WO2013022072A1 - 多管式熱交換器 - Google Patents

多管式熱交換器 Download PDF

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Publication number
WO2013022072A1
WO2013022072A1 PCT/JP2012/070381 JP2012070381W WO2013022072A1 WO 2013022072 A1 WO2013022072 A1 WO 2013022072A1 JP 2012070381 W JP2012070381 W JP 2012070381W WO 2013022072 A1 WO2013022072 A1 WO 2013022072A1
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WO
WIPO (PCT)
Prior art keywords
cooling medium
heat transfer
tube
casing
heat exchanger
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2012/070381
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English (en)
French (fr)
Japanese (ja)
Inventor
滝川　一儀
宮内　祐治
忠弘 後藤
一真 滝川
豪孝 伊藤
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Usui Kokusai Sangyo Kaisha Ltd
Original Assignee
Usui Kokusai Sangyo Kaisha Ltd
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Publication of WO2013022072A1 publication Critical patent/WO2013022072A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
    • F02M26/32—Liquid-cooled heat exchangers
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels

Definitions

  • the present invention relates to a heat recovery from engine exhaust gas or a multi-tube heat exchanger that cools EGR gas with a liquid cooling medium such as cooling water of a diesel engine or a gasoline engine.
  • Patent Documents 1 to 5 the following EGR gas cooling devices (Patent Documents 1 to 5) have been proposed.
  • both ends of the trunk tube 201 provided with the cooling medium inlet 201-1a and the cooling medium outlet 201-2a at both ends are provided.
  • the heat transfer tube group 202 is fixedly arranged on the tube sheet 203 fixed to the tube tube, and end caps 204 are fixed to both ends of the trunk tube 201.
  • the end cap 204 has an EGR gas inlet 204-1 and An outlet 204-2 is provided, and a multi-tube having a structure in which a fastening flange 205 is fitted and fixed to an EGR gas inlet 204-1 of the end cap 204 and an outer opening end of the outlet 204-2.
  • the EGR gas cooling device provided with an inclination with respect to the vertical line with respect to the axis of Dokan 201 to flow along the tube sheet 203 is shown.
  • Patent Document 2 as schematically shown in FIGS. 43 and 44, a plurality of flat tubes 212, a case 213 formed so as to surround the outer periphery of the flat tubes 212, and the case 213 Header plates (tube sheets) 214 provided at both ends of each flat tube, and between the exhaust gas flowing through the flat tube 212 and the cooling water flowing through the case 213
  • the EGR cooler 211 is configured to perform heat exchange with the cooling water supply chamber 215 in which the base end 221 is connected to the case 213 and the cooling water inlet pipe 216 is connected to the tip 220.
  • the cooling water supply chamber 215 has a shape that gradually becomes wider from the distal end portion 220 toward the proximal end portion 221, and the width of the proximal end portion 221 is substantially equal to the width of the case 213. It is formed on so that, at the other end of the case 213 is illustrated EGR cooler cooling water outlet pipe 222 is provided.
  • 217 is an end cap
  • 218 is a fastening flange.
  • the heat exchanger for an EGR cooler in which high-temperature EGR gas is passed through the interior of 232 and heat is exchanged through the cooling water to the outside two or more cooling water inlets 231-1 for introducing cooling water into the shell 231 are provided.
  • An EGR cooler heat exchanger is shown in which one cooling water outlet 231-2 for discharging cooling water from the inside of H.231 is provided, and a cooling water inlet pipe adapter 235 is provided at the cooling water inlet 231-1.
  • reference numeral 231-1a denotes a cooling water inlet pipe
  • 231-2a denotes a cooling water outlet pipe.
  • Patent Document 4 as schematically shown in FIGS. 47 and 48, a hollow shell 241 having a cooling water introduction port 241-1 and a discharge port 241-2, and an EGR arranged inside the shell 241 are disclosed.
  • an EGR cooler 240 having a plurality of flat tubes 242 through which gas passes, a configuration in which an adapter member 243 for introducing cooling water is disposed in a cooling water inlet 241-1 provided in the lower side surface portion 241-3 of the shell 241 The EGR cooler is shown.
  • Patent Document 5 as schematically shown in FIGS. 49 and 50, a hollow shell 251 provided with a cooling water inlet 251-1 and a discharge outlet 251-2, and an EGR arranged inside the shell 251 are disclosed.
  • An EGR cooler 250 including a plurality of flat tubes 252 through which gas passes includes an adapter member 253 that is attached to the cooling water inlet 251-1 and introduces cooling water into the shell 251.
  • the adapter member 253 includes the adapter member 253.
  • An EGR cooler provided with a guide plate 254 that extends from the inside of the member to the inside of the shell 251 and adjusts the inflow direction of the cooling water introduced into the shell 251 from the cooling water introduction port 251-1 is shown.
  • a hollow shell 261 having a cylindrical cooling water inlet pipe 261-1 and a discharge port (not shown), and a shell 261 inside are provided.
  • the EGR cooler 260 includes a plurality of flat tubes 262 through which the EGR gas is disposed, and is a bottomed cylindrical press-molded product joined to the outlet in the shell 261 of the cooling water inlet pipe 261-1.
  • the EGR gas cooling device (FIGS. 41 and 42) described in Patent Document 1 is provided with a plurality of cooling medium inlets 201-1a, so that the overheat area near the tube sheet 203 can be substantially eliminated.
  • the cross-sectional area perpendicular to the inflow direction of the cooling medium inlet 201-1a is substantially equal to the cross-sectional area of the pipe flowing into the cooling medium inlet, and flows from the cooling medium inlet.
  • the EGR cooler heat exchanger (FIGS. 45 and 46) described in Patent Document 3 also flows into the shell 231 from the cooling water inlet 231-1.
  • the cooling water flow is not directional to the inner surface of the end plate (tube sheet) 233, and simply flows in the axial direction of the shell 231 toward the cooling water outlet 231-2a. There is a drawback that the boiling prevention effect cannot be obtained sufficiently.
  • this EGR cooler is limited to a configuration in which the flat heat transfer tubes are arranged vertically so that the longitudinal direction of the flat heat transfer tubes faces the vertical direction, and the flat heat transfer tubes are horizontally arranged and stacked.
  • an EGR cooler having a structure there is a difficulty that it is difficult to obtain an effect of preventing local boiling of cooling water.
  • the cooling water flowing into the shell 261 from the cylindrical cooling water inlet pipe 261-1 is the shell of the cooling water inlet pipe 261-1.
  • the cylindrical cooling water inlet pipe is discharged toward the vicinity of the end plate 264 on the gas inlet side by the bottomed cylindrical attachment 261-2 joined to the outlet in the H.261 and diffused to the left and right.
  • the present invention has been made to solve the above-described problems of the conventional multi-tube heat exchanger, and in particular, in a multi-tube heat exchanger in which the heat transfer tube group is constituted by flat tubes, the heat transfer tube group is introduced into a case or a shell.
  • the cooling water flow is inclined with respect to the vertical line with respect to the axis of the casing, and the directivity and speed-up property on the inner surface of the tube sheet (end plate) are further increased to increase the cooling medium on the exhaust gas (EGR gas) inlet side.
  • An object of the present invention is to provide a multitubular heat exchanger that can sufficiently enhance the boiling prevention effect.
  • a multitubular heat exchanger includes a plurality of stacked flat heat transfer tubes, a casing formed so as to surround an outer periphery of the flat heat transfer tubes, and both ends of the casing.
  • a multi-tubular heat exchanger that exchanges heat between the exhaust gas that circulates in the flat heat transfer tube and the cooling medium that circulates in the casing.
  • a cooling medium distributor having a cooling medium inflow pipe connected to a base end portion in a direction substantially perpendicular to the casing longitudinal direction in the vicinity of the exhaust gas inlet side end of the casing.
  • a nozzle member having a plurality of ejection holes in a direction substantially perpendicular to the longitudinal direction of the casing so that the jet velocity of the cooling medium is increased from the inside of the cooling medium distributor.
  • the sum of the cross-sectional area of the injection holes is characterized in that less than the flow direction the cross-sectional area of the cooling medium in the cooling medium distributor.
  • a multi-tube heat exchanger is provided with a plurality of stacked flat heat transfer tubes, a casing formed so as to surround the outer periphery of the flat heat transfer tubes, and both ends of the casing, And a tube sheet in which both ends of the flat heat transfer tube are penetrated, and a multi-tube heat of a system for exchanging heat between the exhaust gas flowing through the flat heat transfer tube and the cooling medium flowing through the casing
  • a cooling medium inflow pipe connected to the cooling medium distributor, wherein the cooling medium distributor flows the cooling medium flowing into the casing along the inner surface of the tube sheet on the exhaust gas inlet side.
  • a nozzle member provided with a plurality of ejection holes so as to increase the flow velocity of the cooling medium from the inside of the cooling medium distributor.
  • the sum of the sectional areas of the ejection holes is smaller than the sectional area in the flow direction of the cooling medium in the cooling medium distributor.
  • the cooling medium distributor is installed in an inclined manner as stipulated that the cooling medium distributor is provided in an inclined manner with respect to a vertical line with respect to the axis of the casing.
  • the cooling medium distributor should be configured to be parallel (perpendicular to the axis) to the axis perpendicular to the axis of the casing or in the opposite direction to the exhaust gas inlet.
  • this type of multi-tube heat exchanger is provided with a plurality of stacked flat heat transfer tubes, a casing formed so as to surround the outer periphery of the flat heat transfer tubes, and both ends of the casing.
  • a cooling medium distribution wherein a base end portion is connected to an opening portion having a long hole provided in an end portion on the exhaust gas inlet side of the casing in a direction substantially perpendicular to the longitudinal direction of the casing so as to cover the opening portion
  • a cooling medium inflow pipe connected to the cooling medium distributor, and the cooling medium distributor is parallel (perpendicular to the axis) to the axis of the casing or to the exhaust gas inlet side.
  • a nozzle member having a plurality of ejection holes is provided in the vicinity of the opening so that the ejection velocity of the cooling medium is increased from the inside of the cooling medium distributor, and the sum of the sectional areas of the ejection holes is the cooling medium.
  • the axial center of the ejection hole is smaller than the cross-sectional area in the flow direction of the cooling medium in the distributor and the exhaust medium flows so that the cooling medium flowing into the casing flows along the inner surface of the tube sheet on the exhaust gas inlet side. It is directed to the inner surface of the tube sheet on the inlet side.
