JP2014194296A - Multi-tube heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a multi-tube heat exchanger configured so that a group of heat transfer tubes are flat tubes, and capable of improving an action of preventing boiling of cooling water on an exhaust gas inlet by further improving directivity of a cooling water flow introduced into a case or a shell with respect to a direction of an internal surface of a tube sheet or a direction of an exhaust gas inlet.SOLUTION: A multi-tube heat exchanger in which a plurality of stacked flat heat transfer tubes are fixedly attached in a casing, and in which heat exchange is conducted between exhaust gas flowing in the flat heat transfer tubes and cooling water flowing in the casing, comprises a cooling water distributor on an exhaust gas inlet side; and a guide member provided in a space between the flat heat transfer tubes or in each of the space between the flat heat transfer tubes and a space portion between the flat heat transfer tubes and an internal surface of the casing, a tip end of the guide member directing to an internal surface of a tube sheet on the exhaust gas inlet or an end portion near the exhaust gas inlet.

Description

  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.

  As this type of multi-tube heat exchanger, for example, EGR gas cooling devices (Patent Documents 1 to 7) described below have been proposed.

  That is, in Patent Document 1, as shown schematically in FIG. 36 and FIG. 37, near both ends of the body tube 201 provided with the cooling medium inlet 201-1a and the cooling medium outlet 201-2a at both ends. 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. In the EGR gas cooling device of the type, a plurality of cooling medium inlets 201-1a provided on the EGR gas inlet 204-1 side are connected to the EGR gas inlet 204-1 side. 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.

  In Patent Document 2, as schematically shown in FIGS. 38 and 39, 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 as, the other end portion of the case 213 is illustrated EGR cooler cooling water outlet pipe 222 is provided. In the figure, 217 is an end cap, and 218 is a fastening flange.

  In Patent Document 3, as shown schematically in FIGS. 40 and 41, each flat tube in which a tube assembly 234 is built in a shell 231 of a heat exchanger and both ends are supported by end plates (tube sheets) 233. In the heat exchanger for EGR cooler in which high-temperature EGR gas is passed through the interior of 232 and heat is exchanged through the exterior of the cooling water, two or more cooling water inlets 231-1 for introducing cooling water are provided in the shell 231. A heat exchanger for an EGR cooler 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. In the figure, reference numeral 231-1a denotes a cooling water inlet pipe, and 231-2a denotes a cooling water outlet pipe.

  In Patent Document 4, as schematically shown in FIGS. 42 and 43, a hollow shell 241 having a cooling water inlet 241-1 and a discharge outlet 241-2, and an EGR disposed inside the shell 241 are disclosed. In an EGR cooler 240 including a plurality of flat tubes 242 through which gas passes, an adapter member 243 that introduces cooling water into the cooling water introduction port 241-1 provided in the lower side surface portion 241-3 of the shell 241 has an opening 243- An EGR cooler having a configuration with 1 is shown.

  In Patent Document 5, as schematically shown in FIGS. 44 and 45, a hollow shell 251 provided with a cooling water inlet 251-1 and an outlet 251-2, and an end disposed inside the shell 251 are disclosed. In an EGR cooler 250 including a plate (tube sheet) 253 and a plurality of flat tubes 252 through which EGR gas passes, an adapter member 254 that is attached to the cooling water inlet 251-1 and introduces cooling water into the shell 251 is provided. The adapter member 254 extends from the inside of the adapter member to the inside of the shell 251 and includes an EGR cooler provided with a guide plate 255 for adjusting the inflow direction of the cooling water introduced into the shell 251 from the cooling water introduction port 251-1. It is shown.

  In Patent Document 6, as schematically shown in FIGS. 46 and 47, a hollow shell 261 having a cylindrical cooling water inlet pipe 261-1 and a discharge port (not shown), and the inside of the shell 261 are disclosed. The EGR cooler 260 includes a plurality of flat tubes 262 through which 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. In addition, an EGR cooler provided with an attachment 261-2 in which a discharge port 261-2a for discharging cooling water in an arbitrary direction is provided on a bottom surface or a lower side surface is shown.

  The above Patent Documents 1 to 6 are all provided with a tube sheet (header plate, end plate, etc.) for assembling both end portions of a plurality of laminated flat heat transfer tubes. 7 is a tube sheetless type or header plateless type multitubular heat exchanger in which a plurality of flattened heat transfer tubes are accommodated in the main body (body tube, case, outer tube, etc.) while maintaining airtightness. (Drawing omitted) has been proposed. This type of multi-tube heat exchanger is provided with expansion portions at both ends of flat heat transfer tubes that are stacked in a plurality and brought into contact with each other and housed in a main body (body tube, case, outer tube, etc.) The tube sheet (header plate, end plate, etc.) can be omitted by forming both ends of the flat heat transfer tube in an airtight manner in the main body, thereby reducing the manufacturing cost. .

Japanese Patent No. 4386215 JP 2007-154683 A JP 2008-231929 A JP 2009-114924 A JP 2009-91948 A JP 2012-47105 A JP 2007-225190 A

However, the above-described conventional multi-tube heat exchanger has the following drawbacks.
That is, the EGR gas cooling device described in Patent Document 1 is effective in eliminating the boiling of the cooling medium because the overheating area near the tube sheet 203 can be eliminated by providing a plurality of cooling medium inlets 201-1a. However, 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 the flow rate of the cooling medium flowing in from the cooling medium inlet is determined as the cooling medium. Since it does not have an effect of increasing the flow velocity in the pipe flowing into the inflow port, the effect of increasing the flow velocity flowing along the inner surface of the tube sheet 203 cannot be sufficiently obtained, and there is a fear that the boiling prevention effect is insufficient.

  In the EGR gas cooling device described in Patent Document 2, since the cooling water supply chamber 215 is positioned in parallel with the header plate 214, the incoming cooling water flow has no directivity with respect to the inner surface of the header plate 214, and the cooling water supply chamber Since the cooling water flowing in from the front end 220 of the 215 simply flows in the axial direction of the case 213 toward the cooling water outlet pipe 222, the cooling water boiling prevention function on the exhaust gas (EGR gas) inlet side is provided. There is a drawback that it cannot be obtained sufficiently.

  In the EGR cooler heat exchanger described in Patent Document 3, a large amount of flow flows into the shell 231 from the cooling water inlet 231-1 while changing the direction of flowing water to the left and right, and the EGR described in Patent Document 2 described above. Similarly to the gas cooling device, the cooling water flow has no directivity with respect 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 cooling water boiling prevention action on the side cannot be sufficiently obtained.

  In the case of the EGR cooler described in Patent Document 4, the cooling water flowing in from the opening 243-1 passes through the adapter member 243, and a large amount of flow in the shell 241 from the cooling water inlet 241-1 changes the flow direction. It is introduced into between the tubes of the tube row while being changed to the flow direction, and only flows in the axial direction of each tube in the shell 241 along the side surface toward the discharge port 241-2. Sheet) Since there is no directivity with respect to the inner surface of 245, the boiling water preventing action of cooling water on the EGR gas inlet side is the same as the EGR gas cooling device and the heat exchanger for EGR cooler described in Patent Documents 2 and 3 above. There is a drawback that it cannot be obtained sufficiently. In addition, 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. In the case of an EGR cooler having a structure, there is a drawback that an effect of preventing local boiling of cooling water is hardly obtained.

  In the case of the EGR cooler described in Patent Document 5, the flow direction of the cooling water flowing into the shell 251 from the cooling water inlet 251-1 can be changed by about 90 degrees at the elbow adapter member 254 immediately before flowing. After that, the guide plate 255 further directs the flat tube 252 in the stacking direction (a part of the flow is opposite to the guide direction). Since the directivity with respect to the gas is poor, the axial direction of the shell 251 simply flows toward the discharge port 251-2 in the same manner as described in Patent Documents 2 to 4. There is a drawback that the cooling water boiling prevention effect cannot be obtained sufficiently.

