JP2005331217A - Gas cooling device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a gas cooling device capable of efficiently cooling gas such as EGR gas. <P>SOLUTION: In this gas cooling device, a gas pipe for the EGR gas or the like is provided with a large number of cooling pipes vertically crossing a gas flow direction of the pipe such that the cooling pipes penetrate the peripheral wall of the gas pipe, the outer face of the gas pipe on both sides of a pipe axial direction of a refrigerant pipe group thereof or the whole outer face of the gas pipe is provided with a cooling jacket, and the gas inside the gas pipe is cooled by a refrigerant flowing through the cooling pipe. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a gas cooling device, and more specifically, a part of exhaust gas is taken out from an exhaust system of a diesel engine, returned to an engine intake system through an EGR pipe, and added to an air-fuel mixture (hereinafter referred to as EGR). ), An apparatus for cooling the EGR gas in the EGR pipe.

  A method of taking a part of the exhaust gas from the exhaust system, returning it to the engine intake system again, and adding it to the air-fuel mixture is called EGR (Exhaust Gas Recirculation). EGR suppresses the generation of NOx (nitrogen oxide), reduces pump loss, reduces heat dissipation loss to the coolant due to lowering of combustion gas temperature, and increases specific heat ratio due to changes in working gas amount / composition. Since many effects such as improvement of cycle efficiency can be obtained, it is considered to be an effective method for purifying engine exhaust gas and improving thermal efficiency.

  However, when the temperature of the EGR gas is increased and the amount of EGR gas is increased, the durability of the EGR valve is deteriorated due to its thermal action, which may cause premature breakage, and a water cooling structure is necessary to prevent this. It is recognized that there is a decrease in fuel consumption due to a decrease in charging efficiency as the intake air temperature increases. In order to avoid such a situation, an EGR gas cooling device is used with an engine coolant, a car air conditioner refrigerant, cooling air, or the like.

As a conventional EGR gas cooling device, various heat exchanger type coolers have been proposed.
For example, a double pipe in which a metal corrugated plate is inserted as a fin in the inner pipe in an exchanger in which an outer pipe through which a liquid passes is arranged outside the inner pipe through which the gas passes and heat exchange is performed between the gas and the liquid. -Type heat exchanger (refer to Patent Document 1), a double pipe type comprising an inner pipe and an outer pipe, each having either a high-temperature side fluid passage or a low-temperature side fluid passage on the inner pipe side and the outer pipe side, respectively A heat exchanger (see Patent Document 2), an inner pipe for circulating a medium to be cooled, an outer pipe provided so as to surround and surround the outer circumference of the inner pipe, and heat disposed in the inner pipe A double-pipe heat exchanger composed of heat dissipating fins having a stress relieving function (see Patent Document 3), an inner tube through which a medium to be cooled is circulated, and an outer periphery of the inner tube are provided so as to be spaced apart A double pipe type heat exchanger composed of an outer tube and a cross fin disposed inside the inner tube (See Patent Document 4), EGR gas cooling device (see Patent Document 5) in which a cooling pipe (heat transfer pipe) is spirally wound around the outer peripheral surface of the EGR gas pipe, and the outer peripheral wall of the EGR gas pipe And an EGR gas cooling device (see Patent Document 6) having a structure in which a cooling pipe (heat transfer pipe) is inserted into the EGR gas pipe.
Japanese Patent Laid-Open No. 11-23181 JP 2002-350071 A JP 2000-1111277 A JP 2003-21478 A JP-A-9-88730 JP-A-9-88731

However, in the case of the conventional double pipe type EGR gas cooler disclosed in Patent Documents 1 to 4, the inner peripheral surface of the pipe inner surface constituting the EGR gas flow path is smooth over the entire length in the length direction. However, there is a problem that the heat transfer around the center of the pipe is not sufficient and the cooling efficiency of the EGR gas is low.
In addition, the EGR gas cooling device disclosed in Patent Documents 5 to 6 has an advantage that it is easy to manufacture and is inexpensive, but in order to ensure heat transfer performance because the heat transfer area is narrow. It is necessary to lengthen the axial direction, and a layout problem arises when it takes up a large space and is mounted on a car. Furthermore, since the gas flow flows along the EGR gas pipe, There is a problem that the degree is low and the boundary layer of the heat transfer surface is not sufficiently thin and the heat transfer performance is slightly inferior.
The present invention has been made to solve such a problem, and an object of the present invention is to provide a gas cooling device that has excellent cooling efficiency despite being a simple structure and can be easily installed in a limited space. It is what.

The gas cooling device according to the present invention basically improves the heat exchange performance by providing a large number of coolant flow paths that intersect at right angles to the gas flow direction of the gas flow path. 1 In the invention, a number of cooling pipes intersecting a gas pipe at right angles to the gas flow direction of the pipe pass through the outer peripheral wall of the gas pipe as both ends of the pipe open to the outside. A cooling jacket having a cooling medium inflow / outlet is fixed to the outer surface of the gas pipe on the both sides in the axial direction of the cooling medium pipe group or the entire outer surface of the gas pipe, and the cooling medium flowing through the cooling pipe. The gas in the gas pipe is cooled.
Further, the cooling pipe in the gas cooling apparatus has spiral or disk-shaped fins on the outer periphery, or the gas pipe in the heat exchange area in which the cooling pipe is fixedly arranged. At least one plate fin parallel to the flow and perpendicular to the cooling pipe is provided, a burring wall is provided in a through hole into which the cooling pipe of the plate fin is inserted, and a louver is provided on the plate fin. At least one of a through hole, a pin fin, and an unevenness is provided.