  • the axis of the ejection hole is directed to (a) the inner surface of the tube sheet on the exhaust gas inlet side, and (b) a space between the laminated flat heat transfer tubes or flat transmission. Any one of directing the space between the heat tube and the inner surface of the casing is a preferred mode.
  • the nozzle member is provided in either the cooling water distributor or the casing.
  • the nozzle member preferably has a convex portion that protrudes continuously in the stacking direction of the heat transfer tubes on the heat transfer tube side and has the ejection holes on the wall surface.
  • the present invention may further include a protrusion in a space between the flat heat transfer tubes and / or a space between the flat heat transfer tube and the casing inner surface where the convex portions are stacked, It is a preferred embodiment that the holes are provided.
  • the nozzle member is also directed to the space between the flat heat transfer tubes in which the shaft cores are laminated or the space between the flat heat transfer tube and the casing inner surface, and to the tube sheet inner surface on the exhaust gas inlet side. It is preferable to provide a plurality of outflow holes that are not to be provided, or to provide ejection holes and / or outflow holes having different cross-sectional areas. Furthermore, it is preferable that the nozzle member has an ejection hole and / or an outflow hole that are continuously arranged in a substantially straight line substantially parallel to the stacking direction of the heat transfer tubes.
  • the nozzle member is provided with a convex portion continuously projecting in the laminating direction of the heat transfer tube on the flat heat transfer tube side, and has the ejection holes on the side wall surface of the tube sheet of the convex portion.
  • An outlet hole is provided in the wall surface, and the axial cross-sectional shape of the casing of the convex portion protruding continuously in the laminating direction of the heat transfer tube on the flat heat transfer tube side of the nozzle member is V-shaped,
  • a preferred embodiment is one of an inverted trapezoidal shape having a flat portion, a U shape, and an arc shape.
  • a cooling medium guide member is provided in the cooling medium distributor or the nozzle member or the inner wall of the casing, and the guide member is a space portion or a flat portion between the stacked flat heat transfer tubes. It is a preferable aspect to have an extending portion extending in a space between the heat transfer tube and the inner surface of the casing.
  • the guide member of the said cooling medium makes it a preferable aspect that the length of a guide part differs in the lamination direction of a flat heat exchanger tube.
  • a nozzle bush or a nozzle tube is attached to the ejection hole provided in the nozzle member, and the ejection hole is a circle or an ellipse or an ellipse having a major axis in the axial direction of the flat heat transfer tube. It is a preferred embodiment.
  • the opening provided in the casing is provided substantially parallel to the laminating direction of the flat heat transfer tubes.
  • the present invention provides cooling that causes the cooling medium to flow toward the inner surface of the tube sheet at a higher speed as a means for sufficiently enhancing the boiling prevention action of the cooling medium on the exhaust gas (EGR gas) inlet side of the multi-tube heat exchanger.
  • the multitubular heat exchanger according to the present invention has the following effects. 1.
  • the cooling medium distributor preferably inclined with respect to the vertical line with respect to the axis of the casing, the cooling medium flows in the tube sheet inner surface on the exhaust gas inlet side and flows into the casing. Since the cooling medium flows along the inner surface of the tube sheet on the exhaust gas inlet side, boiling of the cooling medium near the inner surface of the tube sheet can be more effectively prevented.
  • a plurality of jet holes having a total cross-sectional area smaller than the cross-sectional area in the flow direction of the cooling medium in the cooling medium distributor are substantially the same as the longitudinal direction of the casing of the multitubular heat exchanger.
  • the inflow speed of the cooling medium is increased, and a larger cooling medium boiling prevention effect near the inner surface of the tube sheet can be obtained.
  • a larger cooling medium boiling prevention effect near the inner surface of the tube sheet can be obtained.
  • a cooling medium guide member is provided in the vicinity of the ejection hole, and a cooling medium jet from the ejection hole is caused to follow the surface of the guide member, so that the cooling medium is placed between the inner surface of the tube sheet and / or between each flat heat transfer tube. Since it can be accurately guided to the space, it is possible to further enhance the cooling medium boiling prevention action in the vicinity of the inner surface of the tube sheet. 6). Even if the cooling medium distributor is inclined parallel to the vertical line to the casing axis or in the opposite direction (exhaust gas inlet side), the plurality of ejection holes provided in the nozzle member are directed to the tube sheet side.
  • the cooling medium flows into the tube sheet inner surface in the same manner as described above, and the cooling medium flowing into the casing flows along the tube sheet inner surface on the exhaust gas inlet side. Coolant boiling near the inner surface can be prevented. 7). Since the EGR gas temperature rises and the gas flow rate increases during high-load operation of the engine, the phenomenon of boiling of the cooling medium occurs not only from the inner surface of the tube sheet but also from the outer surface of the flat heat transfer tube. An ejection hole and / or an outflow hole having an area are provided, or a convex portion continuously projecting in the stacking direction of the heat transfer tubes is provided on the heat transfer tube side of the nozzle member, and the ejection holes are formed on the tube sheet side wall surface of the convex portion.
  • the axial cross-sectional shape of the casing of the nozzle member convex portion is V-shaped, inverted trapezoidal shape having a flat portion at the bottom, U-shaped, or arc-shaped With this shape, it is possible to reliably prevent boiling in a wide range slightly along the flow direction of the EGR gas from the vicinity of the tube sheet even during high load operation. 8).
  • the length of the guide part of the guide member so as to differ in the laminating direction of the flat heat transfer tubes, even if there is a flat flow in the EGR gas flow, the tube sheet inner surface, the flat heat transfer tube from the tube sheet side outer surface The boiling of the cooling medium can also be effectively prevented.
  • the multi-tubular heat exchanger of the present invention by providing means for providing the cooling medium distributor for flowing the cooling medium toward the inner surface of the tube sheet at a higher speed, the cooling medium can be increased.
  • the cooling medium Since it can be accurately guided not only to the inner surface of the tube sheet but also to the space between the flat heat transfer tubes, the multi-tubular heat exchanger is not limited to the flat heat transfer tubes arranged horizontally, but is arranged horizontally.
  • cooling medium boiling prevention action from the outer surface of each flat heat transfer tube in the vicinity of the inner surface of the tube sheet can be further enhanced, and the deterioration of heat exchange performance due to the boiling of the cooling medium can be prevented.
  • Heat recovery from exhaust gases greatly contributes to the cooling of the exhaust gases, such as EGR gas.
  • FIG. 1 It is a schematic longitudinal cross-sectional view which shows the principal part of the multitubular heat exchanger which concerns on 3rd Example of this invention. It is a perspective view which shows the other example of the nozzle member of the multitubular heat exchanger shown in FIG. It is a schematic longitudinal cross-sectional view which shows the principal part of the multitubular heat exchanger which concerns on 4th Example of this invention. It is a schematic longitudinal cross-sectional view which shows the principal part of the multitubular heat exchanger which concerns on 5th Example of this invention. It is a perspective view which abbreviate
  • FIG. 20 is a longitudinal front view taken along the line AA in FIG.
  • FIG. 20 is an enlarged perspective view in which a part of the guide member of the multitubular heat exchanger shown in FIG. 19 is omitted.
  • FIG. 17 is a view corresponding to FIG.
  • FIG. 28 is a view corresponding to FIG. 12, showing an enlarged main part of the multitubular heat exchanger shown in FIG. 27. It is the FIG. 12 equivalent view which expands and shows the principal part of the multitubular heat exchanger which concerns on 18th Example of this invention. It is FIG. 4 equivalent view which shows the nozzle member of the multitubular heat exchanger which concerns on 19th Example of this invention. It is FIG. 4 equivalent view which shows the nozzle member of the multitubular heat exchanger which concerns on 20th Example of this invention.
  • FIG. 32 is a view corresponding to FIG.
  • FIG. 32 is a view corresponding to FIG. 13 showing a nozzle member of the multi-tube heat exchanger according to the twentieth embodiment shown in FIG. 31.
  • FIG. 13 is an enlarged view corresponding to FIG. 12 showing an enlarged main part of a multitubular heat exchanger according to a twenty-first embodiment of the present invention.
  • FIG. 13 is an enlarged view corresponding to FIG. 12 illustrating an essential part of a multitubular heat exchanger according to a twenty-second embodiment of the present invention.
  • FIG. 36 is a view corresponding to FIG. 13 showing a nozzle member of the multitubular heat exchanger according to the 22nd embodiment shown in FIG. 35.
  • FIG. 13 is an enlarged view corresponding to FIG. 12 showing an enlarged main part of a multitubular heat exchanger according to a twenty-third embodiment of the present invention.
  • FIG. 22 is an enlarged perspective view showing a modification of the guide member of the multitubular heat exchanger according to the eleventh embodiment shown in FIGS. It is a schematic longitudinal cross-sectional view which expands and shows the principal part of the multitubular heat exchanger which concerns on 24th Example of this invention. It is a schematic longitudinal cross-sectional view which expands and shows the principal part of the multitubular heat exchanger which concerns on 25th Example of this invention. It is a schematic plan view which abbreviate
  • FIG. 52 is a schematic horizontal and vertical view of the multitubular heat exchanger shown in FIG. 51.
  • the cooling medium supply sections reference numerals 6, 8, 9 etc.
  • the multi-tube heat exchanger according to the first embodiment of the present invention shown in FIGS. 1 to 4 is preferably a flat heat transfer tube 2 in which a plurality of flat heat transfer tubes 2 having heat transfer fins inserted and fixed therein are arranged side by side.
  • the exhaust gas inflow bonnet 4 is provided at one end of the casing 1, the exhaust gas outflow bonnet 5 is provided at the other end, and a flat transmission is provided at the end of the casing outer peripheral wall on the side of the exhaust gas inflow bonnet 4.
  • a cooling medium inflow opening 6 comprising a substantially rectangular long hole substantially parallel to the stacking direction of the heat pipes 2 is provided, and a cooling medium outflow pipe 7 is connected to an end of the exhaust gas outflow bonnet 5.
  • the cooling medium that has flowed into the casing 1 through the box-shaped cooling medium distributor 8 whose base end (bottom) is opened so as to cover the opening 6 is the exhaust gas.
  • the inclination angle ⁇ of the cooling medium distributor 8 is not particularly limited, but is preferably about 5 to 45 °.
