating fluid flows with the long side of the horizontally long heat transfer plate as the flow width and the short side as the flow distance.
  • the flow disturbance is small, the efficiency is poor, and the dispersion is also poor.
  • a thin heat transfer plate can be used. Not only is the amount of material required, but also the heat transfer resistance through the heat transfer plate can be reduced to reduce the required area.
  • the plurality of second raised portions protruding into the respective second heat exchange chambers are in the shape of truncated cones and arranged in the vertical and horizontal directions, so that the folded fluid passages are arranged in the horizontal direction.
  • the heating fluid that flows through the second bulge flows repeatedly while being spread in the vertical direction at each second bulge, so that each time it hits the side surface of each second bulge, the flow is divided into two flows.
  • the flow of the heating fluid can be greatly expanded in a direction perpendicular to the flow direction of the heating fluid.
  • the short side of the horizontally long heat transfer plate flows with the short side as the flow width and the long side as the flow distance.
  • the structure is designed to improve dispersion and heat transfer efficiency.
  • the flowing fluid is so small that it does not compare with evaporative vapor in volume, the flow is less turbulent and the efficiency is poor, and the dispersion is poor.
  • a folded flow is used to reduce the flow path width and increase the flow velocity to improve efficiency.
  • first raised portion and the second raised portion are formed in a truncated cone shape and the top planes thereof are in contact with each other, tolerances during press forming are provided. Even if the heat transfer plates are slightly displaced due to assembly tolerances, subtle movements during operation, etc., it is possible to ensure that the top planes are in contact with each other, so that the pressure applied to each heat transfer plate can be ensured. Can be supported.
  • claim 2 is a case of using as a condenser.
  • the plurality of first raised portions protruding into the first heat exchange chambers are in the shape of truncated cones and arranged in the vertical direction and the horizontal direction, so that the first heat exchange chambers are directed downward.
  • the first bulges support the pressure from the fluid in the second heat exchange chamber, which is usually at a higher pressure, by providing them at appropriate intervals. Deformation can be prevented.
  • herringbone As the heat transfer plate pattern, the most commonly used shape, herringbone, has a pressure loss that is too high, which has the adverse effect of suppressing condensation and is not efficient, and is not sufficiently distributed, resulting in a tunnel-like passage. I could't omit it either.
  • the first heat exchange chamber that is, the large volume of steam that condenses
  • the flow turbulence is small, the efficiency is poor, and the dispersion is also poor.
  • the first ridges at appropriate intervals, both can be remarkably improved, and a thin heat transfer plate is used.
  • the heat transfer resistance through the heat transfer plate can also be reduced and the required area can be reduced.
  • the plurality of second raised portions protruding into the respective second heat exchange chambers are in the shape of truncated cones and arranged in the vertical and horizontal directions, so that the folded fluid passages are arranged in the horizontal direction.
  • the cooling fluid that flows through the second bulge flows repeatedly while being spread in the vertical direction at each second ridge so that each time it hits the side surface of each second bulge, the flow is divided into two flows. Therefore, the flow of the cooling fluid can be greatly spread in the direction perpendicular to the flow direction of the cooling fluid, so that it can be surely dispersed in the folded fluid passage in the entire width direction. .
  • the second heat exchange chamber that is, liquid cooling water
  • the pressure loss is the largest.
  • the structure is designed to improve dispersion and heat transfer efficiency.
  • the flowing fluid is so small that it is incomparable with the vapor that condenses volumetrically, the flow is less disturbed and the efficiency is poor and the dispersion is also poor.
  • a folded flow is used to reduce the flow path width and increase the flow velocity to improve efficiency.
  • first raised portion and the second raised portion are formed in a truncated cone shape, and the top surfaces thereof are in contact with each other, press forming is performed. Even if each heat transfer plate is slightly displaced due to time tolerance, assembly tolerance, or slight movement during operation, it is possible to ensure that the top planes are in contact with each other. The pressure can be reliably supported.
  • the communication with the first heat exchange chamber at the inlet of the liquid to be evaporated is configured to communicate with the first heat exchange chamber through a small hole. Regulating and controlling the amount of liquid to be evaporated entering the chamber through the small holes keeps the same and uniform in all the first heat exchange chambers regardless of differences or fluctuations in other conditions, and makes the evaporation uniform. , All the first heat exchange chambers can be operated uniformly to achieve the highest efficiency.
  • the regular quadrilateral in the arrangement of the first and second bulges is a positive quadrangle whose diagonal is up and down and left and right.
  • the flow of the steam and the heating fluid or the cooling fluid is such that each first ridge or each second ridge in the first first row of the rows perpendicular to the flow direction.
  • the flow is divided into two left and right flows, and each of the two divided right and left flows is a first ridge or each second ridge in the first row in a second row located downstream of the first row.