  In the case of the EGR cooler described in Patent Document 6, the cooling water flowing into the shell 261 from the cylindrical cooling water inlet pipe 261-1 is joined to the outlet in the shell 261 of the cooling water inlet pipe 261-1. The bottomed cylindrical attachment 261-2 is discharged toward the vicinity of the end plate 264 on the gas inlet side, and is released while being slightly expanded to the left and right sides in the width direction of the shell 261. Although the cooling water inlet pipe 261-1 is installed in the vicinity of the end of the shell 261, the cooling water boiling prevention action is the largest in the vicinity of the cooling water inlet pipe 261-1, which is greater than the cooling water inlet pipe 261-1. There is a problem that the effect of preventing the boiling of the cooling water from being uniform over the entire width direction of the shell 261 cannot be obtained as the distance increases. For this reason, the cooling water inlet pipe 261-1 needs to be separated from the end plate 264, but the amount of cooling water tends to be decelerated until it reaches the vicinity of the end plate 264, and this tendency is the both ends of the shell 261 in the width direction. Even in the attachment 261-2 in which the cooling water discharge port 261-2a is formed near the end plate 264, the discharge amount and the inflow speed of the cooling water over the entire width direction of the shell 261. Therefore, it is not suitable for a large EGR cooler in particular, because it cannot uniformly and sufficiently enhance the cooling water boiling prevention function on the exhaust gas (EGR gas) inlet side. There is no difficulty. In the figure, 262 is a flat tube and 263 is an inlet header.

  In the case of a tube sheetless type or header plateless type multi-tube heat exchanger described in Patent Document 7, there is no tube sheet or header plate common to Patent Documents 1 to 6, and therefore Although there is no problem of boiling from the surface, the cooling water that has flowed into the main body (body tube, case, shell, etc.) only flows along the side surface of each flat heat transfer tube within the main body. Since there is no directivity in the direction of the exhaust gas (EGR gas) inlet side of the laminated flat heat transfer tubes, the cooling water on the exhaust gas (EGR gas) inlet side of the outer surface close to the extended portion of the flat heat transfer tubes There is a drawback that the boiling prevention effect cannot be obtained sufficiently.

  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. Cooling on the exhaust gas (EGR gas) inlet side by increasing the directivity of the inner surface of the tube sheet (header plate, end plate, etc.) or the flat heat transfer tube toward the exhaust gas (EGR gas) inlet side An object of the present invention is to provide a multitubular heat exchanger capable of sufficiently enhancing the water boiling prevention effect.

  A multitubular heat exchanger according to the present invention 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. The cooling water inflow pipe for connecting the cooling water pipe to the end portion is provided, and the base end portion is formed of a long hole provided in the exhaust gas inlet side end portion of the casing in a direction substantially orthogonal to the casing longitudinal direction. In the space between the flat heat transfer tubes and the inner surface of the casing, in addition to the space between the stacked flat heat transfer tubes, or in addition to the space, a cooling water distributor connected to cover the water inflow opening, Exhaust gas at the tip At least 1 箇 guide member is directed to the inlet side of the tubesheet inner surface, and is characterized in that it is further secured in at least one location the guide member is in the flattened heat transfer tubes.

  The multi-tube heat exchanger according to the present invention also includes a plurality of stacked flat heat transfer tubes and a casing formed so as to surround an outer periphery of the flat heat transfer tubes, and an exhaust gas that circulates in the flat heat transfer tubes. Tube tubeless type multi-tubular heat exchanger that exchanges heat between the cooling water flowing in the casing and a cooling water inflow pipe for connecting a cooling water pipe to the end and a base end A cooling water distributor that connects to the exhaust gas inlet side end portion of the casing so as to cover a cooling water inflow opening formed of a long hole provided in a direction substantially perpendicular to the casing longitudinal direction, and the lamination In the space between each flat heat transfer tube made or in addition to the space, the space between the flat heat transfer tube and the inner surface of the casing has at least one guide member whose tip is directed to the exhaust gas inlet side, Before It is characterized in that the guide member is fixed at at least one location in the flattened heat transfer tubes.

  In the multitubular heat exchanger provided with the tube sheet of the present invention and the tubesheetless type multitubular heat exchanger, the guide member preferably has a strip shape or a comb shape. .

  Further, the guide member is fixed to both the flat heat transfer tube and a support member fixed to the flat heat transfer tube, the support member is in a strip shape or a comb shape, and In the strip-shaped support member, the vicinity of the tip of the strip-shaped portion is fixed to the flat heat transfer tube, and in the comb-shaped support member, the vicinity of the tip of the comb-shaped portion is fixed to the flat heat transfer tube. Is a preferred embodiment.

  Here, one end of the strip-shaped guide member is fixed to the base end portion of the comb-shaped support member, and the base end portion of the comb-shaped guide member is one end of the strip-shaped support member or the base end of the comb-shaped support member It is a preferred embodiment that it is fixed to the part.

  Further, in the present invention, a plurality of guide members are provided in the axial direction of the flat heat transfer tubes in the space between the laminated flat heat transfer tubes or in the space between the flat heat transfer tube and the casing inner surface in addition to the space. And a plurality of the laminated flat heat transfer tube groups are provided in the flat direction of the flat heat transfer tubes, and at least one guide member is disposed across the flat heat transfer tubes of the plurality of groups. This is a preferred embodiment.

  Furthermore, it is preferable that the strip-shaped guide portion of the guide member is provided substantially perpendicular to the flat surface of the flat heat transfer tube.

  The guide member preferably includes at least one fin portion fixed to the flat heat transfer tube, and the fin portion is provided in the vicinity of the tip end portion of the guide member. .

  According to the present invention, a plurality of the laminated flat heat transfer tube groups are provided in the flat direction of the flat heat transfer tubes, and at least one guide member is disposed across the plurality of groups of flat heat transfer tubes, and the guide Preferably, the member has a plurality of fin portions fixed to each flat heat transfer tube, and the fin portions are fixed to the flat portions of the flat heat transfer tubes.

  Still further, in the present invention, the cooling water is directed in the space between the stacked flat heat transfer tubes near the cooling water inflow opening or in the space between the flat heat transfer tube and the inner surface of the casing in addition to the space. Providing a nozzle member having a plurality of ejection holes at a position corresponding to the space between the laminated flat heat transfer tubes or the space between the flat heat transfer tube and the casing inner surface in addition to the space, And the sum of the cross-sectional areas of the nozzle member ejection holes is smaller than the cross-sectional area in the direction perpendicular to the flow of the cooling water in the cooling water distributor, and the flow rate of the cooling water in the nozzle hole of the nozzle member is within the cooling water distributor It is preferable that the speed is higher than the average flow velocity.

  Further, the nozzle member has, on the flat heat transfer tube side, a convex portion that has a substantially V-shaped or U-shaped cross section and protrudes in accordance with the laminated width of the flat heat transfer tubes, and the tube portion side of the convex portion (exhaust gas) A position corresponding to a space between each flat heat transfer tube on the front side inclined surface, and a front side inclined surface is formed on the gas inlet side), both end inclined surfaces are formed on both ends of the convex portion, and It is a preferred embodiment that the ejection holes directed to the respective spaces are provided at positions corresponding to the spaces between the flat heat transfer tubes and the casings on the inclined surfaces on both ends.