  Similarly, in the second invention, a plurality of plate fins in which a plurality of projecting cylindrical bodies are formed in the same phase by performing burring processing on a single plate on a gas pipe are welded or brazed. The cores in which a large number of tubular cooling medium flow paths are formed by joining together, the tubular cooling medium flow paths of the cores intersect at right angles to the gas flow direction of the piping, and each tubular cooling medium As the end of the flow path opens to the outside, it is fixedly arranged through the outer peripheral wall of the gas pipe, and further on the gas pipe outer surface or the entire gas pipe outer surface on both ends of the tubular cooling medium flow path group, A cooling jacket having an inlet / outlet for the cooling medium is fixed, and the gas in the gas pipe is cooled by the cooling medium flowing through the tubular cooling medium flow path. .

Similarly, in the third invention, a plurality of heat transfer tubes having either a cooling medium inflow port or an outflow port and intersecting at right angles to the gas flow direction between the opposed cooling jackets are maintained at intervals. In the arranged gas cooling apparatus, a plurality of flexible molding portions and / or a plurality of heat radiation fins are arranged on an adjacent wall surface excluding a portion covered by the cooling jacket in parallel or intersecting with the gas flow direction. It is characterized by having.
Further, in this gas cooling apparatus, a plurality of plate fins are joined to the outer peripheral surface of the plurality of heat transfer tubes arranged while maintaining the interval in parallel to the gas flow direction, or joined to the heat transfer tubes. It is preferable that the other end of the plate fin is inserted into the flexible molding portion and sandwiched, and the plate fin has a corrugated shape, a corrugated rectangular corrugated shape, a through hole, an unevenness, and a louver. It is preferable that the processing such as the above is performed and the joining means of each part constituting the gas cooling device is welding and / or brazing.

Similarly, in the fourth invention, a plurality of flat heat transfer tubes that have either an inlet or an outlet for the cooling medium and that intersect between the opposing cooling jackets and intersect at right angles to the gas flow direction are maintained at intervals. In the gas cooling device arranged in this manner, a large number of channel-shaped fins are provided on the flat outer surface of the flat heat transfer tube in parallel with the gas flow direction.
Further, in this gas cooling device, the fin is a strip-shaped fin with a small divided shape and cut and raised over the entire length of the flat heat transfer tube or in the length direction. , Irregularities, corrugations, etc. are provided, and the fins are joined between flat heat transfer tubes or between the flat heat transfer tubes and the outer wall of the cooling device, and then joined, and further constitute a gas cooling device including the fins It is preferable that the joining means of each part to be performed is welding and / or brazing.

Similarly, in the fifth invention, a plurality of flat heat transfer tubes that have either an inlet or an outlet for the cooling medium and that intersect between the opposing cooling jackets and intersect at right angles to the gas flow direction are maintained at intervals. A plurality of gas cooling devices provided on the flat outer surface of the flat heat transfer tubes arranged with the gap therebetween, provided with a plurality of fins substantially perpendicular to and parallel to the gas flow direction. The core is formed by alternately interposing and fixing the cores.
In this gas cooling apparatus, the aspect ratio of the core is 1: 1.5 to 1: 7 or 1: 2.5 to 1 in the ratio of the flat heat transfer tube length / EGR gas flow path. : 5, the flat heat transfer tube itself is composed of one or a plurality of flat tubes, and the single flat heat transfer tube has one to a plurality of reinforcing ribs inside. The fin fixed to the flat outer surface of the flat heat transfer tube is fixed to meander in the gas flow direction, and the flat heat transfer tube itself is deformed into a wave shape in the gas flow direction. The fins formed and fixed to the outer surface thereof are also formed in a corrugated shape, the fins are corrugated fins, the fins are provided with louvers, through holes, pin fins, etc., gas Connection of each part of the cooling device Means, it is an preferred embodiment that the welding and / or brazing.

Similarly, according to the sixth aspect of the present invention, a plurality of heat transfer tubes that have either an inlet or an outlet for the cooling medium and that intersect between the opposing cooling jackets and intersect at right angles to the gas flow direction are spaced apart. In the arranged gas cooling device, the cross-sectional shape of the heat transfer tube is a wedge shape whose width is gradually expanded toward the rear of the gas flow direction, and the gas is supplied by the cooling medium flowing through the heat transfer tube of the wedge shape. It is characterized by cooling.
In this gas cooling device, plate fins are fixed in parallel to the gas flow direction between the wedge-shaped heat transfer tubes or between the heat transfer tubes and the gas pipes. Is preferably provided with through-holes, louvers, pin fins, irregularities, etc., and the joining means of each part constituting the gas cooling device including the plate fins is welding and / or brazing. .

Similarly, according to a seventh aspect of the present invention, there is provided a gas cooling apparatus in which a plurality of heat transfer tubes intersecting at right angles to a flow direction of a gas flowing in a gas pipe are arranged at intervals, and the heat transfer tubes are opened at both ends. In such a state, the gas pipe is fixedly arranged through the outer peripheral wall of the gas pipe, and the gas pipe outer peripheral surface over the entire upper and lower sides or both sides or the entire circumference of the gas pipe at both ends in the tube axis direction of the heat transfer tube row group fixedly arranged. A cooling jacket having either an inlet or an outlet for the cooling medium is fixed, and the cooling medium flowing in from the inlet of the cooling jacket passes from the other cooling jacket outlet through the heat transfer tube array group. In which the weirs are alternately arranged in the flow direction of the cooling medium at the boundary between adjacent heat transfer tube groups, and the flow path and flow velocity of the cooling medium flowing through the heat transfer tubes are arbitrarily set. While controlling the heat transfer tube row It is characterized in that the gas is cooled by a cooling medium flowing through the.
Further, in this gas cooling device, the shape of the plurality of heat transfer tubes forming the heat transfer tube row group is a cylindrical tube tube, an oblong flat tube, a metal tube processed into a wedge-shaped cross section, etc. A plate fin fixed to each heat transfer tube forming the heat transfer tube row group or in a gap between the heat transfer tube and the inner peripheral surface of the gas pipe outer wall in parallel with the gas flow direction; The fins are preferably provided with through holes, louvers, pin fins, irregularities, etc., and the joining means of each part constituting the gas cooling device including the plate fins is welding and / or brazing. is there.