  • the partition member interposed between the heat transfer plates can be formed into a string-like body, and the heat transfer area can be increased by that amount.
  • the string-like body is provided integrally with the string-like body so that the string-like body falls from the heat transfer plate or deviates from a predetermined mounting position. Since it can be surely prevented by adhering one piece to one heat transfer plate, the workability in assembling and disassembling the plate heat exchanger can be improved.
  • FIG. 3 is an enlarged sectional view taken along line III-III in FIG. 1 and a sectional view taken along line III-III in FIG.
  • FIG. 6 is a view showing a second heat exchange chamber in an enlarged sectional view taken along line IV-IV in FIG. 1 and a sectional view taken along line IV-IV in FIG. 5.
  • FIG. 5 is an enlarged sectional view taken along line VV in FIGS. 3 and 4.
  • FIG. 6 is an enlarged sectional view taken along line VI-VI in FIGS. 3 and 4.
  • FIG. 7 is an enlarged sectional view taken along the line VII-VII in FIGS. 3 and 4.
  • FIG. 9 is a sectional view taken along the line IX-IX in FIG. 8. It is a figure which shows the modification in FIG. It is a figure which shows the plate type heat exchange apparatus by 2nd Embodiment. It is a top view of FIG. It is a figure which shows a 1st heat exchange chamber by the XIII-XIII enlarged sectional view of FIG. 11, and the XIII-XIII sectional view of FIG.
  • FIG. 16 is a view showing the second heat exchange chamber in the XIV-XIV enlarged sectional view of FIG. 11 and the XIV-XIV sectional view of FIG. FIG.
  • FIG. 15 is an enlarged cross-sectional view taken along line XV-XV in FIGS. 13 and 14.
  • FIG. 15 is an enlarged cross-sectional view taken along line XVI-XVI in FIGS. 13 and 14.
  • FIG. 15 is an enlarged sectional view taken along the line XVII-XVII in FIGS. 13 and 14. It is sectional drawing of the same location as FIG. 4 in 3rd Embodiment.
  • FIG. 19 is an enlarged cross-sectional view taken along the line XIX-XIX in FIG. 18, (a) shows a state before assembly, and (b) shows a state after assembly.
  • FIG. 19 is an enlarged cross-sectional view taken along the line XX-XX in FIG.
  • FIG. 22 is an enlarged cross-sectional view taken along the line XXII-XXII in FIG. 21, where (a) shows a state before assembly, and (b) shows a state after assembly.
  • FIG. 22 is an enlarged cross-sectional view taken along the line XXIII-XXIII in FIG. 21, where (a) shows a state before assembly and (b) shows a state after assembly.
  • First Embodiment 1 to 9 show a first embodiment of the present invention and show a plate heat exchanger 11 used as an evaporator.
  • This plate-type heat exchange device 11 includes a plurality of heat transfer plates 12 made of a relatively thin metal plate in a horizontally-long rectangular shape, and a first seal body 13 and a second seal body 14 that are also used as spacers are alternately arranged around the plate. And a plurality of first heat exchange chambers 15 that are sealed with the first seal body 13 and a plurality of seals that are sealed with the second seal body 14.
  • the second heat exchange chambers 16 are alternately formed, and the laminate is fixed to a supporting fixed face plate 17 disposed on one end face thereof and a movable face plate 18 provided on the other end face by a plurality of bolts 19. It is configured to be fastened in the stacking direction.
  • the heat exchange device 11 is fixed to the supporting fixed face plate 17 so that a pair of left and right guide rods 20 protrude in the stacking direction, and both guide rods 20 are attached to the heat transfer plates 12.
  • both guide rods 20 are attached to the heat transfer plates 12.
  • each heat transfer plate 12 has a steam outlet 21 formed in a horizontally long shape in the upper side portion thereof, and one of the left and right corners in the lower side.
  • a liquid inlet 22 to be evaporated is drilled in the corner of the liquid crystal.
  • a heating fluid inlet 23 and a heating fluid outlet 24 are vertically drilled in one of the left and right sides. Has been.
  • the first seal body 13 that forms the periphery of each of the first heat exchange chambers 15 includes seal pieces 13 a and 13 b that surround the heating fluid inlet 23 and the heating fluid outlet 24. And a seal piece 13c that surrounds the liquid inlet 22 to be evaporated, and the horizontally long steam outlet 21 communicates with the upper portion of each first heat exchange chamber 15 for the heating.
  • the fluid inlet 23 and the heating fluid outlet 24 are configured not to communicate with the first heat exchange chamber 15.