  • This cooling medium distributor 8 has a flange portion 8-1 that covers the opening 6 at the base end, and a cooling medium inflow connected to a cooling medium pipe (not shown) at the end opposite to the base end.
  • a tube 9 is installed in parallel with the outer wall surface of the casing.
  • the cooling medium inflow pipe 9 is provided with a cooling medium inflow port 9-1 having a long hole communicating with the cooling medium distributor 8, and the other end is closed by a cap 9-2.
  • a plurality of ejection holes 10-1 are provided in the vicinity of the opening 6 of the cooling medium distributor 8 so that the jetting speed of the cooling medium is higher than that in the cooling medium distributor 8.
  • a nozzle member 10 having a direction substantially perpendicular to the casing longitudinal direction of the heat exchanger is attached to the inner wall of the casing 1.
  • the nozzle member 10 is formed of a flat plate provided with ejection holes 10-1 at corresponding positions between the flat heat transfer tubes 2 of the flattened heat transfer tube group laminated as shown in FIG. 4, and the ejection holes 10- 1 is smaller than the cross-sectional area in the flow direction of the cooling medium in the cooling medium distributor 8.
  • the reason is that the flow rate of the cooling medium ejected from the ejection hole 10-1 is higher than the flow rate in the cooling medium distributor 8 and is given high kinetic energy, so that By improving the straightness of the flow so as to reach the inner surface of the tube sheet 3 and rapidly moving the high-temperature cooling medium staying in the vicinity of the inner surface, the tube sheet 3 and the tube sheet 3 of the flat heat transfer tube 2 are moved.
  • the shape of the ejection hole 10-1 of the nozzle member 10 may be a perfect circle, an ellipse having a major axis in the axial direction of the flat heat transfer tube 2, or an oval shape.
  • the cooling medium flows from the cooling medium inflow pipe 9 through the cooling medium distributor 8, the opening 6 and the nozzle member 10 to the exhaust gas inflow bonnet 4 side.
  • the jet flow velocity of the cooling medium flowing out from the jet hole 10-1 of the nozzle member 10 is increased more than in the cooling medium distributor 8, so that the inner surface of the tube sheet 3 is increased. It reaches quickly and cools, and the boiling of the cooling medium is more effectively prevented.
  • the multitubular heat exchanger according to the second embodiment of the present invention shown in FIGS. 5 and 6 includes the nozzle member 10 of the multitubular heat exchanger according to the first embodiment of the multitubular heat exchanger.
  • the cooling medium distributor 8 is provided so as to be substantially orthogonal to the longitudinal direction of the casing, and the structure thereof is a flat heat transfer tube group formed on a plate member having a substantially crank shape in cross section as shown in FIGS.
  • the nozzle member 20 provided with the ejection holes 20-1 at the corresponding positions between the respective flat heat transfer tubes 2 is arranged such that the axis of the ejection hole 20-1 of the nozzle member 20 is the flat heat transfer tube 2 of the flat heat transfer tube group.
  • the sum total of the sectional areas of the ejection holes 20-1 is smaller than the sectional direction area of the cooling medium in the cooling medium distributor 8.
  • the shape of the ejection hole 20-1 of the nozzle member 20 may be either a perfect circle or an ellipse or an ellipse having a major axis in the axial direction of the flat heat transfer tube 2 as described above. Not too long.
  • the cooling medium is exhaust gas from the cooling medium inflow pipe 9 through the cooling medium distributor 8 and the nozzle member 20 through the opening 6.
  • the flow velocity of the cooling medium flowing out from the discharge hole 20-1 of the nozzle member 20 is increased more than in the cooling medium distributor 8 and the inner surface of the tube sheet 3 , And is quickly jetted to the inner surface of the tube sheet 3 and cooled, and the cooling medium is more effectively prevented from boiling.
  • the multitubular heat exchanger according to the third embodiment of the present invention shown in FIG. 7 is a system in which a nozzle member is provided in the cooling medium distributor 8 as in the multitubular heat exchanger according to the second embodiment.
  • a nozzle member 30 integrated with a guide portion for allowing the cooling medium to flow more reliably between the flat heat transfer tubes 2 of the flat heat transfer tube group is adopted.
  • a plate member having a substantially S-shaped section having a guide portion 30-2 is provided with ejection holes 30-1 at corresponding positions between the flat heat transfer tubes 2 of the flat heat transfer tube group.
  • the nozzle member 30 is inserted and disposed in the casing 1 through the opening 6 so that the guide portion 30-2 of the nozzle member 30 is located in the space between the flat heat transfer tube 2 and the inner surface of the casing 1,
  • the axis of the ejection hole 30-1 of the nozzle member 30 is flat. It arrange
  • the sum total of the sectional areas of the ejection holes 30-1 is smaller than the sectional direction area of the cooling medium in the cooling medium distributor 8.
  • the shape of the ejection hole 30-1 may be either a perfect circle or an ellipse or an ellipse having a major axis in the axial direction of the flat heat transfer tube 2 as described above.
  • the guide member-integrated nozzle member 30 is folded inward so that the end opposite to the guide portion 31-2 is along the inner surface of the cooling medium distributor 8, as shown in FIG.
  • the guide portion 31-2 of the nozzle member 31 passes through the opening 6 so as to be located in the space between the flat heat transfer tube 2 and the inner surface of the casing 1.
  • the axial center of the ejection hole 31-1 of the nozzle member 31 is directed to the space between the flat heat transfer tubes 2 of the flat heat transfer tube group, and on the exhaust gas inflow bonnet 4 side. It arrange
  • distributor 8 so that it may face the inner surface of the tube sheet 3. As shown in FIG.
  • the cooling medium is exhausted from the opening 6 through the cooling medium inflow pipe 9 through the cooling medium distributor 8, the nozzle member 30 or the nozzle member 31.
  • the jet flow velocity of the cooling medium flowing out from the jet holes 30-1 and 31-1 of the nozzle members 30 and 31 is higher than that in the cooling medium distributor 8.
  • the coolant that is directed toward the inner surface of the tube sheet 3 is ejected with high kinetic energy, and the cooling medium that has flowed out of the ejection holes 30-1 and 31-1 travels along the guide portions 30-2 and 31-2.
  • the guide members 30-2 and 31-2 of the nozzle members 30 and 31 are formed in a strip shape, and the strip portion is extended into the space between the flat heat transfer tubes 2.
  • the cooling medium quickly and accurately reaches the inner surface of the tube sheet 3 and is cooled, and boiling is further effectively prevented.
  • the multitubular heat exchanger according to the fourth embodiment of the present invention shown in FIG. 9 has a nozzle member in the cooling medium distributor 8 as in the multitubular heat exchanger according to the second and third embodiments.
  • a groove-shaped nozzle member 40 having an L-shaped cross section is employed, and the structure thereof is that of the flat heat transfer tube group as shown in FIG. 9.
  • a groove-shaped nozzle member 40 having an L-shaped cross section provided with a jet hole 40-1 at a corresponding position between the flat heat transfer tubes 2, and the axis of the jet hole 40-1 of the nozzle member 40 is an exhaust gas inflow bonnet.
  • the nozzle member 40 also has a smaller sum of cross-sectional areas of the ejection holes 40-1 than the cross-sectional area in the flow direction of the cooling medium in the cooling medium distributor 8.
  • the shape of the hole 40-1 may be either a perfect circle or an ellipse or an ellipse having a major axis in the axial direction of the flat heat transfer tube 2 as described above.
  • the cooling medium is supplied from the cooling medium inflow pipe 9 through the cooling medium distributor 8 and the groove-shaped nozzle member 40 to the exhaust gas inflow bonnet 4 side.
  • the jet velocity of the cooling medium flowing out from the jet hole 40-1 of the nozzle member 40 is increased more than in the cooling medium distributor 8 and directed toward the inner surface of the tube sheet 3.
  • the cooling medium that is ejected with high kinetic energy and flows out from the ejection hole 40-1 flows between the flat heat transfer tubes 2 of the flat heat transfer tube group in the vicinity of the inner surface of the tube sheet 3. Boiling is more effectively prevented.
  • a guide member (not shown) is provided on the side surface of the groove-shaped nozzle member 40 so that the cooling medium flowing out from the ejection hole 40-1 flows between the flat heat transfer tubes 2 of the flat heat transfer tube group more reliably. Even better.
  • a nozzle member for increasing the flow rate of the cooling medium than in the cooling medium distributor 8 is provided in the opening of the casing 1.
  • a nozzle member 50 having a substantially Z-shaped cross section is employed in place of the nozzle members 20, 30, 31, and 40, and the structure thereof is as shown in FIG. 10 and FIG.
  • an ejection hole 50-1 is provided at a position corresponding to between the flat heat transfer tubes 2 of the flat heat transfer tube group and substantially perpendicular to the longitudinal direction of the casing.
  • the nozzle member 50 has a space between the inner surface of the tube sheet 3 on the exhaust gas inflow bonnet 4 side and the flat heat transfer tubes 2 of the flat heat transfer tube group, with the axial center of the ejection hole 50-1 of the nozzle member 50 being Near the opening 6 of the casing 1 so as to be oriented. It is constructed by attaching the pacing first inner wall. At that time, both ends of the nozzle member 50 are attached to the inner wall of the casing so that part of the upper surface side and the lower surface side of the nozzle member protrude into the cooling medium distributor 8 and the casing 1, respectively.
  • the sum of the sectional areas of the ejection holes 50-1 is smaller than the sectional area in the flow direction of the cooling medium in the cooling medium distributor 8, as with the nozzle members 20, 30, 31, 40.
  • the shape of the ejection hole 50-1 may be either a perfect circle or an ellipse or an ellipse having a major axis in the axial direction of the flat heat transfer tube 2 as described above.
  • the cooling medium flows into the exhaust gas inflow bonnet 4 from the cooling medium inflow pipe 9 through the cooling medium distributor 8 and the nozzle member 50 through the opening 6.
  • the jet flow velocity of the cooling medium flowing out from the jet holes 50-1 of the nozzle member 50 is increased more than in the cooling medium distributor 8 and directed toward the inner surface of the tube sheet 3.
  • the cooling medium that is ejected with high kinetic energy and flows out between the flat heat transfer tubes 2 of the flat heat transfer tube group in the vicinity of the inner surface of the tube sheet 3 as a result of the cooling medium flowing out from the ejection holes 50-1 Is effectively prevented from boiling.