The gas cooling device according to the present invention has the effects described below.
The gas cooling device according to the first and second aspects of the present invention is a cooling system comprising a plurality of cooling medium flow paths arranged in a direction perpendicular to the flow of gas flowing in the gas pipe, that is, straight pipes and finned tubes. Due to the action of the piping, and the cooling piping and the fin plate, the gas flow is turbulent and the heat transfer area is increased, and an excellent effect is obtained in that high heat exchange performance is obtained.

  A gas cooling device according to a third aspect of the present invention is provided on a wall surface by performing a plurality of flexible moldings on an adjacent wall surface excluding a portion covered by a cooling jacket in parallel or intersecting with a gas flow direction. A subtle recess is formed, thereby creating a turbulent flow in the gas flow and promoting contact with the outside air by the expanded contact area to increase its cooling efficiency. Instead of molding, a plurality of heat dissipating plate fins are provided on the wall surface excluding the portion covered by the cooling jacket, on the outer wall surface or on the outer peripheral surface of the heat transfer tube, in parallel or intersecting with the gas flow direction. The other end of the plate fin joined to the heat transfer tube is inserted into the flexible molded portion to be sandwiched, or the play fin has a waveform and a wave By processing the corrugated shape, through-holes, irregularities, louvers, etc., the same smooth flow of gas is prevented, and turbulence and vortex flow are generated in the flow to promote contact with the cooling jacket and heat transfer tube. Therefore, the EGR gas cooling system can be easily installed in a limited space because the structure can be simplified and the size and weight can be reduced. Can be installed.

  According to a fourth aspect of the present invention, there is provided the gas cooling device according to the fourth aspect of the present invention, wherein the cooling medium mainly using the engine coolant orthogonal to the gas flow is narrowed by the flat heat transfer tube, and the flow rate is increased to pass through the tube. In addition, the cooling efficiency is increased by expanding the heat transfer area, and in addition, the multiple channel fins provided between the outer surfaces of the flat heat transfer tubes or between the flat heat transfer tubes and the outer wall of the gas pipe The heat is also transferred to cool this, and the expansion of the heat transfer area is further promoted. On the other hand, the EGR gas whose flow path is blocked by the flat heat transfer tube and the channel type fin passes through the irregular gas flow path with turbulent flow and vortex flow over time. Therefore, the heat of the EGR gas is surely transferred to the cooling medium passing at a high speed through the many channel-type fins and the flat heat transfer tube during this time, and efficiently exchanged heat.

  In addition, by making the shape of the channel type fin into a small divided shape, when arranging and fixing between the flat heat transfer tubes and between the flat heat transfer tubes and the outer wall of the gas pipe, at an arbitrary pitch at an arbitrary position. It becomes possible to arrange, and by arranging in a form corresponding to the EGR gas flow, the heat dissipation can be promoted. Furthermore, the problem that the assembly hole pitch between the flat heat transfer tube and the channel type fins does not match and causes difficulty in the assembly is solved by the division method, and the channel type By making the fin a substantially U-shaped with a small cross section, it is possible to ensure the adhesion and reliability of the junction between the fin and the flat portion of the flat heat transfer tube, and to further improve the heat exchange performance. it can.

  Furthermore, since the channel-type fins are closely attached and fixed between the flat heat transfer tubes or between the flat heat transfer tubes and the gas pipe, it acts as a strong support and exerts a reinforcing effect. As the gas cooling device installed in the operating conditions, it can be used as it is, making it possible to reduce the size and weight of the device, making the cooling device more compact and easily installing it in a limited space. can do.

  According to a fifth aspect of the present invention, there is provided a gas cooling device comprising: a core by alternately interposing and fixing a plurality of fins substantially perpendicular to the outer surface of the flat heat transfer tube and substantially parallel to the gas flow direction. Therefore, the cooling medium that mainly uses engine cooling water orthogonal to the gas flow is narrowed by the flat heat transfer tube, and the flow rate is increased to increase the flow rate in the tube. On the other hand, the gas flow is cored by a number of segments in an alternating stack of flat heat transfer tubes and flat heat transfer tubes by interposing and fixing a large number of fins on the outer surface of the flat heat transfer tubes. And the gas heat is transferred to the outer surface of the flat heat transfer tube and a large number of fins in the meantime, and is orthogonal to the gas flow. do it, Serial The flat heat transfer tube is securely heat transfer to the cooling medium passing through at high speed is effectively heat exchanger.

  The aspect ratio of the core formed by the flat heat transfer tubes and the fins fixed thereto, that is, the ratio of the flat heat transfer tube length / EGR gas flow path length is 1: 1.5 to 1: 7, Preferably, the ratio of 1: 2.5 to 1: 5 can further improve the heat transfer performance and further enhance the cooling efficiency of the EGR gas. Further, the shape of the fin for fixing the fin fixed to the outer surface of the flat heat transfer tube so as to meander with respect to the gas flow direction, or to meander or fix the core to be formed in the same direction of gas flow. Corrugated fins, or by providing louvers, through holes, pin fins, etc. to the plate fins, not only lengthen the gas flow path but also cause turbulence and vortices as appropriate, and contact with the fins It is possible to further enhance the cooling efficiency by effectively promoting the heat transfer to the flat heat transfer tubes via the fins.