  • the second seal body 14 forming the periphery of each of the second heat exchange chambers 16 includes seal pieces 14a and 14b that surround the vapor outlet 21 and the liquid inlet 22 to be evaporated. Are integrally provided, and the heating fluid inlet 23 and the heating fluid outlet 24 communicate with one side of each of the second heat exchange chambers 16, and the vapor outlet 21 and the vaporized liquid inlet 22 are connected to the second heat exchange chamber 16.
  • the heat exchange chamber 16 is configured not to communicate with the heat exchange chamber 16.
  • the second seal body 14 is integrally provided with a partition member 14c that integrally extends in the left-right direction from a portion between the heating fluid inlet 23 and the heating fluid outlet 24.
  • Each of the second heat exchange chambers 16 is configured to have a folded fluid passage that is folded in the left-right direction from the heating fluid inlet 23 toward the heating fluid outlet 24.
  • each of the first heat exchange chambers 15 and the liquid inlet 22 is a seal piece of the second seal body 14 outside the seal piece 13c of the first seal body 13 of the heat transfer plate 12. It is configured to communicate with each other through a plurality of small holes 25 drilled in a portion inside 14b.
  • the vaporized liquid inlet 22 and the small holes 25 can be provided at the left and right corners of the lower side of the heat transfer plate 12.
  • the outer surface of the supporting fixed face plate 17 communicates with a vapor outlet pipe 26 communicating with the vapor outlet 21, a liquid supply pipe 27 to be evaporated communicating with the liquid inlet 22, and a heating fluid inlet 23.
  • a heating fluid supply pipe 28 is connected to a heating fluid outlet pipe 29 communicating with the heating fluid outlet 24.
  • each heat transfer plate 12 has the heat transfer plate 12 placed on the entire portion of the heat transfer plate 12 inside the first seal body 13.
  • a large number of first raised portions 30 formed by bulging and deforming toward the inside of the chamber 15 are provided in an array of appropriate intervals in the vertical direction and the horizontal direction.
  • each first raised portion 30 is based on a cone having a bottom surface with a diameter D0, and the top of the cone is a plane 30a parallel to the bottom surface of the cone.
  • the arrangement is a regular quadrilateral having a dimension P of one side or an arrangement substantially close to a regular quadrilateral,
  • a regular quadrilateral is a regular quadrilateral with its diagonals in the vertical and horizontal directions.
  • first raised portions 30 are configured such that their top planes 30a are in contact with each other in the first heat exchange chamber 15.
  • the diameter D1 of the top plane 30a of one first ridge 30 out of the first ridges 30 contacting each other in the first heat exchange chamber 15 is the top plane of the other first ridge 30. It is configured to be appropriately smaller than the diameter D2 of 30a, thereby reducing the reduction of the heat transfer area as much as possible by contacting the top planes 30a of the first raised portions 30 with each other. .
  • each of the heat transfer plates 12 includes an entire portion of the heat transfer plate 12 on the inner side of the second seal body 14.
  • a plurality of second raised portions 31 formed by bulging and deforming a portion between the raised portions 30 toward the inside of the second heat exchange chamber 16 are provided in an arrangement with appropriate intervals in the vertical direction and the horizontal direction. Yes.
  • each of the second raised portions 31 is based on a cone having a bottom surface with a diameter D0, and the top of the cone is parallel to the bottom surface of the cone. Since it is in the shape of a truncated cone having a height H formed by cutting so as to form a plane 31a, and located in a region between the first raised portions 30, the arrangement is Similar to the first raised portion 30, it is a regular quadrilateral with a dimension P of one side or an array substantially close to a regular quadrilateral, and this regular quadrilateral is a regular quadrilateral whose diagonal is up and down and left and right. It is a shape.
  • each of the second raised portions 31 is configured such that the flat surface 31a at the top thereof is in contact with each other in the second heat exchange chamber 16.
  • the diameter D1 of the top flat surface 31a of one second raised portion 31 of the second raised portions 31 that are in contact with each other in the second heat exchange chamber 16 is equal to that of the second raised portion 31.
  • the size is appropriately smaller than the diameter D2 of the top flat surface 31a, and thus, the reduction of the heat transfer area due to the contact of the top flat surfaces 31a of the second raised portions 31 with each other is minimized. ing.
  • the upper and lower connecting pieces 21a are left in the horizontally long steam outlets 21 so that the steam inlets 21 have a horizontally long shape. In this configuration, the strength of the heat transfer plate 12 is prevented from being reduced.
  • the liquid to be evaporated such as water supplied from the liquid supply pipe 27 to be evaporated in the supporting fixed face plate 17 enters the liquid to be evaporated inlet 22 and passes through the small hole 25 from the liquid to be evaporated inlet 22.
  • the first heat exchange chamber 15 enters the bottom.