In the present invention, as a means for sufficiently enhancing the boiling prevention effect of cooling water on the exhaust gas (EGR gas) inlet side, the cooling water is directed to the inner surface of the tube sheet or the exhaust gas (EGR gas) inlet side of the flat heat transfer tube. This means that the cooling water distributor and the guide member are provided so as to flow in the direction of the gas, and the directivity of the tube sheet or the flat heat transfer tube toward the exhaust gas (EGR gas) inlet side is further enhanced. It is possible to improve the effect of preventing the cooling water from boiling on the exhaust gas (EGR gas) inlet side.
That is, the multitubular heat exchanger according to the present invention has the following effects.
1. The cooling water flows into the casing while facing the inner surface of the tube sheet or the exhaust gas (EGR gas) inlet side of the flat heat transfer tube, so that the cooling water flowing into the casing enters the tube sheet on the exhaust gas inlet side. Since it flows along the surface, it is possible to more effectively prevent cooling water boiling near the inner surface of the tube sheet or near the exhaust gas (EGR gas) inlet side of the flat heat transfer tube.
2. The guide member is brought into contact with and fixed to the outer wall surface of the flat heat transfer tube, in particular, the flat surface, thereby providing the following effects.
・ The heat from the exhaust gas propagates from the fixed part to the guide member, and the guide member functions as a radiating fin to increase the exchange heat from the outer wall surface of the flat tube, coupled with the reliable induction of the cooling water flow. It is possible to reduce the outer wall surface temperature, effectively prevent boiling from the vicinity of the fixed portion, and relieve the thermal stress.
・ When the guide member is placed and fixed between the parallel flat (flat) surfaces of the opposing flat tube outer walls, the guide surfaces are arranged at almost right angles to the flat surfaces of the outer walls of the flat tube. Demonstrates the function of the reinforcing ribs, and suppresses the deformation of the flat heat transfer tube, particularly in the stacking direction, caused by temperature rise and engine vibration, etc., or the fixed part of the tube sheet and the flat heat transfer tube, or the flat heat transfer tube It is possible to effectively prevent an increase in vibration stress and thermal stress of the fixed part between the expanded parts and the fixed part with the casing.
・ Since the flat tube and guide member are abutted and fixed, high-precision assembly and fixing technology that secures a minute gap between the flat tube outer wall surface during assembly is not necessary, and it can be manufactured inexpensively with less man-hours. be able to.
-Even if the strip-shaped guide member is long, the vicinity of its tip is fixed to the outer wall surface of the flat tube, so the change in the cooling water flow velocity or pressure or the mounted engine itself or the road surface of the vehicle on which the engine is mounted The tip position does not fluctuate even if it is vibrated due to vibrations, and the cooling water flow surely flows toward the tube sheet, ensuring the flow along the tube sheet and causing interference with the flat heat transfer tube and the tube sheet. No fretting wear occurs.
-The strip-shaped guide member has its tip and its vicinity fixed to an outer wall surface such as a flat surface of a flat heat transfer tube, so that vibration at the tip is suppressed and the length can be increased, and a laminated arrangement of flat heat transfer tube groups Even if it is a large EGR cooler with multiple rows, the inner surface of the tube sheet side (EGR gas inflow side) of the flat heat transfer tube group disposed at a position away from the cooling water inflow opening (expanded diameter) Near the inner surface of the tube sheet of the flat heat transfer tube group (near the contact portion of the enlarged diameter portion) and the outer surface of the flat heat transfer tube in the vicinity thereof It is possible to effectively prevent cooling water boiling at
-When a plurality of strip-shaped guide members are arranged in one space between flat heat transfer tubes, the cooling water rectifying guide action is more finely demonstrated. For example, a large-sized large heat transfer tube group with a plurality of stacked arrangements In the EGR cooler, the guide member located away from the EGR gas inflow side (tube sheet side) is placed on the wall surface of each flat heat transfer tube of the flat heat transfer tube group arranged away from the cooling water inflow opening. It is a long guide member that reaches, and for the flat heat transfer tube near the cooling water inflow opening, a short guide member that fits in the flat position of the flat heat transfer tube is placed closer to the tube sheet (near the abutting portion of the expanded diameter portion) In addition, by combining the long guide member and the short guide member, the cooling water flow direction, flow velocity, and flow rate are controlled over a wide range on the EGR gas inflow side, thereby making cooling water boiling more effective. It is possible to prevent.
・ Cooling water flow direction, flow velocity and flow rate can be controlled over a wide range on the EGR gas inflow side to prevent the cooling water from boiling more effectively. It becomes possible to separate from the EGR gas inflow side, and the layout is improved. Also, the assembly and fixing workability of the flat heat transfer tube (including the expanded portion), the tube sheet, the casing, and the bonnet is extremely good. .
3. In the vicinity of the cooling water inflow opening provided in the casing, the cooling water is directed in the space between the stacked flat heat transfer tubes or in the space between the flat heat transfer tube and the casing inner surface in addition to the space. By providing a nozzle member provided with a plurality of ejection holes at positions corresponding to the space between the laminated flat heat transfer tubes or the space between the flat heat transfer tube and the inner surface of the casing in addition to the space Further, a greater cooling water boiling prevention effect can be obtained near the inner surface of the tube sheet or near the exhaust gas (EGR gas) inlet side of the flat heat transfer tube.
4). By making the sum of the cross-sectional areas of the ejection holes smaller than the cross-sectional area in the direction perpendicular to the flow of the cooling water in the cooling water distributor, the ejection speed of the cooling water from the ejection holes is cross-sectional in the direction perpendicular to the axis in the cooling water distributor. Thus, the cooling water boiling preventing action near the inner surface of the tube sheet or near the exhaust gas (EGR gas) inlet of the flat heat transfer tube can be further enhanced.

It is a principal part fracture | rupture schematic side view which abbreviate | omits and shows the multitubular heat exchanger which concerns on 1st Example of this invention. It is a 1A-A arrow directional view. It is an expansion perspective view which shows the strip-shaped guide member single-piece | unit of the multi-tube heat exchanger shown in FIG. It is an expansion perspective view which shows the modification of the strip-shaped guide member single-piece | unit of the multi-tube heat exchanger shown in FIG. It is sectional drawing which expands and shows the dotted-circle part of FIG. 2 at the time of employ | adopting the strip-shaped guide member shown in FIG. FIG. 1B is an enlarged cross-sectional view of FIG. 1B-B when the strip-shaped guide member having fixing fins on both the left and right sides shown in FIGS. 3 and 4 and the strip-shaped guide member having fixing fins only on one side are used. ) Shows a case where a strip-shaped guide member having fixing fins on the left and right sides is used, and FIG. 7B shows a case where a strip-shaped guide member having fixing fins on only one side is used. It is an expansion perspective view which shows an example of the comb-tooth shaped guide member used as a guide 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 2nd Example of this invention. It is a perspective view which shows the principal part of the guide member of the multi-tube heat exchanger shown in FIG. It is a perspective view which shows the principal part of the other guide 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 3rd Example of this invention. It is a perspective view which shows the guide member of the multitubular heat exchanger shown in FIG. It is FIG. 11A arrow directional view. It is FIG. 11B-B arrow line view. 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 perspective view which shows the guide 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 5th Example of this invention. It is a perspective view which shows the guide member of the multitubular heat exchanger shown in FIG. It is a perspective view which shows the comb-tooth shaped guide member of the multitubular heat exchanger which concerns on 6th Example of this invention. It is a perspective view which expands and shows the principal part of the comb-tooth shaped guide member shown in FIG. It is a schematic longitudinal cross-sectional view which shows the principal part of the multitubular heat exchanger which concerns on 7th Example of this invention. It is a 21C-C arrow line view. It is a schematic longitudinal cross-sectional view which shows the principal part of the multitubular heat exchanger which concerns on 8th Example of this invention. FIG. 23D is a view as viewed from arrow D-D. It is a schematic longitudinal cross-sectional view which shows the principal part of the multitubular heat exchanger which concerns on 9th Example of this invention. It is a perspective view which expands and shows the principal part of the guide member shown in FIG. It is a schematic longitudinal cross-sectional view which shows the principal part of the multitubular heat exchanger which concerns on 10th Example of this invention. (A) is an arrow view of FIGS. 27E-E, (A) is an enlarged perspective view of the nozzle member shown in FIGS. 27 and 28 (A). It is a schematic longitudinal cross-sectional view which shows the principal part of the multitubular heat exchanger which concerns on 11th Example of this invention. It is a 29F-F arrow line view. It is a perspective view which abbreviate | omits and shows a part of nozzle plate 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 (tube sheetless type) which concerns on 12th Example of this invention. FIG. 32G is a view on arrow G-G. It is a perspective view which shows roughly the flat heat exchanger tube group of the multitubular heat exchanger shown in FIG. FIG. 34 is an enlarged view taken along line HH. It is a schematic plan view which abbreviate | omits the center part and shows the 1st example of the conventional multitubular heat exchanger. It is a schematic longitudinal cross-sectional view which abbreviate | omits the center part of the multitubular heat exchanger shown in FIG. It is a schematic longitudinal cross-sectional view which shows the 2nd example of the conventional multitubular heat exchanger. It is the schematic on the II line | wire of FIG. It is the schematic perspective view which looked at the 3rd example of the conventional multitubular heat exchanger from diagonally downward. It is a schematic longitudinal cross-sectional view of the multitubular heat exchanger shown in FIG. It is the schematic perspective view which looked at the 4th example of the conventional multitubular heat exchanger from diagonally downward. It is a schematic longitudinal cross-sectional view of the multitubular heat exchanger shown in FIG. It is a schematic perspective view which shows the 5th example of the conventional multitubular heat exchanger. It is a schematic longitudinal cross-sectional view of the multi-tube heat exchanger shown in FIG. It is a schematic longitudinal cross-sectional view which shows the 6th example of the conventional multitubular heat exchanger. FIG. 47 is a schematic horizontal and vertical view of the multitubular heat exchanger shown in FIG. 46.