  Further, the core formed by interposing and fixing the corrugated fins between the flat heat transfer tubes or between the flat heat transfer tubes and the gas pipe acts as a strong support, and has a reinforcing effect. Because it can be used as the gas cooling device installed under severe operating conditions, it can be used as it is, making it possible to reduce the size and weight of the device, making the cooling device more compact and limited. It can be installed easily in an open space.

  A gas cooling device according to a sixth aspect of the present invention has a wedge-shaped shape in which the cross-sectional shape of the heat transfer tube is gradually expanded in width from the upstream side (front end portion) to the downstream direction (rear end portion) in the gas flow direction. Since the gas is cooled by the cooling medium that flows in the wedge-shaped heat transfer tube, the gas flow of the gas flows downstream while repeatedly colliding with all the inclined heat transfer surfaces of the cooled heat transfer tube. However, at this time, the gas flow proceeds while gradually peeling the boundary layer simultaneously with the collision with the inclined heat transfer surface, so that the surface condition on the heat transfer surface is improved, and the gas flow The process proceeds downstream without increasing the thickness of the layer, and effective heat exchange proceeds on all the heat transfer surfaces to ensure excellent cooling efficiency. In addition, the gas flow traveling downstream on the outer peripheral surface of the heat transfer tube having a wedge-shaped cross section undergoes a sudden cross-sectional change on the rear side of the heat transfer tube to generate a so-called “Kalman vortex street”, increasing the flow velocity and transferring the gas flow. Effective heat exchange is promoted on all the heat transfer surfaces of the heat transfer tube including the heat transfer surface arranged on the back surface or downstream side of the heat tube, and excellent cooling performance can be exhibited. On the other hand, the cooling medium flowing through the wedge-shaped heat transfer tube has its flow path narrowed at the narrow end face of the heat transfer tube, and the cooling efficiency is increased by passing through the tube at an increased flow rate. On the downstream side where the width is expanded, a large amount of cooling water flows with a low flow resistance to control boiling, and effective heat exchange is achieved along with the expanded surface area. Contributes to improvement.

  In addition, by fixing the plate fin of the arbitrary shape in close contact with each other between the wedge-shaped heat transfer tubes or between the heat transfer tube and the gas pipe, the heat transfer area can be further increased to further improve the heat exchange efficiency. In addition, it acts as a strong support in the gas piping and exerts a reinforcing effect, so it can be used as it is as a gas cooling device placed under severe operating conditions. And can be easily installed in a limited space.

  In the gas cooling device according to the seventh aspect of the present invention, the heat transfer tube row is provided by alternately providing a weir at each boundary of a plurality of heat transfer tube row groups arranged in the device, and arbitrarily changing the position of the weir. Since the flow path of the cooling medium flowing through the group can be controlled as desired, the flow direction flow velocity and flow rate can be arbitrarily controlled, and the cooling medium can be controlled to a desired heat transfer tube array group, and further to the heat transfer tube. It is also possible to concentrate the flow through the individual heat transfer tubes of the row group unit, reduce the stagnation and flow rate variation in the cooling medium flow path of the cooling device, and cause the boiling of the cooling medium and the Bubbles generated by boiling can be promptly peeled and moved from the heat transfer surface to prevent a decrease in cooling efficiency.

In addition, the shape of the heat transfer tube to be incorporated is free, and can be appropriately selected from various types of conventionally used cylindrical tube tubes, oblong flat tubes, metal tubes processed into wedge-shaped cross sections, etc. It is. Furthermore, between the heat transfer tubes or between the heat transfer tube and the gas pipe, by fixing the plate fin of the arbitrary shape in close contact, the heat transfer area is increased, and further heat exchange efficiency is achieved. Since it acts as a strong support in the gas pipe and exerts a reinforcing effect, it can be used as it is as the gas cooling device placed under severe operating conditions, making the device smaller and lighter and compact And can be easily installed in a limited space.
Furthermore, irregularities may be formed on the wall of the gas pipe (including the trunk pipe), the cooling pipe or the heat transfer pipe of the gas cooling apparatus of the present invention as necessary to increase the turbulent flow or heat transfer area.

  In the gas cooling device according to the present invention, for example, by using engine cooling water as a cooling medium, the heat transfer coefficient of the inner surface of the flat heat transfer tube is almost 10 times that of EGR gas. The gas in contact is reliably cooled, and excellent heat exchange performance can be obtained.