  • the liquid to be evaporated is directed upward from below as indicated by an arrow A while boiling and evaporating in the first heat exchange chamber 15 on both the left and right sides by heating by heat transfer from each second heat exchange chamber 16. Then, after a part of the state changes to steam, it reaches the upper horizontally long steam outlet 21 and exits from the steam outlet pipe 26 in the supporting fixed face plate 17.
  • the first raised portions 30 projecting into the first heat exchange chambers 15 are in the shape of truncated cones, and a large number of them are regular quadrilaterals whose diagonals are up and down and left and right. Due to the arrangement, the steam flowing upward in the first heat exchange chamber 15 as indicated by the solid arrow A in FIG. 8 is arranged in a direction perpendicular to the flow direction. Of each of the first ridges 30 on the upstream side of the first ridges 30 are divided into two flows on the left and right sides. Since it flows while repeatedly dividing into two left and right flows when it hits each first raised portion 30 located between them, the flow resistance caused by friction with the wall surface in the steam can be greatly reduced. The flow is left Widened greatly direction is reliably dispersed throughout the first heat exchange chamber 15.
  • the small holes 25 for introducing the liquid to be evaporated into the first heat exchange chambers 15 regulate the amount of the liquid to be evaporated introduced into the first heat exchange chambers 15 with the small holes 25. As a result, regardless of the difference or fluctuation of other conditions, the first heat exchange chamber 15 is kept the same and uniform, and the evaporation is made uniform.
  • the heating fluid flows from the heating fluid inlet 23 and flows in the left-right direction as shown by arrow B, and then the heating fluid Exit from fluid outlet 24.
  • the second raised portions 31 protruding into the respective second heat exchange chambers 16 are in the shape of truncated cones, and many of them are regular quadrilaterals whose diagonals are up and down and left and right. Due to the arrangement, the heating fluids flowing in the left-right direction in the folded fluid passage as shown by arrow B in FIG. 8 are arranged in a row perpendicular to the flow direction. Of these, the upper and lower flows are divided into two upper and lower flows, and each of the upper and lower flows is divided between the second raised portions 31 on the upstream side of the upstream side.
  • the flow is further divided into two parts, the upper and lower parts, so that the flow is made up and down under the condition that the flow resistance caused by the friction with the wall surface can be reduced. Large and wide in the direction It is to be securely dispersed throughout the second heat exchange chamber 16.
  • each of the first heat exchange chambers 15 a plurality of first raised portions 30 provided on the heat transfer plate 12 forming both sides thereof are in contact with each other, while in each of the second heat exchange chambers 16, Since a plurality of second raised portions 31 provided on the heat transfer plates 12 forming both sides thereof are in contact with each other, the heat transfer plates 12 can be supported with each other.
  • each of the first raised portion 30 and the second raised portion 31 is obtained by bulging and deforming the heat transfer plate 12 into the shape of a truncated cone. Heat transfer area can be increased.
  • the one side dimension P in the regular quadrilateral of the arrangement is 20 to 23 mm, and the diameter of the bottom surface in the truncated cone. It was preferable to set D0 to 9-12 mm.
  • the said 1st Embodiment was a case where the 1st protruding part 30 and the 2nd protruding part 31 which protrude in the said 1st heat exchange chamber 15 were made into the shape of the truncated cone.
  • the present invention is not limited to this, and the first and second raised portions 30 'and second raised portions in which the first raised portion and the second raised portion have the shape of a truncated regular quadrangular pyramid as in the modification shown in FIG.
  • first raised portion 30 ′ and the second raised portion 31 ′ of this modification are cut out so that the top of the regular quadrangular pyramid is parallel to the bottom of the regular quadrangular pyramid, based on the regular quadrangular pyramid.
  • each of the side faces of the truncated regular square pyramid is inclined with respect to the vertical direction and the horizontal direction.
  • each side surface of the truncated regular square pyramid is indicated by an arrow A in FIG. It is configured to incline with respect to both the vertical flow and the horizontal flow indicated by arrow B, that is, the diagonal direction of the truncated regular square pyramid is configured to be the vertical direction and the horizontal direction. It is preferable that the flow can be broadened in the transverse direction with respect to the flow direction in a state where the flow resistance can be further reduced.
  • first raised portion and the second raised portion can be formed into the shape of a truncated regular pyramid such as a truncated regular hexagonal pyramid or a truncated regular octagonal pyramid.
  • Each side surface of the regular pyramid is preferably configured to be inclined with respect to the vertical direction and the horizontal direction.
  • each of the heat transfer plates 1 is provided with the first raised portions 30 and 30 'and the second raised portions 31 and 31', and the heat transfer plate 2 is provided with a truncated cone such as a truncated cone or a truncated regular pyramid.
  • a processing method using a press is employed.