  The multitubular heat exchanger according to the first embodiment of the present invention shown in FIGS. 1 to 6 is preferably formed by stacking a plurality of flat heat transfer tubes 2 having heat transfer fins inserted and fixed in parallel. A flat heat transfer tube group, a casing 1 formed so as to surround the outer periphery of the flat heat transfer tube group, and a tube sheet that is provided at both ends of the casing 1 and through which both end portions of each flat heat transfer tube 2 are supported. 3, an exhaust gas inflow bonnet 4 is provided at one end of the casing 1, an exhaust gas outflow bonnet 5 is provided at the other end, and an exhaust gas inflow bonnet 4 side end near the outer peripheral wall surface of the casing 1 is provided. A cooling water inflow opening 6 comprising a substantially rectangular long hole substantially parallel to the laminating direction of the flat heat transfer tubes 2 is provided, and a cooling water outflow tube 7 is connected to an end of the exhaust gas outflow bonnet 5.

  In the cooling water inflow opening 6, a box-shaped cooling water distributor 8 having a base end (bottom part) opened so as to cover the cooling water inflow opening 6 is arranged perpendicular to the axis of the casing 1. It is provided in parallel (or inclined). The cooling water distributor 8 has a flange portion 8-1 that covers the cooling water inflow opening 6 at a base end portion, and is connected to a cooling water pipe (not shown) at an end opposite to the base end portion. A cooling water inflow pipe 9 is provided in parallel with the outer wall surface of the casing. The cooling water inflow pipe 9 is provided with a cooling water inlet 9-1 having a long hole communicating with the cooling water distributor 8, and the other end is closed by a cap (not shown).

In the casing 1, the space between the flat heat transfer tubes 2 in which the cooling water flowing into the casing is oriented in the direction of the exhaust gas inflow bonnet 4 of the flat heat transfer tube 2 and along the inner surface of the tube sheet 3. A strip-shaped guide member 10a or 10b for flowing through the section is disposed. As shown in an enlarged view in FIG. 3, the strip-shaped guide member 10a has a fin 10a-2 for fixing to the flat surface of the flat heat transfer tube 2 or the inner wall of the casing 1 at the upper portion of the guide surface 10a-1. The strip-shaped guide member 10b shown in an enlarged view in FIG. 4 is flush with the side surface of the guide member 10b. The formed fixing fins 10b-2 are formed at two locations, the substantially middle portion and the lower portion of the guide surface 10b-1. Here, a strip-shaped guide member 10a shown in FIG. 3 is illustrated as an example of a multi-tube heat exchanger in which the flat heat transfer tube 2 is attached to the flat heat transfer tube 2. As shown in an enlarged view in FIG. 10a is attached to the flat surface of the flat heat transfer tube 2 by, for example, Ni brazing via fixing fins 10a-2.
Moreover, 10a-2 and 10b-2 do not necessarily need to be provided on both sides, and there is no particular problem even if single-sided fixing with one-side fins or alternate fixing of one side (not shown). FIG. 6 is an explanatory view showing a double-sided fixing method and a single-sided fixing method, and FIG. 6A is a flat transmission through strip-shaped guide members 10a and 10b via fixing fins 10a-2 and 10b-2 provided on both sides, respectively. The method of attaching to the flat surface of the heat tube 2 by brazing, FIG. (B) shows a strip-shaped guide member (not shown) having fixing fins 10a-2 and 10b-2 only on one side, and fixing only on one side. The method of attaching to the flat surface of the flat heat exchanger tube 2 via the fins 10a-2 and 10b-2 for soldering is shown, respectively.

  In the case of the multitubular heat exchanger configured as shown in FIGS. 1 to 6, the cooling water flowing into the casing 1 from the cooling water inflow pipe 9 through the cooling water distributor 8 and the cooling water inflow opening 6 is a strip. In the tube sheet 3 along the guide surfaces 10a-1 and 10b-1 of the guide members 10a and 10b and directed toward the space between the flat heat transfer tubes 2 and the direction of the exhaust gas inflow bonnet 4 of the flat heat transfer tubes 2 Boiling of cooling water is more effectively prevented by reaching the surface quickly and reliably and cooling. Then, the cooling water flowing in the casing 1 and the exhaust gas flowing in the flat heat transfer tube 2 are heat-exchanged without boiling the cooling water. When the strip-shaped guide member 10a shown in FIG. 3 is used, as shown in FIG. 5, from the gap 10a-3 formed between the flat surface of the flat heat transfer tube 2 and the strip-shaped guide member 10a. Since the cooling water flows along the flat surface and turbulently with the vortex and also flows to the outflow pipe 7 side, stagnation on the back side of the strip-shaped guide member 10a is prevented. Further, since the strip-shaped guide members 10a and 10b are fixed by brazing or the like, the heat of the exhaust gas is transferred from the fixed portion to act as a heat radiating fin, and the temperature of the flat surface of the flat heat transfer tube 2 is lowered. To suppress boiling and increase the amount of exchange heat (the temperature of the exhaust gas is lowered). In addition, the guide member located in the flat part of the flat heat transfer tube 2 is provided at a substantially right angle with respect to the flat surface, and the fin is fixed across the flat part of the adjacent flat heat transfer tube 2, thereby Reinforcing rib action against deformation in the laminating direction and the like is exhibited, and vibration resistance and heat resistance (preventing deformation due to thermal stress) can be improved.

  The guide member shown in FIG. 7 exemplifies a comb-shaped guide member 10c used in place of the strip-shaped guide members 10a and 10b, and its structure is substantially the same as that shown in FIG. A plurality of strip-shaped guide members 10c-3 having fixing fins 10c-2 formed at two lower portions are integrally formed together with their base end portions (end portions on the cooling water inlet side) 10c-4. In the same manner as the strip-shaped guide members 10a and 10b, the strip-shaped guide member 10c-3 is disposed between the flat heat transfer tubes 2 and the flat surface of the flat heat transfer tubes 2 via the fixing fins 10c-2. For example, it is attached by Ni brazing. In the case of the comb-shaped guide member shown in FIG. 7, the cooling water flowing into the casing 1 flows along the base end portion 10c-4 and leaks along the inner surface of the casing 1 toward the outlet direction of the exhaust gas. Then, the flow rate of the cooling water that does not contribute to the prevention of boiling is reduced, and the space between the flat heat transfer tubes 2 and the exhaust gas inflow bonnet direction of the flat heat transfer tubes 2 are directed toward the tip of the strip-shaped guide member 10c-3. As a result, the inner surface of the tube sheet 3 is quickly and surely cooled and the cooling water is effectively prevented from boiling.