1 to 18 are gas cooling apparatuses corresponding to claims 1 to 5 of the present invention. FIG. 1 is a longitudinal side view showing a part of the apparatus of the first embodiment, and FIG. FIG. 3 is a longitudinal sectional front view on the roll line of FIG. 1, FIG. 4 is a longitudinal sectional side view showing a part of the apparatus of the second embodiment omitted, and FIG. 5 is a transverse planar view on the haha line of FIG. 6 is a longitudinal side view showing the third embodiment apparatus with a part omitted, FIG. 7 is a transverse plan view on the Nini line of FIG. 6, and FIG. 8 is a cooling in the third embodiment apparatus shown in FIGS. FIG. 9 is a sectional view showing an example of a joining structure of a pipe (heat transfer tube) and a plate fin, FIG. 9 is a sectional view showing various structural examples of the plate fin in the third embodiment apparatus shown in FIG. 6 and FIG. Plate fins with through-holes, (b) and (c) plate fins with louvers, (d) pre-pin fins Tofin, (e) denotes a plate fin having irregularities by press molding. FIG. 10 is a longitudinal side view showing the apparatus of the fourth embodiment with a part thereof omitted, FIG. 11 is a cross-sectional plan view on the hoho line in FIG. 10, FIG. 12 is a longitudinal front view on the hae line in FIG. FIG. 14 is a front view of the longitudinal section on the tote line in FIG. 13, and FIGS. 15A and 15B are enlarged views of corrugated plate parts in the fifth embodiment apparatus. It is a fragmentary perspective view.
FIGS. 16 to 23 show a gas cooling device corresponding to claim 6 of the present invention, in which FIG. 16 is a longitudinal side view showing the device of the sixth embodiment, FIG. 17 is a perspective view showing plate fins in the device, and FIG. 18 is a cross-sectional plan view on the teach line in FIG. 16, FIG. 19 is a longitudinal front view on the reel line in FIG. 16, FIG. 20 is a longitudinal side view showing the apparatus of the seventh embodiment, and FIG. The perspective view which shows the plate fin in an example apparatus, FIG. 22 is the cross-sectional top view on the Noon line of FIG. 20, FIG. 23 is the vertical front view on the Rule line of FIG.
FIGS. 24 to 34 are gas cooling apparatuses corresponding to the seventh to eleventh aspects of the present invention, FIG. 24 is a schematic perspective view of the main part showing the eighth embodiment apparatus, and FIG. 25 is the same as the embodiment apparatus. FIG. 26 is a perspective view of the principal part of the flexible molding part in the apparatus of the embodiment, FIG. 27 is a longitudinal front view of the ninth embodiment apparatus, and FIG. 28 is the tenth embodiment apparatus. FIG. 29A is a cross-sectional plan view, FIG. 29B is a vertical front view, FIG. 29 is an eleventh embodiment device, FIG. 29A is a cross-sectional plan view, FIG. FIG. 31 shows a cross-sectional plan view, FIG. 31 shows a thirteenth embodiment device, (a) a cross-sectional plan view, and (b) a vertical front view, FIG. 32 is a perspective view showing a part of a corrugated fin having undulations optionally used in the eighth embodiment apparatus to the thirteenth embodiment apparatus. A.
FIGS. 33 to 40 are gas cooling apparatuses corresponding to claims 12 to 17 of the present invention. FIG. 33 is a schematic front view showing a fourteenth embodiment apparatus, and FIG. FIG. 35 is a schematic front view showing the fifteenth embodiment apparatus, FIG. 36 is a partially enlarged sectional view partially showing the embodiment apparatus, and FIG. 37 is used in the embodiment apparatus. FIG. 38 is a perspective view showing a single piece of various fins that can be arbitrarily used in each example device, and FIG. 38A is a view provided with a circular hole. FIG. 39 (a) shows a case in which unevenness with a semicircular cross section is provided, FIG. 39 (c) shows a case in which folds with an uneven cross section are provided over the entire length, and FIG. ) (B) (c) provided louvers among various fins Illustrated perspective view from FIG. 40 is a plan view showing an assembled state of the fin partially.
FIGS. 41 to 48 are gas cooling apparatuses corresponding to claims 18 to 27 of the present invention. FIG. 41 is a schematic front view showing the apparatus of the sixteenth embodiment, and FIG. 42 is a view of the heat transfer tube in the apparatus of the same embodiment. FIG. 43 is a partially enlarged perspective view partially showing another embodiment, FIG. 43 is a front view partially showing another embodiment of the heat transfer tube, and FIG. 44 is a partial view of still another embodiment of the heat transfer tube. 45 is a plan view partially showing still another embodiment of the heat transfer tube, FIG. 46 is a schematic three-view diagram showing the seventeenth embodiment device, (a) is a plan view thereof, and (b) is a plan view thereof. Is a longitudinal side view thereof, (c) is a cross-sectional plan view on the line A of (a), FIG. 47 is a partial view of various fins that can be arbitrarily used in the devices of the above embodiments, (a) Is an I-shaped fin, (b) is an S-shaped fin, and (c) is a perspective view showing a U-shaped fin. FIG. 48 is a cross-sectional view showing the structure of the plate fin. (A) is a plate fin provided with a through hole, (b) and (c) are provided with a louver, and (d) is provided with a pin fin. And (e) show those provided with irregularities.
49 to 56 are gas cooling apparatuses corresponding to claims 28 to 31 of the present invention, wherein FIG. 49 is a longitudinal side view showing the apparatus of the eighteenth embodiment, and FIG. 50 is a cross-sectional view on the rule line of FIG. FIG. 51 is a longitudinal front view of FIG. 49 taken along the line of FIG. 49. FIG. 52 is a longitudinal side view of the nineteenth embodiment. FIG. FIG. 52 is a perspective view showing an example of a single heat transfer tube according to the present invention, and FIG. 56 is a perspective view showing another example of the single heat transfer tube.
57 to 74 are gas cooling devices corresponding to claims 32 to 36 of the present invention. FIG. 57 is a longitudinal side view showing a part of the nineteenth embodiment omitted, and FIG. 58 is a side view of FIG. 59 is a cross-sectional plan view on the line Y, FIG. 59 is a vertical front view on the line of FIG. 57, FIG. 60 is a vertical side view showing a part of the twentieth embodiment omitted, and FIG. 62 is a longitudinal sectional side view showing the apparatus of the 21st embodiment with a part thereof omitted, FIG. 63 is a transverse plane view on the source line of FIG. 62, and FIG. 64 is the apparatus of the 22nd embodiment. FIG. 65 is a cross-sectional plan view taken along the line of FIG. 64, FIG. 66 is a longitudinal front view of the line of FIG. 64, and FIG. 68 is a vertical side view of the vertical section on the null line of FIG. 67, and FIG. 69 is a vertical view of the apparatus shown in FIG. 70 is a cross-sectional plan view on the line of FIG. 69, FIG. 71 is a longitudinal front view on the line of FIG. 69, and FIG. 72 is a longitudinal side view partially omitting the 25th embodiment. 73, FIG. 73 is a transverse plan view on the Wu line in FIG. 74, FIG. 74 is a longitudinal front view on the Nono line in FIG. 72, and FIG. 75 is a wall surface of a gas pipe (including a trunk pipe) of each apparatus of the present invention. FIG. 76 is a partial cross-sectional view showing an example of the cross-sectional structure of the wall surface of the cooling pipe or the heat transfer tube of each embodiment of the present invention.
Here, an EGR gas cooling device will be described as an example.