  • the truncated cone height dimension H is set to half the spacing dimension S between the heat transfer plates 12, and the cone angle ⁇ is set to 30 degrees to 120 degrees. Is preferred. In particular, it is more preferable to set 80 degrees to 120 degrees.
  • the workability by pressing the truncated cone and the durability of the press die are improved as the cone angle ⁇ is increased.
  • the cone angle ⁇ exceeds 120 degrees, the truncated cone is configured.
  • the cone angle ⁇ should be set within a range of 30 to 120 degrees in consideration of these points.
  • the first raised portions 30, 30 'and the second raised portions 31, 31' are arranged in the shape of a truncated cone and a regular quadrilateral as described above.
  • the side dimension P in the regular quadrilateral of the array is set to 3 to 8 times the distance dimension S between the heat transfer plates 12, while the top plane of the truncated cone
  • the diameters D1 and D2 at 30a, 30a ′, 31a, and 31a ′ are preferably set to be 1/2 to 3 times the space dimension S between the heat transfer plates 2, and in particular, 1 of the space dimension S. More preferably, the ratio is from / 2 to 1.5 times.
  • the pitch interval along the column direction perpendicular to the flow is widened. Is less effective, and when the one-side dimension P is less than three times the spacing dimension S, the pitch interval along the column direction perpendicular to the flow becomes narrow, so that the flow is dispersed. Although the effect of is high, the flow resistance is greatly increased.
  • the top planes 30a, 30a ', 31a, 31a' are for ensuring that they are always in contact with each other against a shift in a direction parallel to the heat transfer surface of each heat transfer plate 12.
  • the minimum value in the diameter dimensions D1 and D2 should be 1 ⁇ 2 times the spacing dimension S. However, if the diameter dimensions D1 and D2 exceed 3 times the spacing dimension S, the above-described values are Since the diameter at the bottom of the truncated cone is remarkably increased and the flow resistance is increased, the diameter dimensions D1 and D2 are 1 ⁇ 2 to 3 times the distance dimension S in consideration of these points. Should have been set within the range.
  • FIGS. 11 to 17 show a plate heat exchanger 110 used as a condenser according to a second embodiment of the present invention.
  • This plate type heat exchanging device 110 is basically composed of a large number of heat transfer plates 120 made of a relatively thin metal plate in the form of a horizontally long rectangle, like the plate type heat exchanging device 11 of the first embodiment.
  • a plurality of first seal members 130 are hermetically sealed by the first seal member 130 by laminating the sheets so that the first seal member 130 and the second seal member 140 alternately serving as spacers are alternately sandwiched between them.
  • a heat exchange chamber 150 and a plurality of second heat exchange chambers 160 each having a sealed periphery with the second seal body 140 are alternately formed, and this laminated body is disposed on one end surface thereof for support.
  • the fixed face plate 170 and the movable face plate 180 disposed on the other end face are fastened to each other in the stacking direction by a plurality of bolts 190, while the heat transfer plates 120 and the movable face plate 180 are fixed to the supporting fixed face plate 170. And a configuration that is supported in a state of movable in stacking direction at the guide rod 200.
  • each of the heat transfer plates 120 has a steam inlet 210 formed in a horizontally long shape in the upper side portion, and one of the left and right corners in the lower side.
  • Condensed liquid outlet 220 is drilled in the corner of each, and cooling fluid inlet 230 and cooling fluid outlet 240 are drilled side by side in the part of one of the left and right sides. .
  • the first seal body 130 that forms the periphery of each of the first heat exchange chambers 150 includes seal pieces 130a and 130b that surround the cooling fluid inlet 230 and the cooling fluid outlet 240.
  • seal pieces 130a and 130b that surround the cooling fluid inlet 230 and the cooling fluid outlet 240 are provided integrally, and the horizontally long steam inlet 210 communicates with the upper portion of each first heat exchange chamber 150 and the condensate liquid outlet 220 communicates with the lower portion.
  • the cooling fluid inlet 230 and the cooling fluid outlet 240 is configured not to communicate with the first heat exchange chamber 150.
  • condensed liquid outlet 220 communicating with the lower part in each first heat exchange chamber 150 can be provided at the other corner of the lower side.
  • the second seal body 140 that forms the periphery of each of the second heat exchange chambers 160 has seal pieces 140 a and 140 b that surround the vapor inlet 210 and the condensed liquid outlet 220.
  • the cooling fluid inlet 230 and the cooling fluid outlet 240 communicate with one side of each of the second heat exchange chambers 160, and the vapor inlet 210 and the condensed liquid outlet 220 are connected to the second heat exchange chamber.
  • the interior of the chamber 160 is not communicated.
  • the second seal body 140 is integrally provided with a partition member 140c that integrally extends in a left-right direction from a portion between the cooling fluid inlet 230 and the cooling fluid outlet 240.