  • a guide member (not shown) is attached to the lower surface of the nozzle member 50 in order to allow the cooling medium flowing out from the ejection holes 50-1 to flow more reliably between the flat heat transfer tubes 2 of the flat heat transfer tube group. Even better.
  • the multi-tube heat exchanger according to the sixth embodiment of the present invention shown in FIGS. 12 and 13 has a nozzle member for increasing the flow rate of the cooling medium higher than that in the cooling medium distributor 8.
  • the flat heat transfer tube 2 side protrudes according to the laminated width of the flat heat transfer tube 2 with a substantially V-shaped or U-shaped cross section.
  • a nozzle member 60 having a convex portion 60-3 is employed, and the structure thereof is on one side of the wall surface of the convex portion 60-3 having a substantially V-shaped cross section as shown in FIGS.
  • a nozzle member 60 provided with an ejection hole 60-1 at a position corresponding to the space between the flat heat transfer tubes 2 of the flat heat transfer tube group and substantially orthogonal to the longitudinal direction of the casing is formed in the inclined portion 60-2.
  • the axial center of the ejection hole 60-1 is the channel on the exhaust gas inflow bonnet 4 side. It is constructed by attaching to the casing 1 inside wall near the opening portion 6 of the casing 1 so as to direct the space between the flat heat transfer tubes 2 of the surface and the flattened heat transfer pipe group of Bushito 3. At that time, both ends of the nozzle member 60 are attached to the inner wall of the casing 1 so that the V-shaped convex portion 60-3 of the nozzle member protrudes into the casing 1.
  • the sum of the cross-sectional areas of the ejection holes 60-1 is smaller than the cross-sectional area in the flow direction of the cooling medium in the cooling medium distributor 8.
  • the shape of the ejection hole 60-1 may be either a perfect circle or an ellipse or an ellipse having a major axis in the axial direction of the flat heat transfer tube 2 as described above.
  • the cooling medium distributor is introduced from the cooling medium inflow pipe 9 similarly to the multitubular heat exchanger having the configurations shown in FIGS. 8.
  • the cooling medium flows into the tube sheet 3 on the exhaust gas inflow bonnet 4 side from the ejection hole 60-1 through the opening 6, the nozzle member 60, and the convex portion 60-3, the ejection of the nozzle member 60
  • the jet flow velocity of the cooling medium flowing out from the hole 60-1 is increased from that in the cooling medium distributor 8 and is jetted with high kinetic energy toward the inner surface of the tube sheet 3, and the jet hole 60-
  • the cooling medium flowing out from 1 flows between the flat heat transfer tubes 2 of the flat heat transfer tube group in the vicinity of the inner surface of the tube sheet 3, thereby preventing the cooling medium from boiling more effectively.
  • the cooling medium flowing out from the ejection hole 60-1 is more reliably introduced into the lower surface of the nozzle member 60 in order to flow between the flat heat transfer tubes 2 of the flat heat transfer tube group. It is even better if a guide member (not shown) is attached.
  • the multi-tube heat exchanger according to the seventh embodiment of the present invention has a nozzle member for increasing the flow rate of the cooling medium as compared with that in the cooling medium distributor 8 as an opening of the casing 1.
  • a convex portion 70-3 that protrudes corresponding to the laminated width of the flat heat transfer tube 2 with a substantially V-shaped or U-shaped cross section on the flat heat transfer tube 2 side.
  • a section U corresponding to a space portion between the flat heat transfer tubes 2 of the flat heat transfer tube group of the convex portion 70-3 and projecting into the space portion at a position substantially orthogonal to the longitudinal direction of the casing.
  • a nozzle member 70 in which a letter-shaped or V-shaped projecting portion 70-4 is formed and an ejection hole 70-1 is provided in an inclined portion 70-2 on one side of the wall surface of the projecting portion 70-4 is adopted.
  • the nozzle member 70 is connected to the nozzle. It is constructed by being attached to the inner wall of the casing 1 in the vicinity of the opening 6 of the casing 1 so that the axial center of the ejection hole 70-1 of the material 70 is directed to the space between the flat heat transfer tubes 2 of the flat heat transfer tube group. is there.
  • both ends of the nozzle member 70 are attached to the inner wall of the casing 1 so that the convex portions 70-3 and the protruding portions 70-4 of the nozzle member protrude into the casing 1.
  • the sum of the sectional areas of the ejection holes 70-1 is smaller than the sectional area of the cooling medium distributor 8 in the flow direction of the cooling medium.
  • the shape may be either a perfect circle or an ellipse or an ellipse having a major axis in the axial direction of the flat heat transfer tube 2 in the same manner as described above.
  • the cooling medium inflow pipe 9 passes through the cooling medium distributor 8 and the opening 6.
  • the jet velocity of the cooling medium flowing out from the jet hole 70-1 of the nozzle member 70 is higher than that in the cooling medium distributor 8.
  • the cooling medium which is accelerated and jets toward the inner surface of the tube sheet 3 with high kinetic energy, and the cooling medium flowing out from the ejection holes 70-1 of each of the flat heat transfer tube groups near the inner surface of the tube sheet 3 By flowing between the flat heat transfer tubes 2, the cooling medium is more effectively prevented from boiling.
  • the protruding portion 70-4 of the nozzle member 70 protrudes in a space portion between the flat heat transfer tubes 2 of the flat heat transfer tube group, the cooling medium flowing out from the ejection hole 70-1 is reliably ensured. Since it can be made to flow in between each flat heat exchanger tube 2 of a flat heat exchanger tube group, the above-mentioned guide member 61 etc. may be omitted.
  • the multitubular heat exchanger according to the eighth embodiment of the present invention shown in FIG. 16 has a nozzle member for increasing the jetting flow rate of the cooling medium higher than that in the cooling medium distributor 8 in the vicinity of the opening of the casing 1.
  • the nozzle member 80 having a convex portion with a substantially V-shaped cross section similar to the nozzle member 60 of the multi-tube heat exchanger according to the sixth embodiment of the present invention shown in FIGS.
  • the structure corresponds to the inclined portion on one side of the wall of the convex portion having a substantially V-shaped cross section between the flat heat transfer tubes 2 of the flat heat transfer tube group as shown in FIG.
  • a nozzle member 80 provided with a short tubular burring nozzle 80-2 having a jet hole 80-1 at the tip and bulging toward the flat heat transfer tube 2 is provided at the tip of the burring nozzle 80-2 of the nozzle member 80.
  • the center of the injection hole 80-1 is on the exhaust gas inflow bonnet 4 side. It is constructed by attaching to the casing 1 inside wall near the opening portion 6 of the casing 1 so as to direct the space between the flat heat transfer tubes 2 of the surface and the flattened heat transfer pipe group of Yubushito 3. At this time, both ends of the nozzle member 80 are attached to the inner wall of the casing 1 so that the burring nozzle 80-2 of the V-shaped convex portion of the nozzle member protrudes into the casing 1.
  • the sum of the cross-sectional areas of the ejection holes 80-1 is smaller than the cross-sectional area of the cooling medium distributor 8 in the flow direction of the cooling medium, and the burring nozzle 80-2 and Needless to say, the hole shape of the ejection hole 80-1 may be either a perfect circle or an ellipse or an ellipse having a major axis in the axial direction of the flat heat transfer tube 2 as described above.
  • the cooling medium is supplied from the cooling medium inflow pipe 9 through the cooling medium distributor 8 and the opening 6, and the cooling medium is supplied from the nozzle member 80 to the exhaust gas inflow bonnet 4 side tube.
  • the jetting flow velocity of the cooling medium flowing out by being guided by the tubular burring wall of the burring nozzle 80-2 of the nozzle member 80 is improved as compared with that in the cooling medium distributor 8.
  • the cooling medium that is accelerated and jets toward the inner surface of the tube sheet 3 with high kinetic energy, and the cooling medium that has flowed out of the burring nozzle 80-2 is formed in each flat heat transfer tube group near the inner surface of the tube sheet 3.
  • the linearity of the cooling medium is further increased by the action of the burring nozzle 80-2, whereby the inner surface of the tube sheet 3 of the cooling medium. Quickly and accurately reached to cool boiling can be prevented more effectively. It is more effective to attach a guide member (not shown) to the lower surface of the nozzle member 80.
  • the multitubular heat exchanger according to the ninth embodiment of the present invention shown in FIG. 17 has a nozzle member for increasing the flow rate of the jetted cooling medium as compared with that in the cooling medium distributor 8 in the vicinity of the opening of the casing 1.
  • a nozzle member 90 similar to the nozzle member 40 of the multitubular heat exchanger according to the fourth embodiment of the present invention shown in FIG. 9 is adopted, and the structure thereof is shown in FIG.
  • each of the outflow holes 90-3 of the groove-shaped member having a concave cross section provided with outflow holes 90-3 at positions corresponding to the flat heat transfer tubes 2 of the flat heat transfer tube group is ejected at the tip.
  • -1 axis is between each flat heat transfer tube 2 in the flat heat transfer tube group Space and mounted near the proximal end portion of the cooling medium distributor 8 to direct tubesheet 3 inside surface is obtained by configuration.
  • the nozzle member 90 with the nozzle bush 90-2 is preferably mounted in the cooling medium distributor 8 so that the nozzle bush 90-2 passes through the opening 6 and its tip protrudes into the casing 1. .
  • a guide member (Not shown) may be attached.
  • the flow hole 90-3 and the ejection hole 90-1 of the nozzle member 90 and the shape of the nozzle bush 90-2 and the ejection hole 90-1 are also the same as the above, and the axis of the perfect circular or flat heat transfer tube 2 is used. Needless to say, it may be oval or oval having a major axis in the direction.
  • the nozzle bush 90-2 may be formed integrally with the nozzle member 90 as in the eighth embodiment.
  • the cooling medium is supplied from the cooling medium inflow pipe 9 through the cooling medium distributor 8 and the nozzle member 90, and the cooling medium is supplied from the opening 6 to the exhaust gas inflow bonnet 4 side tube.
  • the jet velocity of the cooling medium flowing out from the flow hole 90-3 of the nozzle member 90 and the jet hole 90-1 of the nozzle bush 90-2 is increased more than in the cooling medium distributor 8.
  • the liquid is ejected toward the inner surface of the tube sheet 3 with high kinetic energy, and the cooling medium flowing out from the ejection hole 90-1 at the tip of the nozzle bush 90-2 is flattened near the inner surface of the tube sheet 3.