  First, the EGR gas cooling device 1 shown in FIG. 1, FIG. 2, and FIG. 3 is perpendicular to the gas flow direction (arrow g) of the EGR gas flowing in the EGR gas pipe 2 whose diameter is expanded to a rectangular cross section. A large number of cooling pipes (heat transfer pipes) 3 intersecting with each other are fixedly arranged at predetermined intervals through the outer peripheral wall of the EGR gas pipe as both pipe ends of the pipes open to the outside. Then, the cooling jackets 4-1 and 4-2 are fixed to the outer surfaces of the EGR gas pipes on both sides in the pipe axis direction of the cooling pipe. The cooling jackets 4-1 and 4-2 are respectively provided with an inlet P1 and an outlet P2 for the cooling medium.

  In the EGR gas cooling device 1 configured as described above, the EGR gas flowing in the direction of the arrow g in the EGR gas pipe 2 is cooled by the cooling medium flowing in the direction of the arrow c in each cooling pipe 3 from one cooling jacket 4-1. . At this time, since the EGR gas flowing through the EGR gas pipe 2 is turbulent by the multiple cooling pipes 3 arranged so as to intersect the gas flow, the EGR gas flow is circulated in the multiple cooling pipes 3. Heat exchange with the cooling medium flowing in the orthogonal direction (direction of arrow c) is promptly performed.

The EGR gas cooling device 11 shown in FIGS. 4 and 5 has the same configuration as the cooling device shown in FIGS. 1 and 2 except that finned tubes 13-1 and 13-2 are used for cooling piping. That is, a large number of finned tubes 13-1 and 13-2 that intersect the EGR gas pipe 12 expanded in a rectangular cross section at right angles to the gas flow direction (arrow g) of the EGR gas flowing in the pipe, As the both pipe ends of each pipe open to the outside, they pass through the outer peripheral wall of the EGR gas pipe and are fixedly arranged at a predetermined interval, and the cooling jacket 14-1 is attached to the outer surface of the EGR gas pipe on both sides in the pipe axis direction of the cooling pipe. 14-2 are fixed. Here, the finned tube 13-1 is provided with spiral fins 13-1a on the outer peripheral surface of the tube main body, and the tube 13-2 with fins is provided with disc-shaped fins 13-2a on the outer peripheral surface of the tube main body. It is a thing.
In addition, although the structure which combined the tube 13-1 with a spiral fin and the tube 13-2 with a disk-shaped fin was shown here, a corrugated fin and a pin-shaped fin outside a spiral fin and a disk-shaped fin were shown. Etc., and may be configured by combining various types of finned tubes using only one type of tube, for example, only a spiral finned tube 13-1 or a disk-shaped finned tube 13-2. Needless to say, it may be configured by.

  In the case of the EGR gas cooling device 11 having the configuration shown in FIGS. 4 and 5, the EGR gas flowing in the direction of the arrow g in the EGR gas pipe 12 is supplied to one cooling jacket 14 as in the devices shown in FIGS. 1 and 2. -1 is cooled by the cooling medium flowing in the direction of the arrow c in the finned tubes 13-1 and 13-2. At this time, the EGR gas flowing through the EGR gas pipe 12 is not only turbulent in gas flow by the finned tubes 13-1 and 13-2 disposed so as to cross the gas flow, but also spiral fins. 13-1a and the stirring action of the disk-shaped fins 13-2a are added to perform heat transfer more quickly, and high heat exchange performance is obtained due to the effect of increasing the heat transfer area of the fins.

  The EGR gas cooling device 21 shown in FIG. 6 and FIG. 7 is parallel to the gas flow in the EGR gas pipe and perpendicular to the cooling pipe in the EGR gas pipe 22 in the heat exchange region where the cooling pipe group is fixedly arranged. Except for the provision of the plate fins 25, the configuration is the same as that of the EGR gas cooling apparatus 1 shown in FIGS. That is, a large number of cooling pipes 23 intersecting at right angles to the gas flow direction (arrow g) of the EGR gas flowing in the EGR gas pipe 22 having an enlarged diameter in cross section are connected to both ends of each pipe. A gas flow (in the EGR gas pipe 22 in which a large number of cooling pipes 23 are arranged and fixed in a predetermined interval through the outer peripheral wall of the EGR gas pipe as it opens to the outside (flowing through the gas pipe ( Here, five plate fins 25 parallel to the arrow g) and perpendicular to the cooling pipe 23 are arranged at regular intervals, and cooling jackets 24-1 and 24- are provided on the outer surface of the EGR gas pipe on both sides in the pipe axis direction of the cooling pipe. 2 is fixed.