  • a folded fluid passage is formed that is folded in the left-right direction from the cooling fluid inlet 230 toward the cooling fluid outlet 240.
  • the outer surface of the supporting fixed face plate 170 has a steam inlet pipe 260 communicating with the steam inlet 210, a condensed liquid outlet pipe 270 communicating with the condensed liquid outlet 220, and a cooling communicating with the cooling fluid inlet 230.
  • a cooling fluid supply pipe 280 and a cooling fluid outlet pipe 290 communicating with the cooling fluid outlet 240 are connected.
  • each heat transfer plate 120 is formed by bulging and deforming the heat transfer plate 120 into the shape of a truncated cone so as to protrude into the first heat exchange chamber 150, as shown in FIG.
  • a large number of first raised portions 300 are provided in an arrangement with appropriate intervals in the vertical and horizontal directions, and the first raised portions 300 are configured such that the top surfaces of the first raised portions 300 are in contact with each other in the first heat exchange chamber 150.
  • the regular quadrilateral of the array is a regular quadrilateral whose diagonal is up and down and left and right.
  • each heat transfer plate 120 is provided with a portion of the heat transfer plate 120 between the first raised portions 300 so as to protrude into the second heat exchange chamber 160.
  • a plurality of second raised portions 310 bulging and deforming into the shape of a head cone are provided in an array with appropriate spacing in the vertical and horizontal directions, and the top surface of the second raised portion 310 is the second flat portion.
  • the regular quadrilaterals that are in contact with each other in the heat exchange chamber 160 and that are arranged in the heat exchange chamber 160 are regular quadrilaterals whose diagonals are up and down and left and right.
  • This steam flows through the first heat exchange chamber 150 from the top to the bottom as shown by the arrow A ′ while condensing by cooling by heat transfer to each second heat exchange chamber 160 on both the left and right sides. After condensing into the liquid, it reaches the condensed liquid outlet 220 at the bottom and exits from the condensed liquid outlet pipe 270 in the supporting fixed face plate 170.
  • the first raised portions 300 protruding into the first heat exchange chambers 150 are in the shape of truncated cones, and many of them are regular quadrilaterals whose diagonals are up and down and left and right. Due to the arrangement, the steam flowing downward in the first heat exchange chamber 150 as indicated by the solid arrow A ′ in FIG. 13 is perpendicular to the flow direction.
  • the left and right flows are divided into two left and right flows when hitting each of the first ridges 300 located on the upstream side in the row, and each of the two divided right and left flows is downstream of the first ridges 300 on the upstream side. Since it flows while repeatedly dividing into two left and right flows when hitting each first ridge 300 located between the two, the flow can be reliably dispersed throughout the first heat exchange chamber 150.
  • the cooling fluid flows in from the cooling fluid inlet 230 and flows in the left-right direction as indicated by the arrow B ', and then cooled. Go out from the fluid outlet 240.
  • the second raised portions 310 protruding into the respective second heat exchange chambers 160 are in the shape of truncated cones, and many of them are regular quadrilaterals whose diagonals are up and down and left and right. Due to the arrangement, the cooling fluid flowing in the left-right direction in the folded fluid passage as indicated by arrow B ′ in FIG. 14 is arranged in a direction perpendicular to the flow direction.
  • the upper and lower flows are divided into two upper and lower flows on the upstream side, and each of the upper and lower flows is separated from the upstream side of the second raised portions 310 on the upstream side. Since it flows while repeatedly dividing into two separate upper and lower flows when it hits each second raised portion 310 positioned between them, the flow can be reliably dispersed throughout the second heat exchange chamber 160.
  • first raised portion 300 and the second raised portion 310 can be configured as a truncated pyramid such as a truncated quadrangular pyramid as shown in FIG.
  • size, shape, and arrangement of the first raised portion 300 and the second raised portion 310 are the same as those in the first embodiment.
  • [Third Embodiment] 18 to 20 show a third embodiment.
  • the “plate type heat exchange device 11 as an evaporator” of the first embodiment shown in FIGS. 1 to 10 is folded into each second heat exchange chamber 16.
  • the “partition member 14c” for defining the fluid passage is modified, and other configurations are the same as those in the first embodiment.
  • the partition member 14c is separated from the second seal body 14 that seals the periphery of the second heat exchange chamber 16, and is long with a small diameter D by a soft elastic body such as heat-resistant rubber.
  • a long string-like body 14c ' is formed, and the string-like body 14c' is formed in a concave groove 12a provided in both heat transfer plates 12 forming a part of the diameter direction on both sides of the second heat exchange chamber 16. In this state, the two heat transfer plates 12 are sandwiched while being elastically deformed.