  • a nozzle member for increasing the jet velocity of the cooling medium as compared with that in the cooling medium distributor 8 is provided in the vicinity of the opening of the casing 1.
  • the nozzle member similar to the nozzle member 50 of the multitubular heat exchanger according to the fifth embodiment of the present invention shown in FIG. 10 is relatively long and has a nozzle tube 100-1 at the tip.
  • the structure of the flat heat transfer tube group in the flat heat transfer tube group is formed on the inclined portion of the central portion of the substantially Z-shaped plate member.
  • a long length having an ejection hole 100-1 at the tip so that the plate member passes through the plate member at a corresponding position between the heat tubes 2 and the axis is directed to the space between the flat heat transfer tubes 2 of the flat heat transfer tube group.
  • the nozzle member 100 to which the nozzle pipe 100-2 is attached is connected to the casing 1 Spiral fins 100-3 are provided in the nozzle tube 100-2 so as to provide a swirlability to the cooling medium and further improve linearity in the nozzle tube 100-2. ing.
  • the cross-sectional shape of the nozzle tube 100-2 and the tip ejection hole 100-1 of the nozzle member 100 is a perfect circle or an ellipse or an ellipse having a major axis in the axial direction of the flat heat transfer tube 2 as described above. Needless to say, any shape is acceptable.
  • the cooling medium is exhaust gas from the opening 6 through the cooling medium inflow pipe 9 through the cooling medium distributor 8, the nozzle member 100 and the nozzle pipe 100-2.
  • the jet flow velocity of the cooling medium flowing out from the jet hole 100-1 at the tip of the nozzle tube 100-2 of the nozzle member 100 is higher than that in the cooling medium distributor 8.
  • the coolant that is directed toward the inner surface of the tube sheet 3 with high kinetic energy is ejected, and the cooling medium that has flowed out of the ejection hole 100-1 is in the flat heat transfer tube group in the vicinity of the inner surface of the tube sheet 3.
  • a multi-tube heat exchanger according to an eleventh embodiment of the present invention shown in FIGS. 19 to 21 includes a nozzle member for increasing the jetting flow rate of the cooling medium more than that in the cooling medium distributor 8, the casing 1
  • a guide member is provided to allow the cooling medium flowing into the tube sheet to flow along the inner surface of the tube sheet or through the space between the flat heat transfer tubes 2, and the comb-shaped guide member is adopted as the guide member.
  • the structure is the same as that of the multitubular heat exchanger according to the first embodiment of the present invention shown in FIGS. 1 to 4 attached to the inner wall of the casing 1 near the opening 6 of the cooling medium distributor 8.
  • a comb-like guide member 110 having a nozzle member 10 with an ejection hole 10-1 and a strip-like guide portion 110-1 provided extending in each space between the laminated flat heat transfer tubes 2;
  • Strip-shaped guide portion of the guide member 110 10-1 is the one constructed by attaching a bent portion 110-2 of the upper end portions by penetrating the ejection holes 10-1 of the nozzle member 10 to the inner surface of the cooling medium distributor 8.
  • the cooling medium inflow pipe 9 passes through the cooling medium distributor 8, the nozzle member 10 with the ejection holes 10-1, and the comb-shaped guide member 110.
  • the flow velocity of the cooling medium flowing out from the opening 6 is increased more than in the cooling medium distributor 8 and is comb-shaped.
  • the guide member 110 By the action of the guide member 110, that is, the action by the strip-shaped guide part 110-1 being extended and crossing the space between the flat heat transfer tube groups and the guide tip reaching the inner surface of the tube sheet 3,
  • the cooling medium ejected with a higher kinetic energy than the ejection hole 10-1 through the opening 6 flows along the surface of the strip-shaped guide part 110-1 and reliably reaches the tip thereof.
  • Quickly and accurately reached to cool boiling tubesheet 3 inner surface through each space between the TairaDennetsu tube 2 can be prevented more effectively.
  • boiling prevention is achieved by appropriately selecting and changing the curved shape (guide surface shape) of the strip-shaped guide portion 110-1 according to the temperature distribution, flow velocity, flow direction characteristics, etc. of the cooling medium. It is possible to increase the effect.
  • the multi-tube heat exchanger shown in FIGS. 22 and 23 is a system in which the cooling medium that has flowed into the casing 1 is caused to flow toward the tube sheet 3 on the exhaust gas inflow bonnet 4 side by a guide member.
  • the nozzle member is not shown, but the nozzle member 20 of the second embodiment, the nozzle member 40 of the fourth embodiment, etc. are distributed as a cooling medium.
  • the casing 8 is disposed in the casing 8 so that the guide member 120 is positioned in the space between the flat heat transfer tube 2 of the flat heat transfer tube group and the inner surface of the casing 1 in the cooling medium inflow opening 6 provided on the outer peripheral wall surface of the casing.
  • this guide member 120 is good also as a structure which formed the lower end part in a strip shape as shown in the said FIG. 21, and extended the said strip-shaped part to the space part between each flat heat exchanger tubes 2 (2 points
  • the cooling medium flowing in from the cooling medium inflow pipe 9 and the cooling medium distributor 8 and the opening 6 is applied to the inner surface of the tube sheet 3 by the action of the guide member 120. It reaches quickly and cools, and the boiling of the cooling medium is effectively prevented.
  • the multitubular heat exchanger according to the thirteenth embodiment of the present invention shown in FIG. 23 has a nozzle member not shown, but the nozzle member 10 of the first embodiment, the nozzle member 50 of the fifth embodiment and the like are casings. 1, and a guide member 130 similar to the guide member 120 is configured to pass through the cooling medium inflow opening 6 provided on the outer peripheral wall surface of the casing and is attached to the inner wall of the cooling medium distributor 8.
  • the guide member 130 may have a structure in which the lower end portion is formed in a strip shape as shown in FIG. 21 and the strip portion is extended into the space between the flat heat transfer tubes 2 (two-dot chain line). ).
  • the multitubular heat exchanger having the configuration shown in FIG.
  • a multitubular heat exchanger according to a fourteenth embodiment of the present invention shown in FIG. 24 is for replacing the guide members 120 and 130 with a cooling medium flow rate higher than that in the cooling medium distributor 8.
  • the guide unit integrated nozzle member 140 has a structure in which the ejection hole 140 is formed at a position corresponding to between the flat heat transfer tubes 2 of the flat heat transfer tube group on the upper side corresponding to the nozzle member. -1 is provided, the guide end integrated nozzle member 140 having a guide portion 140-2 at a position facing the ejection hole by curving and extending its continuous end, and the guide portion 140-2 is a flat heat transfer tube.
  • the nozzle member 140 may have a structure in which a lower end portion is formed in a strip shape and the strip portion is extended into a space between the flat heat transfer tubes 2. Good (indicated by a two-dot chain line). Further, the sum of the cross-sectional areas of the ejection holes 140-1 is smaller than the cross-sectional area in the flow direction of the cooling medium in the cooling medium distributor 8, and the shape of the ejection holes 140-1 is a perfect circle or a flat transmission similar to the above. Needless to say, either an ellipse or an ellipse having a major axis in the axial direction of the heat tube 2 may be used.
  • the cooling medium is supplied from the cooling medium inflow pipe 9 through the cooling medium distributor 8 and the nozzle member 140, and the cooling medium is supplied from the opening 6 to the exhaust gas inflow bonnet 4 side tube.
  • the flow velocity of the cooling medium flowing out from the ejection hole 140-1 of the nozzle member 140 is increased from that in the cooling medium distributor 8 and also flows out from the ejection hole 140-1.
  • the cooling medium quickly reaches the inner surface of the tube sheet 3 by the action of the guide portion 140-2 and is cooled, so that boiling of the cooling medium is effectively prevented.
  • the cooling medium inflow pipe 9 is provided at the end opposite to the base end of the cooling medium distributor 8 to cool the cooling medium.
  • the supply method of the cooling medium is not limited to the above method, and the supply method shown in FIGS. 25 and 26 is used. It may be adopted. That is, in the multitubular heat exchangers according to the fifteenth and sixteenth embodiments of the present invention shown in FIGS. 25 and 26, the cooling medium inflow pipes 19 and 29 are directly connected to the cooling medium distributor 8, respectively. 25, the multi-tube heat exchanger shown in FIG.
  • the multi-tube heat exchanger shown in FIG. 26 uses the same cooling medium distributor 28 as described above, and supplies a cooling medium by connecting a linear cooling medium inflow pipe 29 above the back of the cooling medium distributor 28. It is a method to do.
  • the cooling medium inflow pipes 19 and 29 are provided to be inclined with respect to the tube axis of the heat transfer pipe 2 so that the cooling medium flows downward from above in order to increase the flow rate of the cooling medium as much as possible. preferable.
  • the embodiment shown in FIGS. 1 to 26 of the present invention is a multi-tube heat exchanger in which the cooling medium distributors 8, 18, and 28 are inclined with respect to the axis of the casing 1.
  • the structure of the nozzle member 60 for increasing the flow rate of the cooling medium from that in the cooling medium distributor 8 is provided in the casing 1.
  • the box-shaped cooling medium distributor 8A having a base end (bottom) opened so that the flange 8A-1 covers the cooling medium inflow opening 6 provided in the casing 1 is provided.
  • each flat heat transfer tube group Fixed vertically to the axis of the casing 1, each flat heat transfer tube group
  • the nozzle member 60 provided with the ejection holes 60-1 corresponding to the space between the heat transfer tubes 2 and substantially perpendicular to the longitudinal direction of the casing is arranged such that the axis of the ejection holes 60-1 of the nozzle member 60 is the exhaust gas inflow bonnet 4.
  • the casing 1 of the cooling medium inflow opening 6 of the casing 1 is directed to the inner surface of the tube sheet 3 (FIG. 1) on the (FIG.
  • the nozzle member 60 side and the space between the flat heat transfer tubes 2 of the flat heat transfer tube group. It is configured to be attached to the inner wall. At that time, both ends of the nozzle member 60 are attached to the inner wall of the casing 1 so that the V-shaped convex portion 60-3 of the nozzle member protrudes into the casing 1.
  • the sum of the cross-sectional areas of the ejection holes 60-1 is larger than the flow direction area of the cooling medium in the vertical cooling medium distributor 8A.
  • the shape of the ejection hole 60-1 may be either a perfect circle or an ellipse having a long diameter in the axial direction of the flat heat transfer tube 2 or an oval shape, similar to the above.