  In the case of the EGR gas cooling device 21 having the configuration shown in FIGS. 6 and 7 as well, the EGR gas flowing in the direction of the arrow g in the EGR gas pipe 22 is supplied to one cooling jacket 24 as in the devices shown in FIGS. -1 is cooled by the cooling medium flowing in each cooling pipe 3 in the direction of the arrow c. At this time, the EGR gas flowing through the EGR gas pipe 22 is arranged so as to intersect with the gas flow. 3 not only makes the gas flow turbulent, but also increases the heat transfer area by the plate fin 25 parallel to the gas flow (arrow g) flowing through the gas pipe and perpendicular to the cooling pipe 23. Also in this case, heat transfer is performed more quickly, and higher heat exchange performance can be obtained.

  Moreover, as shown in FIG. 8, the cooling pipe 23 of the plate fin 25 is inserted as the joining structure of the cooling pipe 23 and the plate fin 25 in the EGR gas cooling device 21 with the plate fin 25 built-in shown in FIGS. In order to increase the contact area between the plate fin and the cooling pipe, a burring wall 25-1 may be provided in the through-hole.

  Further, in order to increase the turbulent flow and the stirring action of the EGR gas flowing through the EGR gas pipe 22, for example, as shown in FIG. 9, a large number of through holes 25-2 (FIG. A) and louvers 25- 3 (FIG. B), 25-4 (FIG. C), pin fins 25-5 (FIG. D), and unevenness 25-6 (FIG. E) by press molding may be provided. Note that the unevenness 25-6 shown in FIG.

  The EGR gas cooling device 31 shown in FIG. 10, FIG. 11 and FIG. 12 intersects an EGR gas pipe 32 whose diameter is expanded to a rectangular cross section at right angles to the gas flow direction (arrow g) of the EGR gas flowing in the pipe. In the same manner as described above, a number of flat tubes 33 are fixedly arranged at predetermined intervals through the outer peripheral wall of the EGR gas pipe so that both ends of the flat tubes 33 open to the outside. This is a so-called double pipe type in which a cooling jacket 34 whose inside is divided into two upper and lower parts via a separator 34-1 is fixed to the entire outer periphery of the pipe 32.

In the case of the EGR gas cooling device 31 of the double pipe type configured as shown in FIGS. 10, 11, and 12, the EGR gas flowing in the direction of the arrow g in the EGR gas pipe 32 surrounds the EGR gas pipe 32. It cools with the cooling medium which flows in the inside of each flat tube 33 from the cooling jacket 34 provided in the arrow c direction. Also in the case of this EGR gas cooling device 31 of the double pipe type, the EGR gas flowing in the EGR gas pipe 32 is turbulent in the gas flow by the flat tube 33 arranged so as to intersect the gas flow. Heat exchange with the cooling medium flowing in the direction (arrow c direction) orthogonal to the EGR gas flow in the many flat tubes 33 is performed quickly.
In this embodiment, the arrangement of the flat tubes 33 is changed between the entry side and the exit side of the EGR gas pipe 32. However, the arrangement of the flat tubes 33 is not limited to this arrangement, and the EGR gas pipe is arranged. Needless to say, the entire 32 may be configured by the arrangement of the flat tubes 33 on the entry side or the exit side.

  The EGR gas cooling device 41 shown in FIG. 13 and FIG. 14 has a number of EGR gas pipes 42 whose diameters are expanded to a rectangular cross section, and intersect with the gas flow direction (arrow g) of EGR gas flowing through the pipes at right angles. The flat tubes 43 are juxtaposed in parallel so as to be multistage in parallel with each other through the side walls of the EGR gas pipe as the both ends of the flat tubes 43 open to the outside. Between the flat tubes 43, two types of corrugated plates 45a and 45b shown in an enlarged manner in FIG. 15 are divided into several stages, respectively, and interposed in the longitudinal direction of the EGR gas pipe 42 to form flow paths 46a and 46b. A gas jacket 42 is formed by fixing a cooling jacket 44, which is divided into two left and right sides through a separator 44-1, around the entire outer periphery of the gas pipe 42. Is

  Of the two types of corrugated plates 45a and 45b, one corrugated plate 45a has a rounded top 45a-1 as shown in FIG. The other corrugated plate 45b has a flat top portion 45b-1 as shown in FIG. 15 (b), and the flat surface between the top portions is formed as an uneven barrier 45b-2. A turbulent flow or a vortex flow is generated in the flow of the gas flowing inside, so that the heat exchange efficiency of the EGR gas can be further improved. Also, in the case of the EGR gas cooling device 41 shown in FIGS. 13 and 14, here, an example is shown in which the corrugated plate 45a is disposed on the upper side of the EGR gas pipe 42 and the corrugated plate 45b is disposed on the lower side. On the contrary, the corrugated plate 45b may be disposed on the upper side and the corrugated plate 45a may be disposed on the lower side, or the entire EGR gas pipe 42 may be composed of either one of the corrugated plates. Absent.

  In the case of the EGR gas cooling device 41 of the double pipe type configured as shown in FIGS. 13 and 14, the EGR gas flowing in the direction of the arrow g in the EGR gas pipe 42 is provided so as to surround the EGR gas pipe 42. The cooling jacket 44 cools each flat tube 43 by a cooling medium flowing in the direction of arrow c. In the case of this double pipe type EGR gas cooling device 41, the EGR gas flowing in the EGR gas pipe 42 flows while flowing through the flow paths 46a and 46b formed by the two types of corrugated plates 45a and 45b. Since turbulent flow or vortex flow is generated in the flow, heat exchange with the cooling medium flowing in the direction (arrow c direction) orthogonal to the EGR gas flow in a number of flat tubes 43 is performed quickly, and higher heat exchange efficiency is obtained. It is done.