  • plate-like pieces 14c ′′ having a width W larger than the diameter D of the string-like body 14c ′ are integrally provided at a plurality of locations along the longitudinal direction of the string-like body 14c ′.
  • the plate-like piece 14c ′′ is configured to be bonded to one of the heat transfer plates 12 using an adhesive or a double-sided adhesive tape.
  • the figure shows a case where the string-like body 14c ′ is configured to fit into the recessed grooves 12a of the two heat transfer plates 12, but this string-like body 14c ′ is not attached to the string-like body 14c ′.
  • the provided plate-like piece 14c ′′ can be configured to be fitted only in the recessed groove 12a in one heat transfer plate 12.
  • the string-like body 14c ′ is attached to one heat transfer plate with an adhesive or You may make it adhere
  • the heat transfer area can be increased by the amount of the partition member 14c formed by the string-like body 14c ′ having a small diameter D.
  • the plate-like piece 14c ′′ provided integrally with the string-like body 14c ′. This can be reliably prevented by adhesion to one heat transfer plate 12.
  • the “plate type heat exchange device 110 as a condenser” of the second embodiment shown in FIGS. 11 to 17 is folded into each second heat exchange chamber 160.
  • the “partition member 140c” for defining the fluid passage is modified, and other configurations are the same as those of the second embodiment.
  • the partition member 140c is separated from the second seal body 140 that seals the periphery of the second heat exchange chamber 160, and is long with a small diameter D by a soft elastic body such as heat-resistant rubber.
  • a long string-like body 140c ′ is formed, and the string-like body 140c ′ is formed in a concave groove 120a provided in both heat transfer plates 120 that form part of the diameter direction of both sides of the second heat exchange chamber 160. In this state, the two heat transfer plates 120 are sandwiched while being elastically deformed.
  • plate-like pieces 140c ′′ having a width W larger than the diameter D of the string-like body 140c ′ are integrally provided at a plurality of locations along the longitudinal direction of the string-like body 140c ′.
  • the plate-like piece 140c ′′ is configured to be bonded to one of the heat transfer plates 120 using an adhesive or a double-sided adhesive tape.
  • the string-like body 140c ′ is configured to fit into the recessed grooves 120a of the two heat transfer plates 120
  • the string-like body 140c ′ is connected to the string-like body 140c ′.
  • the provided plate-like piece 140c ′′ can be configured to be fitted only in the recessed groove 120a in one heat transfer plate 120 to be bonded.
  • the string-like body 140c ′ can be bonded to one heat transfer plate with an adhesive or You may make it adhere
  • the heat transfer area can be increased by the amount of the partition member 140c formed as the string-shaped body 140c ′ having a small diameter D.
  • the plate-like piece 140c ′′ provided integrally with the string-like body 140c ′. This can be reliably prevented by adhesion to one heat transfer plate 120.

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

Abstract

L'invention porte sur un échangeur de chaleur à plaque, dans lequel une pluralité de plaques de transfert de chaleur (12) sont empilées d'une manière telle qu'une pluralité de premières chambres d'échange de chaleur (15) et une pluralité de secondes chambres d'échange de chaleur sont formées de façon alternée entre les plaques de transfert de chaleur, et de la vapeur est générée ou condensée dans les premières chambres d'échange de chaleur. Une capacité d'évaporation lorsque de la vapeur est générée ou une capacité de condensation lorsque la vapeur est condensée est accrue dans l'échangeur de chaleur. Un grand nombre de premières parties surélevées (30) d'une forme tronconique se projetant dans la première chambre d'échange de chaleur (15) et un grand nombre de secondes parties surélevées (31) d'une forme tronconique se projetant dans la seconde chambre d'échange de chaleur (16) sont disposés sur chaque plaque de transfert de chaleur (12). Les premières parties surélevées (30) sont amenées en contact les unes avec les autres dans la première chambre d'échange de chaleur (15), et les secondes parties surélevées (31) sont amenées en contact les unes avec les autres dans la seconde chambre d'échange de chaleur (16).