  The multitubular heat exchanger according to the second embodiment of the present invention shown in FIGS. 8 to 10 is similar to the multitubular heat exchanger according to the first embodiment. 9, a plurality of strip-shaped guide members 10d shown in FIG. 9, for example, a strip having an arc-shaped groove 11a-2 on the back side at the base end (cooling water inlet side end) 10d-3. A guide member integrated by brazing or welding with the base end portion 11a-3 of the comb-like stay 11a provided with the braided stay 11a-1 is brazed or welded to the side surface of the flat heat transfer tube 2 as shown in FIG. The structure is fixed by the above. 10d-1 is a guide surface, 10d-2 is a fixed fin. Further, the guide member shown in FIG. 10 has a strip-like stay 11b− having a plurality of strip-shaped guide members 10d having arc-shaped groove portions 11b-2 on the back side at the base end portion (end portion on the cooling water inlet side) 10d-3. 1 is integrated by brazing or welding to a base end portion 11b-3 of an L-shaped comb-like stay 11b. The guide member shown in FIG. 10 is also fixed to the flat surface and the convex surface of the flat heat transfer tube 2 by brazing or welding, as shown in FIG. 8, similarly to the comb-like stay 11a.

  In the case of the multitubular heat exchanger of the present invention having the configuration shown in FIGS. 8 to 10, as in the multitubular heat exchanger according to the second embodiment, the boiling prevention associated with the rectification of the cooling water flow and the guide action. -Not only the effect of increasing the amount of exchange heat (decreasing the exhaust gas temperature) is obtained, but also the base ends 11a-3, 11b-3 and the circle from the guide member of the multi-tube heat exchanger according to the second embodiment. The rigidity of the comb-like stay is further improved and the heat dissipation is achieved by the presence of the fixing portion to the convex side surface of the flat tube 2 of the strip-like stays 11a-1 and 11b-1 having the arc-shaped groove portions 11a-2 and 11b-2. And higher durability and reliability can be obtained.

  A multitubular heat exchanger according to a third embodiment of the present invention shown in FIGS. 11 to 14 has a comb-shaped guide member 10e having a structure substantially similar to the comb-shaped guide member 10c shown in FIG. A guide member constituted by a strip-like stay 11c is adopted, and the structure of the guide member is a plurality of strip-shaped guides having fixing fins 10e-2 formed on the guide surface 10e-1 as shown in the figure. On the back surface of the base end portion 10e-3 of the comb-shaped guide member 10e having a structure in which the member is integrally molded at the base end portion (end portion on the cooling water inlet side) 10e-3, the same number as the flat heat transfer tubes 2 A structure in which the base end portion 11c-2 of the strip-like stay 11c having the arc-shaped groove portion 11c-1 at a position corresponding to the convex surface of the side surface of each flat heat transfer tube 2 is integrated by brazing or welding. is there. In this embodiment, the guide member is fixed to the flat and convex surfaces of the flat heat transfer tubes 2 by brazing or welding. In addition, the length of the guide surface 10e-1 part of the comb-tooth shaped guide member 10e is not specifically limited, and shall be determined suitably.

  In the case of the multitubular heat exchanger according to the third embodiment of the present invention having the configuration shown in FIGS. 11 to 14, the cooling water flow is the same as the multitubular heat exchanger according to the first and second embodiments. In addition to the effect of preventing boiling and increasing the amount of exchange heat (decreasing the exhaust gas temperature) associated with the rectification and guide action of the pipe, the strip-like stay is further improved than the guide member of the multi-tube heat exchanger according to the second embodiment. The presence of 11c (corresponding to the comb-like stay 11b) improves the rigidity of the comb-like guide member 10e, and higher durability reliability is obtained.

  The multitubular heat exchanger according to the fourth embodiment of the present invention shown in FIGS. 15 to 16 includes a guide member having a shape substantially similar to the guide member of the multitubular heat exchanger according to the third embodiment. As shown in the figure, the guide member is structured such that a plurality of strip-shaped guide members having fixing fins 10f-2 formed on the guide surface 10f-1 are arranged at the base end (cooling water inlet side). On the rear surface of the base end portion of the comb-shaped guide member 10f having a structure integrally formed at the end portion 10f-3, the material is positioned integrally with the comb-shaped guide member (the material located in the groove portion for the flat heat transfer tube is curved to the back side. And a comb-like stay 10f-4 having an arcuate groove portion 10f-5 connected to the base end portion. In this embodiment, the guide member is fixed to the side surface of each flat heat transfer tube 2 by brazing or welding.

  In the case of the multitubular heat exchanger according to the fourth embodiment of the present invention having the configuration shown in FIGS. 15 to 16, the cooling water flow is similar to the multitubular heat exchanger according to the second and third embodiments. Bout prevention / increase in heat exchange (decrease in exhaust gas temperature) due to the rectification and guide action of the gas, and the comb-like stay 10f-4 of the comb-like guide member is located in the groove for the flat heat transfer tube Since the material to be bent is integrally formed on the back side, the material yield is better than the guide member employed in the multi-tube heat exchanger according to the second and third embodiments, and the comb-like stay 10f. The rigidity of -4 is also improved, and higher durability reliability is obtained.

  The multi-tube heat exchanger according to the fifth embodiment of the present invention shown in FIGS. 17 to 18 employs a guide member having a shape similar to the guide member of the multi-tube heat exchanger according to the third embodiment. As shown in the figure, the guide member has a structure in which a plurality of strip-shaped guide members having fixing fins 10g-2 formed on the guide surface 10g-1 are arranged at the base end (cooling water inlet side end). Part) 10g-3, integrally formed with the comb-shaped guide member on the rear surface of the base end of the comb-shaped guide member 10g formed integrally (with the material located in the same phase as the flat heat transfer tube groove on the back side) This is a structure in which a comb-like stay 10g-4 having an arcuate groove portion 10g-5 connected to the base end portion is provided. In this embodiment, the guide member is fixed to the side surface of each flat heat transfer tube 2 by brazing or welding.

  In the case of the multitubular heat exchanger according to the fifth embodiment of the present invention having the configuration shown in FIGS. 17 to 18, the cooling water flow is the same as the multitubular heat exchanger according to the second and third embodiments. In addition to the effect of preventing boiling and increasing the exchange heat amount (decreasing the exhaust gas temperature) associated with the rectification and guide action of the guide, the comb-like stay 10g-4 of the comb-like guide member 10g is connected to the flat heat transfer tube groove portion. Since the material positioned in the same phase is bent to the back side and integrally molded, the multitubular type according to the second and third embodiments is the same as the multitubular heat exchanger according to the fourth example. Compared to the guide member employed in the heat exchanger, the number of manufacturing steps is small, the material yield is good, the rigidity of the comb-like stay 10g-4 is improved, and higher durability reliability is obtained.

  The multi-tube heat exchanger according to the sixth embodiment of the present invention shown in FIGS. 19 to 20 employs a guide member having a shape similar to the guide member of the multi-tube heat exchanger according to the second embodiment. As shown in the drawing, the structure of the guide member is a method in which strip-shaped guide members are arranged between the flat heat transfer tubes 2 as shown in the drawing, and a plurality of strip-shaped guide members 10d shown in FIGS. On the back side at the end (cooling water inflow side end) 10d-3, a curved portion 10h-2 having an arcuate cross section straddling each flat heat transfer tube 2, a connecting portion 10h-3 and a connecting portion 10h- connecting the curved portions. Brazing or welding the guide member in which the tongue-like portion 10h-4 of the belt-like stay 10h-1 having the tongue-like portion 10h-4 formed in the portion 3 is brazed or welded to the side surface of the flat heat transfer tube 2 or A structure that is fixed by welding. That.