  • the cooling medium flows vertically to the axial center of the casing 1 by the cooling medium distributor 8A, but the ejection hole 60- 1 of the casing 1 is oriented so that the inner surface of the tube sheet 3 (FIG. 1) on the exhaust gas inflow bonnet 4 (FIG. 1) side and the space between the flat heat transfer tubes 2 of the flat heat transfer tube group are oriented. Since the cooling medium inflow opening 6 is attached to the inner wall of the casing 1 so as to be substantially orthogonal to the longitudinal direction of the casing, the cooling medium is cooled from the ejection hole 60-1 through the opening 6, the nozzle member 60, and the convex portion 60-3.
  • the jet flow velocity of the cooling medium flowing out from the jet hole 60-1 of the nozzle member 60 is increased as compared with that in the cooling medium distributor 8A and the tube sheet. 3 inner surface
  • the cooling medium flowing out from the ejection hole 60-1 flows between the flat heat transfer tubes 2 of the flat heat transfer tube group in the vicinity of the inner surface of the tube sheet 3 while being jetted with high kinetic energy. This effectively prevents the cooling medium from boiling.
  • the cooling medium flowing out from the ejection hole 60-1 is more reliably introduced into the lower surface of the nozzle member 60 so as to flow between the flat heat transfer tubes 2 of the flat heat transfer tube group. It is more effective to attach a guide member (not shown).
  • the multitubular heat exchanger according to the eighteenth embodiment of the present invention shown in FIG. 29 is the same as the heat exchanger according to the sixth embodiment shown in FIG.
  • a configuration (cooling medium distributor 8B) that is installed to be inclined at a desired angle ( ⁇ ) in the opposite direction the structure thereof is the same as that of the heat exchanger according to the sixth embodiment shown in FIG.
  • the cooling medium inflow opening 6 provided in the casing 1 is provided with the flange 8B-.
  • a box-shaped cooling medium distributor 8B having a base end (bottom) opened so as to cover 1 is inclined at a desired angle ( ⁇ ) toward the exhaust gas inflow bonnet 4 (FIG. 1) with respect to the axis of the casing 1 And fixed to the casing 1, flat heat transfer tube group
  • the nozzle member 60 provided with the ejection holes 60-1 at the corresponding positions between the flat heat transfer tubes 2 is connected to the exhaust gas inflow bonnet 4 (FIG. 1) side.
  • the cooling medium inflow opening 6 of the casing 1 is directed to the space between the inner surface of the tube sheet 3 (FIG. 1) and the flat heat transfer tubes 2 of the flat heat transfer tube group and substantially orthogonal to the casing longitudinal direction.
  • the casing 1 is attached to the inner wall of the casing 1.
  • both ends of the nozzle member 60 are attached to the inner wall of the casing 1 so that the V-shaped convex portion 60-3 of the nozzle member protrudes into the casing 1.
  • the sum of the cross-sectional areas of the ejection holes 60-1 is larger than the flow direction area of the cooling medium in the vertical cooling medium distributor 8A.
  • the shape of the ejection hole 60-1 may be either a perfect circle or an ellipse having a long diameter in the axial direction of the flat heat transfer tube 2 or an oval shape, similar to the above.
  • the cooling medium is opposite to the heat exchanger according to the sixth embodiment shown in FIG. 12 with respect to the axis of the casing 1 by the cooling medium distributor 8B.
  • the cooling medium inflow opening 6 of the casing 1 so as to be directed to the inner surface of the tube sheet 3 (FIG. 1) on the inflow bonnet 4 (FIG. 1) side and the space between the flat heat transfer tubes 2 of the flat heat transfer tube group.
  • the nozzle member 60 When the cooling medium flows into the tube sheet 3 from the ejection hole 60-1 through the opening 6, the nozzle member 60, and the convex portion 60-3, the nozzle member 60 is attached to the inner wall of the casing 1. Flows out from the nozzle 60-1 The jet velocity of the cooling medium is increased as compared with that in the cooling medium distributor 8B and is jetted with high kinetic energy toward the inner surface of the tube sheet 3, and the jet hole 60- The cooling medium flowing out from 1 flows between the flat heat transfer tubes 2 of the flat heat transfer tube group in the vicinity of the inner surface of the tube sheet 3, thereby effectively preventing the cooling medium from boiling.
  • the cooling medium flowing out from the ejection hole 60-1 is more reliably introduced into the lower surface of the nozzle member 60 so as to flow between the flat heat transfer tubes 2 of the flat heat transfer tube group. It is more effective to attach a guide member (not shown).
  • the multitubular heat exchanger according to the nineteenth embodiment of the present invention shown in FIG. 30 employs a nozzle member 60A provided with ejection holes having different cross-sectional areas in the nozzle member.
  • the ejection holes provided between the flat heat transfer tubes 2 and at positions substantially orthogonal to the longitudinal direction of the casing, the ejection holes 60A- having different cross-sectional areas so that the cross-sectional area gradually increases along the laminating direction of the flat heat transfer tubes. 1 to 60A-4 are provided.
  • the nozzle member is provided with the ejection holes 60A-1 to 60A-4 having different cross-sectional areas as described above, particularly in a large-sized multi-tube heat exchanger having a large number of flat heat transfer tubes.
  • the cross-sectional area of the ejection holes 60A-1 to 60A-4 is sequentially changed
  • the correspondence for changing the cross-sectional area of the ejection holes is not limited to this, and the cross-sectional area is not limited to each of the ejection holes. Needless to say, the area may be changed as desired.
  • the multitubular heat exchanger according to the twentieth embodiment of the present invention shown in FIGS. 31 to 33 has a nozzle member with an ejection hole directed to the tube sheet inner surface on the exhaust gas inlet side and an outflow not directed to the tube sheet inner surface.
  • the nozzle member 60B having a hole is employed, and the structure thereof is, for example, that the EGR gas of the convex portion 60B-3 having a substantially V-shaped cross section protruding continuously in the stacking direction of the heat transfer tube on the heat transfer tube side.
  • an ejection hole 60B-1 is provided at a position corresponding to the space between the flat heat transfer tubes of the flat heat transfer tube group and substantially orthogonal to the casing longitudinal direction.
  • 60B-3 EGR gas flow direction downstream side wall surface (inclined portion) 60B-4 is directed to a space portion between flat heat transfer tubes in which axial cores are laminated or a space portion between flat heat transfer tubes and the inner surface of the casing.
  • a plurality of nozzle members 60B provided with outflow hole 60B-5 of small diameter which does not directed to Bushito inner surface is constructed by attaching to the inner wall of the casing 1.
  • the nozzle member 60B-1 directed to the inner surface of the tube sheet on the exhaust gas inlet side but also the nozzle member 60B provided with the outflow hole 60B-5 not directed to the inner surface of the tube sheet is employed in the nozzle member.
  • the EGR gas temperature rises and the gas flow rate increases, so that not only the inner surface of the tube sheet but also the outer surface of the flat heat transfer tube in the vicinity of the tube sheet may cause boiling of the cooling medium.
  • the cooling medium from the small diameter outflow hole is accelerated and flows between the flat heat transfer tubes in the vicinity of the tube sheet.
  • the outflow hole 60B-5 may be provided, for example, only at a position where the outer surface of the flat heat transfer tube is at a high temperature or by changing the cross-sectional area.
  • the multitubular heat exchanger according to the twenty-first embodiment of the present invention shown in FIG. 34 is a nozzle having a convex portion 60B-3 having a substantially V-shaped cross section of the multitubular heat exchanger according to the twentieth embodiment.
  • a nozzle member 60C having a convex portion 60C-3 having a substantially U-shaped cross section is adopted, and the structure thereof is a cross section substantially protruding in the stacking direction of the heat transfer tubes on the heat transfer tube side.
  • the portion of the flange portion 60C-6 formed at the opening end of the nozzle member 60C on the cooling medium distributor 8A side is the base end of the cooling medium distributor 8A. It is possible to adopt a method of being fixed to the outer surface of the casing 1 by being interposed between the flange portion 8A-1. Also in this case, not only the ejection hole 60C-1 directed to the inner surface of the tube sheet on the exhaust gas inlet side but also the small diameter not directed to the inner surface of the tube sheet in the nozzle member having the convex portion 60C-3 having a substantially U-shaped cross section.
  • the nozzle member 60C provided with the outflow hole 60C-5 is not only the inner surface of the tube sheet but also the flatness in the vicinity of the tube sheet, because the EGR gas temperature rises and the gas flow rate increases at the time of high load operation of the engine.
  • the phenomenon that boiling of the cooling medium also occurs from the outer surface of the heat transfer tube, and not only the cooling in the vicinity of the inner surface of the tube sheet by the cooling water from the ejection hole 60C-1, but also the cooling medium from the small diameter outlet hole 60C-5
  • Even when the engine is under high engine load the air flows between the flat heat transfer tubes near the tube sheet and effectively cools the outer surface of each flat heat transfer tube. This is because it is possible to reliably prevent boiling of a wide range around Yubushito.
  • the method of fixing the nozzle member 60 ⁇ / b> C on the outer surface of the casing 1 has better workability for assembling the nozzle member than the method of fixing the nozzle member 60 ⁇ / b> C on the inner surface of the casing 1.
  • the outflow hole 60C-5 may be provided, for example, only at a position where the outer surface of the flat heat transfer tube is at a high temperature or by changing the cross-sectional area.
  • the multitubular heat exchanger according to the 22nd embodiment of the present invention shown in FIGS. 35 and 36 has an ejection hole directed to the inner surface of the tube sheet on the exhaust gas inlet side and an outflow not directed to the inner surface of the tube sheet.
  • a nozzle member 60D provided with a hole and an outflow hole provided between the ejection hole and the outflow hole that does not face the inner surface of the tube sheet is employed, and the structure thereof is, for example, the lamination of the heat transfer tube on the heat transfer tube side.
  • the space between the flat heat transfer tubes Alternatively, there are provided a plurality of small-diameter outflow holes 60D-5 that are directed to the space between the flat heat transfer tube and the inner surface of the casing and are not directed to the inner surface of the tube sheet on the exhaust gas inlet side.
  • a space between the flat heat transfer tubes or the space between the flat heat transfer tubes and the inner surface of the casing, which is located between the gas flow outlet 60D-5 and the shaft core is laminated on the bottom of the convex portion 60D-3.