PCT/JP2009/062943 2008-07-29 2009-07-17 Échangeur de chaleur à plaque utilisé comme évaporateur ou condenseur WO2010013608A1 (fr)

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JP2010502108A JPWO2010013608A1 (ja) 2008-07-29 2009-07-17 蒸発器又は凝縮器として使用されるプレート型熱交換装置

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JP2008195063 2008-07-29
JP2008-195063 2008-07-29

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JP2012107803A (ja) * 2010-11-17 2012-06-07 Toyota Industries Corp 熱交換器
FR2979983A1 (fr) * 2011-09-13 2013-03-15 Valeo Systemes Thermiques Echangeur thermique et procede de realisation d'un tel echangeur thermique
CN107782179A (zh) * 2016-08-25 2018-03-09 杭州三花研究院有限公司 板式换热器
EP3734209A1 (fr) 2019-04-30 2020-11-04 Alfa Laval Corporate AB Échangeur thermique à plaque pour le traitement d'un aliment, plaque pour échangeur de chaleur à plaques pour le traitement d'un aliment, joint destiné à être utilisé avec la plaque d'échangeur de chaleur et procédé de fabrication d'un échangeur de chaleur pour le traitement d'un aliment
EP3738657A1 (fr) 2019-05-16 2020-11-18 Alfa Laval Corporate AB Échangeur de chaleur à plaques, plaque d'échange de chaleur et procédé de traitement d'un flux tel que de l'eau de mer
WO2021180680A1 (fr) * 2020-03-12 2021-09-16 Sgl Carbon Se Échangeur de chaleur à plaques
EP4109026A1 (fr) 2021-06-24 2022-12-28 Alfa Laval Corporate AB Agencement de joint d'étanchéité, plaque de transfert de chaleur, kit, ensemble, échangeur de chaleur et procédé
CN116146970A (zh) * 2023-04-24 2023-05-23 厦门铭光能源科技有限公司 一种焊接式板式省煤器

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CN103424025A (zh) * 2012-05-15 2013-12-04 杭州三花研究院有限公司 板式换热器及其板片
ES2714527T3 (es) * 2013-10-14 2019-05-28 Alfa Laval Corp Ab Placa para un intercambiador de calor e intercambiador de calor
CN108062152B (zh) * 2017-12-25 2020-05-08 奇鋐科技股份有限公司 散热水排结构
JP6506865B1 (ja) * 2018-03-14 2019-04-24 栗田工業株式会社 蒸気の凝縮方法
DK3792581T3 (da) * 2019-09-13 2023-04-17 Alfa Laval Corp Ab Pladevarmeveksler til behandling af en væsketilførsel
CN114688897A (zh) * 2020-12-31 2022-07-01 浙江三花汽车零部件有限公司 一种换热器

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Cited By (14)

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Publication number Priority date Publication date Assignee Title
JP2012107803A (ja) * 2010-11-17 2012-06-07 Toyota Industries Corp 熱交換器
FR2979983A1 (fr) * 2011-09-13 2013-03-15 Valeo Systemes Thermiques Echangeur thermique et procede de realisation d'un tel echangeur thermique
WO2013037469A1 (fr) * 2011-09-13 2013-03-21 Valeo Systemes Thermiques Echangeur thermique et procede de realisation d'un tel echangeur thermique
US11346612B2 (en) * 2016-08-25 2022-05-31 Zhejiang Sanhua Intelligent Controls Co., Ltd. Plate heat exchanger
CN107782179A (zh) * 2016-08-25 2018-03-09 杭州三花研究院有限公司 板式换热器
EP3734209A1 (fr) 2019-04-30 2020-11-04 Alfa Laval Corporate AB Échangeur thermique à plaque pour le traitement d'un aliment, plaque pour échangeur de chaleur à plaques pour le traitement d'un aliment, joint destiné à être utilisé avec la plaque d'échangeur de chaleur et procédé de fabrication d'un échangeur de chaleur pour le traitement d'un aliment
WO2020221732A1 (fr) 2019-04-30 2020-11-05 Alfa Laval Corporate Ab Échangeur de chaleur à plaques de traitement de l'alimentation
EP3738657A1 (fr) 2019-05-16 2020-11-18 Alfa Laval Corporate AB Échangeur de chaleur à plaques, plaque d'échange de chaleur et procédé de traitement d'un flux tel que de l'eau de mer
WO2020229162A1 (fr) 2019-05-16 2020-11-19 Alfa Laval Corporate Ab Échangeur de chaleur à plaques, plaque d'échange de chaleur et procédé de traitement d'une matière première telle que de l'eau de mer
WO2021180680A1 (fr) * 2020-03-12 2021-09-16 Sgl Carbon Se Échangeur de chaleur à plaques
EP4109026A1 (fr) 2021-06-24 2022-12-28 Alfa Laval Corporate AB Agencement de joint d'étanchéité, plaque de transfert de chaleur, kit, ensemble, échangeur de chaleur et procédé
WO2022268617A1 (fr) 2021-06-24 2022-12-29 Alfa Laval Corporate Ab Agencement de joint d'étanchéité, plaque de transfert de chaleur, kit, ensemble, échangeur de chaleur et procédé
CN116146970A (zh) * 2023-04-24 2023-05-23 厦门铭光能源科技有限公司 一种焊接式板式省煤器
CN116146970B (zh) * 2023-04-24 2023-07-25 厦门铭光能源科技有限公司 一种焊接式板式省煤器

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