  In the case of the multitubular heat exchanger according to the sixth embodiment of the present invention having the configuration shown in FIGS. 19 to 20, the cooling water flow is rectified and guided in the same manner as each of the multitubular heat exchangers. Not only is the effect of preventing boiling / increasing exchange heat (decreasing exhaust gas temperature) obtained, but vibration is also caused when the belt-like stay 10h-1 of the guide member is firmly fixed to each flat heat transfer tube by the curved portion 10h-2. The effect that the deformation | transformation of the flat heat exchanger tube by etc. can be prevented effectively is produced.

  In the multi-tube heat exchanger according to the seventh embodiment of the present invention shown in FIGS. 21 to 22, when the laminated arrangement of flat heat transfer tubes extends over a plurality of rows, each guide member is extended from the cooling water inlet side to each row. In this embodiment, the structure includes a plurality of flat heat transfer tube groups 2a and 2b arranged in two upper and lower stages in which a plurality of flat heat transfer tubes 2 are arranged side by side in a casing 1 and stacked. In the tubular heat exchanger, for example, a guide member substantially similar to that shown in FIG. 7, that is, a substantially intermediate portion of the guide surface 10 i-1 having a length corresponding to the flat heat transfer tube group arranged in two upper and lower stages, A comb-shaped guide member 10i having a structure in which a plurality of strip-shaped guide members having fixing fins 10i-2 formed at two lower portions are integrally formed at the base end portion (end portion on the cooling water inlet side). The strip-shaped guide members are positioned between the flat heat transfer tubes 2 respectively. Is constructed by mounting at flat surface such as Ni brazing the flat heat transfer tubes 2 via the respective fixing fins 10i-2 to.

  In the case of the multitubular heat exchanger according to the seventh embodiment of the present invention shown in FIGS. 21 to 22, the boiling prevention associated with the rectification of the cooling water flow and the guide action as in the case of the above multitubular heat exchangers. The flat heat transfer tubes of the flat heat transfer tube group 2b that are stacked and arranged not only at the effect of increasing the amount of exchange heat (decreasing the exhaust gas temperature) but also from the cooling water inflow opening 6 side. Since each strip-shaped guide member is extended to the surface, it is surely cooled to the inner surface of the tube sheet 3 at a position away from the cooling water inlet side, the exhaust gas inflow bonnet side of each flat heat transfer tube 2, and the flat heat transfer tube surface. There is an effect that water can be guided.

The multi-tube heat exchanger according to the eighth embodiment of the present invention shown in FIGS. 23 to 24 shows an embodiment in which a plurality of guide members are arranged in each space between the stacked flat heat transfer tubes 2. Therefore, here, a multi-tube heat exchanger having two upper and lower rows of flat heat transfer tubes similar to the multi-tube heat exchanger according to the seventh embodiment will be described as an example.
That is, in the multi-tube heat exchanger according to the eighth embodiment, the flat heat transfer tube groups 2a and 2b arranged in two upper and lower stages in which a plurality of flat heat transfer tubes 2 are arranged side by side in the casing 1 and stacked. , A guide member similar to that shown in FIGS. 21 and 22, for example, a guide having a length corresponding to the flat heat transfer tube groups 2a and 2b arranged in two upper and lower stages. A structure in which a plurality of strip-shaped guide members having fixing fins 10j-2 formed at two substantially lower and lower portions of the surface 10j-1 are integrally formed at the base end (cooling water inlet side end). The long comb-teeth guide member (first guide member) 10j and the fixing fin 10k-2 are provided in the middle of the guide surface 10k-1 having a length shorter than the width of the flat surface of the flat heat transfer tube. A short strip-shaped guide member (second guide member) 10k A long strip-shaped guide member (first guide member) 10j and a short strip-shaped guide member (second guide member) 10k are positioned between the flat heat transfer tubes 2 and are short strip-shaped. The guide member 10k is configured to be attached to the flat surface of the flat heat transfer tube 2 by, for example, Ni brazing, through the fixing fins 10j-2 and 10k-2, respectively, at a position close to the exhaust gas inflow bonnet 4 side. is there.

  In the case of the multitubular heat exchanger according to the eighth embodiment of the present invention shown in FIGS. 23 to 24, as in the case of each of the multitubular heat exchangers described above, boil prevention due to the rectification of the cooling water flow and the guide action. -Comb-shaped guide members (first guides) that are stacked and arranged not only from the cooling water inlet side, but also from the effect of increasing the amount of exchange heat (decreasing exhaust gas temperature) and improving vibration resistance Member) 10j and a strip-shaped guide member (second guide member) 10k disposed at a position close to the cooling water inflow opening side, a wide range of inner surfaces of the tube sheet 3 and each flat heat transfer tube 2 The effect of being able to reliably guide the cooling water to the exhaust gas inflow bonnet 4 side and the flat heat transfer tube surface, and the tube sheet even if the cooling water inflow opening is disposed at a position slightly away from the tube sheet 3 in the axial direction Inside as well as An effect that can be guided reliably cooling water to the exhaust gas inlet hood 4 side and the flat heat-transfer tube surface of the flat heat transfer tubes 2.

  The multitubular heat exchanger according to the ninth embodiment of the present invention shown in FIGS. 25 to 26 has the same configuration as the multitubular heat exchanger according to the first embodiment shown in FIGS. In the multi-tube heat exchanger, a small hole 10l-3 is formed in the guide surface 10l-1 of the strip-shaped guide member 10l having the fixing fins 10l-2, and a part of the cooling water flowing into the casing 1 is obtained. By actively flowing to the outflow pipe 7 side, the boiling prevention effect is obtained in a wide range. That is, in the case of the multitubular heat exchanger according to the ninth embodiment, as in the case of each of the multitubular heat exchangers described above, the boil prevention / exchange heat quantity increase (exhaust gas) associated with the rectification of the cooling water flow and the guide action. Not only the effect of lowering the temperature) and the improvement of vibration resistance, but also the cooling water flowing out from the small hole 10l-3 of the strip-shaped guide member 10l to the back side is slightly away from the tube sheet 3 in the axial direction. Since it reaches the flat surface of the flat heat transfer tube quickly and promotes cooling over a wide range, the effect of preventing boiling can be obtained even when the exhaust gas temperature rises and the exhaust gas flow rate increases and speeds up.

  The multitubular heat exchanger according to the tenth embodiment of the present invention shown in FIGS. 27 to 28 has the same configuration as the multitubular heat exchanger according to the first embodiment shown in FIGS. In the multi-tube heat exchanger, a space between the stacked flat heat transfer tubes 2 in the vicinity of the cooling water inflow opening 6 of the casing 1 provided with the cooling water distributor 8 or the flat heat transfer tubes 2 in addition to the spaces. The space between the laminated flat heat transfer tubes 2 or the space between the flat heat transfer tubes 2 and the inner surface of the casing 1 so that the cooling water is directed in the space between the inner surface of the casing 1 and the inner surface of the casing 1. And a nozzle member 13 provided with a plurality of ejection holes 13-1 at positions corresponding to the above is provided on the inner wall or outer wall (not shown) of the casing 1. Here, in the nozzle member 13, the sum of the cross-sectional areas of the ejection holes 13-1 is smaller than the cross-sectional area in the flow direction of the cooling water in the cooling water distributor 8, whereby the cooling water ejection flow rate in the ejection holes 13-1 is achieved. Can be increased more than the average flow velocity in the cross section perpendicular to the axis in the cooling water distributor 8. In the case of the multitubular heat exchanger according to the tenth embodiment, as in the case of each of the multitubular heat exchangers described above, the boil prevention / exchange heat amount (exhaust gas temperature The cooling water that is preferably increased in speed from the ejection holes 13-1 and flows into the casing 1 flows into the inner surface of the tube sheet 3 as well as the exhaust gas inflow bonnet side of each flat heat transfer tube 2 and the flat The effect of promptly reaching the flat surface of the heat transfer tube and cooling it to prevent boiling, and the inner surface of the tube sheet 3 and each flat surface even if the cooling water inlet is located slightly away from the tube sheet 3 in the axial direction An excellent effect is obtained that the cooling water can be reliably guided to the exhaust gas inflow bonnet side of the heat transfer tube 2 and the flat heat transfer tube surface. In addition, the ejection hole 13-1 provided in the position corresponding to the space between the flat heat exchanger tube 2 of the nozzle member 13 and the inner surface of the casing 1 does not necessarily need to be a hole shape in which the entire periphery is connected, and has an opening. When the entire periphery is not connected, for example, as shown in FIGS. 28A and 28A, it is provided as a U-shaped notch and is installed on the inner surface or outer surface (not shown) of the casing 1. The opening may be closed by the periphery of the cooling water inflow opening 6, and the entire periphery of the ejection hole 13-1 may be connected in a hole shape.