  • a nozzle member 60D having a plurality of small-diameter outflow holes 60D-6 that are directed and do not face the inner surface of the tube sheet on the exhaust gas inlet side is attached to the inner wall of the casing 1.
  • a small-diameter outflow is formed at the bottom of the convex portion 60D-3.
  • the nozzle member 60D provided with the hole 60D-6 is used because the EGR gas temperature rises and the gas flow rate increases during high load operation of the engine, so that not only the inner surface of the tube sheet but also the flat heat transfer tube near the tube sheet.
  • the coolant flowing in at right angles flows into the flat heat transfer tube through the outflow hole 60D-6, and has a small diameter provided on the downstream side wall surface in the EGR gas flow direction.
  • the cooling medium from the outlet hole 60D-5 is accelerated and flows into the flat heat transfer tubes slightly away from the tube sheet, thereby effectively cooling the outer surface of each flat heat transfer tube. This is because boiling in a wide range including the vicinity of the tube sheet can be more reliably prevented.
  • the cross-sectional area of the ejection hole 60D-1 is provided by changing the cross-sectional area as desired for each of the ejection holes, or the outflow holes 60D-5 and 60D-6 are provided, for example, on the outer surface of a flat heat transfer tube. Needless to say, it may be provided only at a position where the temperature is high, or may be provided by changing the cross-sectional area.
  • a multitubular heat exchanger according to a twenty-third embodiment of the present invention shown in FIG. 37 has a nozzle having a convex part 60D-3 having a substantially inverted trapezoidal cross section of the multitubular heat exchanger according to the twenty-second embodiment.
  • a nozzle member 60E having a convex portion 60E-3 having a substantially arc-shaped cross section is adopted, and the structure thereof is, for example, a cross section substantially projecting in the stacking direction of the heat transfer tubes on the heat transfer tube side.
  • the ejection hole 60E corresponds to the space between the flat heat transfer tubes of the flat heat transfer tube group and is substantially orthogonal to the casing longitudinal direction.
  • a plurality of small-diameter outflow holes 60E-6 that are directed to the space between the formed flat heat transfer tubes or the space between the flat heat transfer tubes and the inner surface of the casing and not to the inner surface of the tube sheet on the exhaust gas inlet side.
  • the nozzle member 60E having the same is formed by attaching the flange portion 60E-7 to the casing 1 by a method in which the nozzle portion 60E-7 is fixed to the outer surface of the casing 1 in the same manner as described above.
  • the ejection hole 60E-1 directed toward the inner surface of the tube sheet on the exhaust gas inlet side and the outflow hole 60E-5 not directed toward the inner surface of the tube sheet the small diameter outflow is formed at the bottom of the convex portion 60E-3.
  • the nozzle member 60E provided with the hole 60E-6 is used not only for the inner surface of the tube sheet but also for the vicinity of the tube sheet because the EGR gas temperature rises and the gas flow rate increases during high load operation of the engine as described above.
  • the cooling medium flowing in substantially perpendicular to the flow direction is caused to flow into the flat heat transfer tube through the outflow hole 60E-6, and on the downstream side wall surface in the EGR gas flow direction.
  • the cooling medium from the small-diameter outlet hole 60E-5 is accelerated and flows between the flat heat transfer tubes slightly away from the tube sheet to effectively cool the outer surface of each flat heat transfer tube, so that the engine can be operated at high engine load.
  • the outflow holes 60E-5 and 60E-6 may be provided, for example, only at a position where the outer surface of the flat heat transfer tube is at a high temperature or by changing the cross-sectional area.
  • a comb-teeth guide member 110A shown in FIG. 38 is the same as the comb-teeth guide member shown in FIGS. 19 to 21 except that the length of the guide portion is different in the laminating direction of the flat heat transfer tubes.
  • the length of the strip-shaped guide portion 110A-1 extending in each space between the stacked flat heat transfer tubes is gradually increased along the stacking direction of the flat heat transfer tubes, and the center portion is formed to be the longest. It is a thing.
  • the strip-shaped guide portion 110A-1 is provided with a bent portion 110A-2 for attaching the guide member 110A to the cooling medium distributors 8 and 8A.
  • the reason why the length of the guide portion is different in the laminating direction of the flat heat transfer tubes is as follows. That is, the flow rate distribution of the EGR gas flowing into the EGR gas cooling device (EGR cooler) is not uniform and flows while generating a drift, and the tube sheet and the flat transmission near the flat heat transfer tube having a high EGR gas flow rate and a high gas flow rate.
  • EGR cooler EGR gas cooling device
  • a nozzle member 60F having an ejection hole 60F-1 directed to the inner surface of the tube sheet on the exhaust gas inlet side at a position corresponding to the space between the heat pipes 2 and substantially orthogonal to the longitudinal direction of the casing is attached to the inner wall of the casing 1 It is.
  • 7 is a cooling medium outflow pipe.
  • the cooling medium flows horizontally from the side surface of the casing 1 by the cooling medium distributor 8A, but the ejection hole 60F-1 of the nozzle member 60F is a flat heat transfer tube group.
  • the ejection holes 60 F ⁇ are provided through the opening 6 and the nozzle member 60 F.
  • Boiling of the cooling medium is effectively prevented by flowing between the flat heat transfer tubes 2 of the flat heat transfer tube group horizontal arrangement in the near.
  • natural convection due to a rise in the temperature of the cooling medium is unlikely to occur, and the flow is stagnant and is likely to boil.
  • boiling of the cooling medium is reliably prevented by high-speed ejection of the cooling medium between the flat heat transfer tubes in a substantially horizontal direction directed to the tube sheet from the ejection hole 60F-1 of the nozzle member 60F. It becomes possible to do. In addition, even if fine bubbles are generated, they can be accelerated and flowed down quickly by a high-speed cooling medium flow, effectively preventing the bubble growth and boiling caused by the low flow rate. be able to.
  • a series of flat heat transfer tube groups has been described here as an example, the same effect is also obtained in the case of a double flat heat transfer tube group (not shown) in which flat heat transfer tube groups are arranged in parallel in the horizontal direction. It goes without saying that it can be obtained.
  • the multitubular heat exchanger according to the 25th embodiment of the present invention shown in FIG. 40 is different from the multitubular heat exchanger (series of flat heat transfer tube group) according to the 24th embodiment shown in FIG.
  • a multi-tubular heat exchanger having a configuration in which a triple-type flat heat transfer tube group is horizontally arranged is illustrated, and the configuration is such that seven flat heat transfer tubes 2 are horizontally arranged and stacked.
  • the cooling medium flows into the side surfaces on both sides of the casing 1 in which the flat heat transfer tube groups in which the flat heat transfer tube groups are horizontally arranged in three rows are accommodated so as to cover the openings 6 provided on the both side surfaces.
  • a cooling medium distributor 8A with a tube 9 is fixed, and the tube sheet inner surface on the exhaust gas inlet side is disposed at a position corresponding to the space between the flat heat transfer tubes 2 of the flat heat transfer tube groups on both sides and substantially orthogonal to the longitudinal direction of the casing.
  • a nozzle member 60G having a directed ejection hole 60G-1 is attached to the inner walls on both sides of the casing 1 It is obtained by configuration Te.
  • the cooling medium flows horizontally from the side surface of the casing 1 by the cooling medium distributor 8A provided on both sides of the casing 1, but the series shown in FIG.
  • the nozzle hole 60G-1 is directed toward the inner surface of the tube sheet correspondingly between the flat heat transfer tubes 2 of the flat heat transfer tube group.
  • the cooling medium flows into the tube sheet from the ejection holes 60G-1 through the openings 6 on both sides of the casing and the nozzle member 60G.
  • the jet velocity of the coolant flowing out from the jet holes 60G-1 of both nozzle members 60G in the substantially horizontal direction is increased more than in the coolant distributor 8A and the tube sheet
  • the coolant flowing out from the jet hole 60G-1 flows between the flat heat transfer tubes 2 of the three horizontal flat heat transfer tube groups while being jetted with high kinetic energy directed toward the surface. This effectively prevents the cooling medium from boiling.
  • each of the tubes in a substantially horizontal direction directed to the tube sheet from the ejection hole 60G-1 of the nozzle member 60G provided on both sides of the casing 1 Due to the high-speed ejection of the cooling medium between the flat heat transfer tubes, it is possible to reliably prevent the cooling medium from boiling not only in the flat heat transfer tube groups on both sides but also in the central flat heat transfer tube group.
  • a multi-tube heat exchanger composed of a series and triple-type flat heat transfer tube group has been described as an example, but the same effect is also obtained in the case of a double-type flat heat transfer tube group (not shown). Needless to say, an effect can be obtained.
  • the multi-tube heat exchanger according to the present invention allows the cooling medium to flow toward the inner surface of the tube sheet at a higher speed as a means for sufficiently enhancing the boiling prevention effect of the cooling medium on the exhaust gas (EGR gas) inlet side.
  • a cooling medium distributor, a nozzle member, a guide member, and the like having a plurality of ejection holes through which the cooling medium flows at a higher speed than the inside of the cooling medium distributor in a direction substantially perpendicular to the casing longitudinal direction of the multi-tubular heat exchanger are provided.
  • the cooling medium can be accelerated, and the directivity toward the inner surface of the tube sheet can be further improved, so that the cooling medium on the exhaust gas (EGR gas) inlet side Boiling Not only can it be eliminated almost certainly, but also the outer surface of each flat heat transfer tube in the vicinity of the tube sheet can be effectively cooled, so that it is possible to reliably prevent boiling in a wide area near the tube sheet. Decrease in heat exchange performance due to boiling of the gas can be prevented, greatly contributing to heat recovery from engine exhaust gas and cooling of exhaust gas such as EGR gas.