  In the multi-tube heat exchanger according to the eleventh embodiment of the present invention shown in FIGS. 29 to 31, the cooling water flow rate is increased in the vicinity of the cooling water inflow opening of the cooling water distributor 8 from the inside of the cooling water distributor 8. In the method of providing a nozzle member provided with a plurality of ejection holes on the inner wall or outer wall (not shown) of the casing 1 in place of the nozzle member 13 of the multitubular heat exchanger according to the tenth embodiment, A nozzle member 23 having a convex portion 23-1 that has a substantially V-shaped or U-shaped cross section and protrudes in accordance with the lamination width of the flat heat transfer tube 2 is employed on the flat heat transfer tube 2 side. An inclined surface directed to the tube sheet side (exhaust gas inlet side) is formed at both ends of the V-shaped convex portion 23-1, and the front-side inclined surface 23-1a of the convex portion 23-1 Ejection holes 23-2a which are located corresponding to the spaces between the flat heat transfer tubes 2 and are directed to the spaces The both-end inclined surfaces 23-1b at both ends of the convex portion 23-1 are respectively provided with ejection holes 23-2b that are positioned corresponding to the space between the flat heat transfer tube 2 and the casing 1 and are directed to the space. Is. Here, similarly to the nozzle member 13, the sum total of the sectional areas of the ejection holes 23-2 a and 23-2 b is smaller than the sectional area in the direction perpendicular to the flow of the cooling water in the cooling water distributor 8. The shape of the ejection holes 23-2a and 23-2b may be a perfect circle, an ellipse, or an ellipse. In the case of the multi-tube heat exchanger according to the eleventh embodiment, each flat heat transfer tube 2 is connected from the ejection hole 23-2a of the front side inclined surface 23-1a of the convex portion 23-1 of the nozzle member 23. The space between the flat heat transfer tube 2 and the casing 1 that is closest to the inner wall of the casing of the laminated flat heat transfer tube group from the ejection holes 23-2b provided on the inclined surfaces 23-1b at both ends on both sides. The cooling water jetted in the direction of flow surely flows along the strip-shaped guide members 10a to 10l disposed in the spaces between the flat heat transfer tubes, so that the cooling water in a wide range including the space portion is obtained. Boiling is more effectively prevented. Although an example in which the nozzle member has a substantially V-shaped cross section and the front side inclined surface is a substantially flat surface is shown, the nozzle member may have a substantially U-shaped cross section and the front side inclined surface may be a curved surface. Needless to say.

  A multi-tube heat exchanger according to a twelfth embodiment of the present invention shown in FIGS. 32 to 35 has a tube sheet 3 that supports a flat heat transfer tube group in which a plurality of flat heat transfer tubes are arranged side by side. Is a so-called tube sheetless type multi-tube heat exchanger, the structure of which is a flat heat transfer tube group in which a plurality of flat heat transfer tubes 12 with heat transfer fins inserted and fixed therein are arranged and stacked The casing 11 is formed so as to surround the outer periphery of the flat heat transfer tube group, and both end portions of each flat heat transfer tube 12 are airtightly incorporated into both end portions of the casing 11, and at one end portion of the casing 11. The exhaust gas inflow bonnet 14 is provided at the other end, and the exhaust gas outflow bonnet 15 is provided at the other end, and the exhaust gas inflow bonnet 14 side end of the outer peripheral wall surface of the casing is substantially rectangular parallel to the stacking direction of the flat heat transfer tubes 12. Long hole Ranaru coolant inlet opening 16 is provided, the cooling water outlet pipe 17 is connected to the exhaust gas outlet hood 15 side end portion. The flat heat transfer tube 12 of this tube sheetless type multi-tube heat exchanger is a flat hollow prismatic tube body having expanded tube portions 12-1 bulging at both ends as shown in FIGS. The inner fin 12-2 is interposed, and the flat heat transfer tubes 12 are laminated in the thickness direction to form a flat heat transfer tube group.

  The cooling water inflow opening 16 has a box shape with a base end (bottom) opened so as to cover the cooling water inflow opening 16 in the same manner as the multi-tube heat exchanger with the tube sheet. The cooling water distributor 18 is provided in parallel (or inclined) with respect to a vertical line with respect to the axis of the casing 11. This cooling water distributor 18 also has a flange portion 18-1 covering the cooling water inflow opening 16 at the base end portion, and the cooling water pipe ( A cooling water inflow pipe 19 connected to (not shown) is provided in parallel with the outer wall surface of the casing. The cooling water inflow pipe 19 is provided with a cooling water inlet 19-1 having a long hole communicating with the cooling water distributor 18, and the other end is closed by a cap (not shown).

  In the casing 11, similarly to the tube-tube heat exchanger with the tube sheet, the flat heat transfer tube flows through the space between the flat heat transfer tubes 12 in which the cooling water flowing into the casing is stacked. A strip-shaped guide member 20a is arranged to flow in the direction toward the exhaust gas inlet side. In this strip-shaped guide member 20a, fixing fins 20a-2 with the flat surface of the flat heat transfer tube 12 protrude outward from the side surface of the guide member 20a by two thicknesses at an upper portion and a lower portion of the guide surface 20a-1. In this way, it is bent at a right angle on the back side. This strip-shaped guide member 20a is also attached by, for example, Ni brazing to the flat surface on the side surface of the flat heat transfer tube 2 via the fixing fins 20a-2 in the same manner as described above. Also in this case, the fixing fins 20a-2 do not necessarily have to be provided on both sides, and there is no particular problem even if one-side fixing with one-side fins.

  In the case of the multi-tube heat exchanger configured as shown in FIGS. 32 to 35, the cooling water flowing into the casing 11 from the cooling water inflow pipe 19 through the cooling water distributor 18 and the cooling water inflow opening 16 is a strip. Flow along the guide surface 20a-1 of the guide member 20a and quickly and surely reach the space between the flat heat transfer tubes 12 and near the exhaust gas inlet side end of the flat heat transfer tubes, Boiling of the cooling water in the space between the flat heat transfer tubes 12 and the vicinity of the exhaust gas inlet side end of the flat heat transfer tubes is effectively prevented. Then, heat exchange is performed between the cooling water flowing in the casing 11 and the exhaust gas flowing in the flat heat transfer tube 12 without boiling the cooling water.

  In addition, the example which arrange | positioned the strip-shaped guide member in the space between the flat heat-transfer tube closest to the inner wall of a casing and the casing of the laminated flat heat-transfer tube group, and provided the convex part in the guide member, the convex part An example in which ejection holes are provided on the inclined surfaces at both ends of the tube is shown. However, when the outer surface of the casing can be sufficiently cooled by an engine cooling fan (not shown), the laminated flat heat transfer tube group When the boiling in the space between the flat heat transfer tube closest to the inner wall of the casing and the casing is not a concern, it may not be necessarily arranged.

DESCRIPTION OF SYMBOLS 1,11 Casing 2,12 Flat heat exchanger tube 2a, 2b Flat heat exchanger tube group 3 Tube sheet | seat 4,14 Exhaust gas inflow bonnet 5,15 Exhaust gas outflow bonnet 6,16 Cooling water inflow opening 7,17 Cooling water outflow tube 8, 18 Cooling water distributors 8-1, 18-1 Flange portions 9, 19 Cooling water inflow pipes 9-1, 19-1 Cooling water inlets 10a, 10b, 10c-3, 10d, 10k, 10l, 20a Strip-shaped guide members 10a-1, 10b-1, 10c-1, 10d-1, 10e-1, 10f-1, 10g-1, 10i-1, 10j-1, 10k-1, 10l-1, 20a-1 Guide surface 10a -2, 10b-2, 10c-2, 10d-2, 10e-2, 10f-2, 10g-2, 10i-2, 10j-2, 10k-2, 10l-2, 20a-2 fixing fin 10 -3 gaps 10c, 10e, 10f, 10g, 10i, 10j comb-shaped guide members 10c-4, 10d-3, 10e-3, 10e-4, 10f-3, 10g-3, 11a-3, 11b-3 , 11c-2 Base end portion 10h-1 Band-shaped stay 10h-2 Curved portion 10h-3 Connecting portion 10h-4 Tongue portion 10l-3 Small holes 11a, 11b, 10f-4, 10g-4 Comb-shaped stay 11a- 1, 11b-1, 11c Strip-like stays 10f-5, 10g-5, 11a-2, 11b-2, 11c-1 Arc-shaped groove portion 12-1 Expanded tube portion 12-2 Inner fin 13, 23 Nozzle member 13-1 , 23-2a, 23-2b Ejection hole 23-1 Convex part 23-1a Front side inclined surface 23-1b Both end inclined surface

Claims (22)

  A plurality of laminated flat heat transfer tubes, a casing formed so as to surround the outer periphery of the flat heat transfer tubes, a tube sheet provided at both ends of the casing and through which both ends of the flat heat transfer tubes are penetrated; A multi-tubular heat exchanger of a type that performs heat exchange between the exhaust gas that flows through the flat heat transfer tube and the cooling water that flows through the casing. Cooling in which a water inflow pipe is provided and a base end portion is connected to an end portion on the exhaust gas inlet side of the casing so as to cover a cooling water inflow opening made of a long hole provided in a direction substantially orthogonal to the casing longitudinal direction. In the space between the laminated flat heat transfer tubes or the space between the flat heat transfer tubes and the casing inner surface in addition to the stacked flat heat transfer tubes, the tip of the tube sheet inner surface on the exhaust gas inlet side finger And had at least 1 箇 guide member, further multitubular heat exchanger in which the guide member is characterized in that it is fixed at at least one location in the flattened heat transfer tubes.   A plurality of stacked flat heat transfer tubes and a casing formed so as to surround the outer periphery of the flat heat transfer tubes, and between exhaust gas flowing through the flat heat transfer tubes and cooling water flowing through the casing In the tube sheetless type multi-tube heat exchanger of the type for performing heat exchange, a cooling water inflow pipe for connecting a cooling water pipe is provided at an end portion, and a base end portion is provided at an end portion on the exhaust gas inlet side of the casing. A space between the stacked flat heat transfer tubes, or the space, including a cooling water distributor connected to cover a cooling water inflow opening formed of a long hole provided in a direction substantially orthogonal to the longitudinal direction of the casing In addition, in the space between the flat heat transfer tube and the inner surface of the casing, there is at least one guide member whose tip is directed to the exhaust gas inlet side, and the guide member is small in the flat heat transfer tube. Multitubular heat exchanger, characterized in that it is fixed in Kutomo one place.   The multitubular heat exchanger according to claim 1 or 2, wherein the guide member has a strip shape.   The multitubular heat exchanger according to claim 1 or 2, wherein the guide member has a comb-teeth shape.   The multi-tube heat exchanger according to any one of claims 1 to 4, wherein the guide member is fixed to both the flat heat transfer tube and a support member fixed to the flat heat transfer tube. .   The multitubular heat exchanger according to claim 5, wherein the support member has a strip shape.   The multi-tube heat exchanger according to claim 5, wherein the support member has a comb-teeth shape.   The multitubular heat exchanger according to claim 6, wherein the strip-shaped support member has a portion near the tip of the strip-shaped portion fixed to a flat heat transfer tube.   The multi-pipe heat exchanger according to claim 7, wherein the comb-like support member has a comb-like portion near a tip thereof fixed to a flat heat transfer tube.   The multitubular heat exchanger according to claim 3, wherein one end of the strip-shaped guide member is fixed to a base end portion of a comb-like support member.   The multitubular heat exchanger according to claim 4, wherein a base end portion of the comb-shaped guide member is fixed to one end of the strip-shaped support member or a base end portion of the comb-shaped support member.   A plurality of guide members are provided in the axial direction of the flat heat transfer tube in the space between the stacked flat heat transfer tubes or in the space between the flat heat transfer tube and the casing inner surface in addition to the space. Item 12. The multitubular heat exchanger according to any one of Items 1 to 11.   The stacked flat heat transfer tube group is provided in a plurality of groups in a flat direction of the flat heat transfer tube, and at least one guide member is disposed across the multiple groups of flat heat transfer tubes. The multitubular heat exchanger according to any one of 1 to 11.   The multitubular heat exchanger according to claim 3 or 10, wherein the strip-shaped guide portion of the guide member is provided substantially perpendicular to the flat surface of the flat heat transfer tube.   The multi-tube heat exchanger according to claim 1, wherein the guide member has at least one fin portion fixed to the flat heat transfer tube.   The multi-tube heat exchanger according to claim 15, wherein the fin portion is provided in the vicinity of a tip portion of the guide member.   A plurality of the laminated flat heat transfer tube groups are provided in the flat direction of the flat heat transfer tubes, and at least one guide member is disposed across the flat heat transfer tubes of the plurality of groups. The multitubular heat exchanger according to any one of claims 13 to 16, further comprising a plurality of fin portions fixed to the heat transfer tubes.   The multi-tube heat exchanger according to claim 17, wherein the fin portion is fixed to a flat portion of the flat heat transfer tube.   In the vicinity of the cooling water inflow opening, the layers are stacked so that the cooling water is directed into the space between the stacked flat heat transfer tubes or in the space between the flat heat transfer tube and the casing inner surface in addition to the space. A nozzle member having a plurality of ejection holes is provided at a position corresponding to the space between the flat heat transfer tubes or the space between the flat heat transfer tube and the casing inner surface in addition to the space. The multitubular heat exchanger according to 1 or 2.   The nozzle member has a substantially V-shaped or U-shaped cross section on the flat heat transfer tube side and has a convex portion that protrudes in accordance with the lamination width of the flat heat transfer tube, and the tube portion side of the convex portion (exhaust gas inlet) The front side inclined surface is formed on both sides of the convex portion, and both end inclined surfaces are formed on both ends of the convex portion, and the positions corresponding to the spaces between the flat heat transfer tubes on the front side inclined surface and the both end inclined The multi-tube heat exchanger according to claim 19, wherein a jet hole directed to each space is provided at a position corresponding to the space between the flat heat transfer tube and the casing on the surface.   21. The multitubular heat exchanger according to claim 19 or 20, wherein the sum of the sectional areas of the ejection holes of the nozzle member is smaller than the sectional area in the direction perpendicular to the flow of the cooling water in the cooling water distributor.   The multi-tube heat exchanger according to claim 19 or 21, wherein a jetting flow rate of the cooling water in the nozzle hole of the nozzle member is increased from an average flow rate in the cooling water distributor.

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