  • Cooling medium inflow opening 7 Cooling medium outflow pipes 8, 8A, 8B, 18, 28 Cooling medium distributors 8-1, 8A- 1, 8B-1 Flange portion 9, 19, 29 Cooling medium inflow pipe 9-1
  • Cooling medium inlet 9-2 Cap 10, 20, 30, 31, 40, 50, 60, 60A, 60B, 60C, 60D, 60E 60F, 60G, 70, 80, 90, 100 Nozzle members 10-1, 20-1, 30-1, 31-1, 40-1, 50-1, 60-1, 60A-1 to 60A-4, 60B-1, 60C-1, 60D-1, 60E-1, 60F-1, 60G-1, 70-1, 80-1, 90-1, 100-1, 140-1 ejection holes 50-2, 60 -2 70-2 Inclined part 60-3, 60B-3, 60C-3, 60D-3, 60E-3, 70-3 Convex part 60B-2, 60C-2,

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
PCT/JP2012/070381 2011-08-10 2012-08-09 多管式熱交換器 Ceased WO2013022072A1 (ja)

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JP2011-174580 2011-08-10
JP2012-176248 2012-08-08
JP2012176248A JP5988296B2 (ja) 2011-08-10 2012-08-08 多管式熱交換器

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Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150129182A1 (en) * 2012-05-01 2015-05-14 Benteler Automobiltechnik Gmbh Heat exchanger comprising a supply channel
DE102014213718A1 (de) * 2014-07-15 2016-01-21 Mahle International Gmbh Wärmeübertrager
EP3034979A1 (de) * 2014-12-19 2016-06-22 Benteler Automobiltechnik GmbH Abgaswärmeübertrager
EP3246647A1 (en) * 2016-05-19 2017-11-22 Borgwarner Emissions Systems Spain, S.L.U. Heat exchange device
IT201700021474A1 (it) * 2017-02-24 2018-08-24 Mitsubishi Electric Hydronics & It Cooling Systems S P A Scambiatore di calore a fascio tubiero ad espansione secca
JP2019095077A (ja) * 2017-11-17 2019-06-20 株式会社ティラド ヘッダープレートレス型熱交換器の冷却水入口構造
EP3567331A1 (en) * 2018-05-09 2019-11-13 João de Deus & Filhos, S.A. Heat exchanger
EP3786562A1 (en) * 2019-08-28 2021-03-03 Valeo Termico S.A. Exhaust gas recirculation cooler
EP3786567A1 (en) * 2019-08-26 2021-03-03 Valeo Termico S.A. An egr cooler
WO2021116630A1 (fr) * 2019-12-13 2021-06-17 Valeo Systemes Thermiques Echangeur de chaleur avec collecteur rapporté
EP3869025A1 (en) * 2020-02-21 2021-08-25 Mahle International GmbH Heat exchanger, in particular exhaust gas cooling device, for cooling exhaust gas from an internal combustion engine
EP4015976A1 (en) * 2020-12-15 2022-06-22 Valeo Autosystemy SP. Z.O.O. Heat exchanger
EP4265982A4 (en) * 2020-12-17 2024-11-20 Panasonic Intellectual Property Management Co., Ltd. TUBE BUNDLE HEAT EXCHANGER, REFRIGERATION CYCLE DEVICE AND HEAT EXCHANGE METHODS

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6143335B2 (ja) * 2013-03-28 2017-06-07 臼井国際産業株式会社 多管式熱交換器
JP5941878B2 (ja) * 2013-07-25 2016-06-29 株式会社ユタカ技研 熱交換器及び熱交換デバイス
KR20150073705A (ko) 2013-12-23 2015-07-01 현대자동차주식회사 내연기관의 배기열 재활용 시스템
DE102014202447A1 (de) * 2014-02-11 2015-08-13 MAHLE Behr GmbH & Co. KG Abgaswärmeübertrager
DE102014219078A1 (de) 2014-09-22 2016-03-24 Mahle International Gmbh Vorrichtung zur Zuführung eines Kühlmittels zu einem Wärmeübertrager, vorzugsweise für einen Abgaskühler eines Verbrennungsmotors eines Kraftfahrzeuges
DE102014226883A1 (de) * 2014-12-22 2016-06-23 Mahle International Gmbh Wärmeübertrager
US10563624B2 (en) 2016-01-12 2020-02-18 T.Rad Co., Ltd. Exhaust gas heat exchanger having stacked flat tubes
KR101825120B1 (ko) * 2017-04-17 2018-02-07 주식회사 코렌스 냉각수 유동성이 개선된 이지알 쿨러
DE102017130153B4 (de) 2017-12-15 2022-12-29 Hanon Systems Vorrichtung zur Wärmeübertragung und Verfahren zum Herstellen der Vorrichtung
WO2019198554A1 (ja) * 2018-04-12 2019-10-17 パナソニック株式会社 シェルアンドチューブ式熱交換器及びそれにおける噴霧方法
FR3084408B1 (fr) * 2018-07-24 2021-09-17 Faurecia Systemes Dechappement Echangeur de chaleur et procede de fabrication correspondant
JP7134842B2 (ja) * 2018-11-15 2022-09-12 株式会社ティラド Ｅｇｒクーラの冷却水入口構造
JP7146085B2 (ja) * 2020-02-25 2022-10-03 日本碍子株式会社 熱交換器の流路構造、及び熱交換器
JP7689331B2 (ja) * 2021-02-24 2025-06-06 パナソニックＩｐマネジメント株式会社 シェルアンドチューブ式熱交換器、冷凍サイクル装置、及び熱交換方法
JP7689327B2 (ja) * 2020-12-17 2025-06-06 パナソニックＩｐマネジメント株式会社 シェルアンドチューブ式熱交換器及び冷凍サイクル装置

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS52103058A (en) * 1976-02-24 1977-08-29 Corning Glass Works Multiple passage and method of producing same
JPH1113550A (ja) * 1997-06-23 1999-01-19 Isuzu Motors Ltd Ｅｇｒクーラ
WO2006035985A1 (ja) * 2004-09-28 2006-04-06 T.Rad Co., Ltd. 熱交換器
KR100748756B1 (ko) * 2006-05-11 2007-08-13 현대자동차주식회사 차량용 ｅｇｒ 장치의 ｅｇｒ 쿨러
JP2008045444A (ja) * 2006-08-11 2008-02-28 Hino Motors Ltd Ｅｇｒクーラ
JP2009091948A (ja) * 2007-10-05 2009-04-30 Tokyo Radiator Mfg Co Ltd Ｅｇｒクーラ
JP2009114923A (ja) * 2007-11-05 2009-05-28 Tokyo Radiator Mfg Co Ltd Ｅｇｒクーラ

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS52103058A (en) * 1976-02-24 1977-08-29 Corning Glass Works Multiple passage and method of producing same
JPH1113550A (ja) * 1997-06-23 1999-01-19 Isuzu Motors Ltd Ｅｇｒクーラ
WO2006035985A1 (ja) * 2004-09-28 2006-04-06 T.Rad Co., Ltd. 熱交換器
KR100748756B1 (ko) * 2006-05-11 2007-08-13 현대자동차주식회사 차량용 ｅｇｒ 장치의 ｅｇｒ 쿨러
JP2008045444A (ja) * 2006-08-11 2008-02-28 Hino Motors Ltd Ｅｇｒクーラ
JP2009091948A (ja) * 2007-10-05 2009-04-30 Tokyo Radiator Mfg Co Ltd Ｅｇｒクーラ
JP2009114923A (ja) * 2007-11-05 2009-05-28 Tokyo Radiator Mfg Co Ltd Ｅｇｒクーラ

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20150129182A1 (en) * 2012-05-01 2015-05-14 Benteler Automobiltechnik Gmbh Heat exchanger comprising a supply channel
US10337807B2 (en) 2014-07-15 2019-07-02 Mahle International Gmbh Heat exchanger with coolant channel and panel
DE102014213718A1 (de) * 2014-07-15 2016-01-21 Mahle International Gmbh Wärmeübertrager
EP3034979A1 (de) * 2014-12-19 2016-06-22 Benteler Automobiltechnik GmbH Abgaswärmeübertrager
DE102014119227A1 (de) * 2014-12-19 2016-06-23 Benteler Automobiltechnik Gmbh Abgaswärmeübertrager
US20160177888A1 (en) * 2014-12-19 2016-06-23 Benteler Automobiltechnik Gmbh Exhaust gas heat exchanger
US9995250B2 (en) 2014-12-19 2018-06-12 Benteler Automobiltechnik Gmbh Exhaust gas heat exchanger
EP3246647A1 (en) * 2016-05-19 2017-11-22 Borgwarner Emissions Systems Spain, S.L.U. Heat exchange device
CN107401939A (zh) * 2016-05-19 2017-11-28 博格华纳排放系统西班牙有限责任公司 热交换装置
IT201700021474A1 (it) * 2017-02-24 2018-08-24 Mitsubishi Electric Hydronics & It Cooling Systems S P A Scambiatore di calore a fascio tubiero ad espansione secca
EP3367036A1 (en) * 2017-02-24 2018-08-29 Mitsubishi Electric Hydronics & IT Cooling Systems S.p.A. A dry-expansion tube bundle heat exchanger
JP2019095077A (ja) * 2017-11-17 2019-06-20 株式会社ティラド ヘッダープレートレス型熱交換器の冷却水入口構造
EP3567331A1 (en) * 2018-05-09 2019-11-13 João de Deus & Filhos, S.A. Heat exchanger
US10989487B2 (en) 2018-05-09 2021-04-27 João de Deus & Filhos, S.A. Heat exchanger
EP3786567A1 (en) * 2019-08-26 2021-03-03 Valeo Termico S.A. An egr cooler
EP3786562A1 (en) * 2019-08-28 2021-03-03 Valeo Termico S.A. Exhaust gas recirculation cooler
WO2021116630A1 (fr) * 2019-12-13 2021-06-17 Valeo Systemes Thermiques Echangeur de chaleur avec collecteur rapporté
FR3107344A1 (fr) * 2019-12-13 2021-08-20 Valeo Systemes Thermiques Echangeur de chaleur avec collecteur rapporté.
CN114981605A (zh) * 2019-12-13 2022-08-30 法雷奥热系统公司 带有附加收集器的热交换器
US12253317B2 (en) 2019-12-13 2025-03-18 Valeo Systemes Thermiques Heat exchanger with an added-on collector
EP3869025A1 (en) * 2020-02-21 2021-08-25 Mahle International GmbH Heat exchanger, in particular exhaust gas cooling device, for cooling exhaust gas from an internal combustion engine
EP4015976A1 (en) * 2020-12-15 2022-06-22 Valeo Autosystemy SP. Z.O.O. Heat exchanger
EP4265982A4 (en) * 2020-12-17 2024-11-20 Panasonic Intellectual Property Management Co., Ltd. TUBE BUNDLE HEAT EXCHANGER, REFRIGERATION CYCLE DEVICE AND HEAT EXCHANGE METHODS

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