The arrangement, number, thickness, etc. of the cooling pipes 3, 23, finned tubes 13-1, 13-2, and flat tubes 33, 43 in the EGR gas cooling device described above are not particularly limited. It is determined appropriately according to the size of the gas pipes 2, 12, 22, 32, 42, the scale of the cooling device, and the like. In addition, the cooling pipe is shown here as a circular pipe or a flat pipe with a perfect cross-sectional shape, but the invention is not limited to this, and an elliptical circular pipe, a pipe with a rectangular or polygonal cross section, etc. can also be used. Not too long. Moreover, welding, brazing, etc. can be used as the close contact and fixing means of each part.

  Next, the EGR gas cooling apparatus 101 shown in FIGS. 16 to 19 is perpendicular to the gas flow direction (arrow g) of the EGR gas flowing in the EGR gas pipe 102 whose diameter is expanded to a rectangular cross section. The core 103 composed of a plurality of plate fins 103-1 having a large number of intersecting tubular coolant flow paths 103-2 is arranged so that each plate fin 103-1 is parallel to the gas flow in the EGR gas pipe. The cooling jackets 104-1 and 104-2 provided with the cooling medium inlet P1 and the outlet P2 are fixed to the outer surfaces of the EGR gas pipes at both ends of the tubular cooling medium flow path 103-2. It is configured.

As shown in FIG. 17, the core 103 in the EGR gas cooling device 101 is subjected to burring on a single plate to form a protruding circular body 103-3 having a perfectly circular cross section with a predetermined height and width in a predetermined direction. For example, a plurality of plate fins 103-1 (in this case, 5) formed, for example, with 15 intervals are produced, and the five plate fins 103-1 are mutually connected so that the projecting cylinders 103-3 are matched. The protruding cylindrical body portion is overlapped and joined to the other plate fin 103-1 by welding or brazing to form 15 tubular cooling medium flow paths 103-2.
When the core 103 assembled in this way is installed in the EGR gas pipe 2, the EGR gas is inserted into the EGR gas through a rectangular window hole formed by cutting and removing one outer wall of the EGR gas pipe 102 in advance. Inserted into the pipe 102, the opening end of the outer projecting cylinder 103-3 constituting each tubular cooling medium flow path 103-2 of the core was previously drilled in the outer peripheral wall of the EGR gas pipe 2 The part is fixed by welding or brazing by fitting it into a circular hole of the same shape, and the four sides of the plate fin 103-1 located outside the opposite side are welded or brazed to the outer wall of the EGR gas pipe 102 Join with.

  In the EGR gas cooling apparatus shown in FIGS. 16 to 19, the EGR gas flowing in the direction of the arrow g in the EGR gas pipe 102 flows from each cooling jacket 104-1 to each tubular cooling medium flow path 103-2 of the core 103. It is cooled by a cooling medium (for example, cooling water) flowing in the direction of arrow c. At this time, the EGR gas flowing in the EGR gas pipe 102 is not only turbulent but also turbulent by the numerous tubular cooling medium flow paths 103-2 of the core 103 disposed so as to intersect the gas flow. The heat transfer area is further increased by the plate fin 103-1 parallel to the gas flow (arrow g) flowing through the gas pipe and perpendicular to the tubular cooling medium flow path 103-2. And higher heat exchange performance is obtained.

The EGR gas cooling device 111 shown in FIG. 20 to FIG. 23 is configured by fixing a cooling jacket 114, which is divided into two upper and lower parts via a separator 114-1, around the entire outer periphery of the EGR gas pipe 112. It is what is called a double pipe type, and is comprised by the flat tubular cooling medium flow path 113-2.
In other words, this EGR gas cooling device 111 has a number of tube-shaped coolings intersecting at right angles to the gas flow direction (arrow g) of the EGR gas flowing in the EGR gas pipe 112 whose diameter is expanded to a rectangular cross section. A core 113 composed of a plurality of plate fins 113-1 having a medium flow path 113-2 is housed and installed so that each plate fin 113-1 is parallel to the gas flow in the EGR gas pipe, and this EGR gas A cooling jacket 114 is provided on the entire outer periphery of the pipe 112. The cooling jacket 114 is divided into an upper part and a lower part through a separator 114-1, and a cooling medium inlet P1 is provided on one side and an outlet P2 is provided on the other side. It is configured as follows.

Similarly to the cooling device shown in FIGS. 16 to 19, the core 113 in the EGR gas cooling device 111 is also a protruding cylinder having a flat cross section having the same height as shown in FIG. For example, five plate fins 113-1 each having nine bodies 113-3 formed at predetermined intervals in the vertical direction and the horizontal direction are manufactured. The five plate fins 113-1 are each formed into a flat projecting cylindrical body 113. -3 are overlapped with each other so as to match, and the projecting cylindrical part is joined to the other plate fin 113-1 by welding or brazing to form nine flat tubular coolant flow paths 113-2. Is.
When the core 113 assembled in this manner is installed in the EGR gas pipe 112, the core 113 is inserted into the EGR gas pipe from a rectangular window hole formed in advance on one outer wall of the EGR gas pipe 112, as described above. 112 is inserted into the outer peripheral wall of the EGR gas pipe 112 in advance. This portion is fitted into an elliptical hole having the same shape and fixed by welding or brazing, and the four sides of the plate fin 113-1 positioned outside the opposite side are welded to the outer wall of the EGR gas pipe 2 or Join by brazing.

  In the case of the double-tube type EGR gas cooling device 111 configured as shown in FIGS. 20 to 23, the EGR gas flowing in the direction of the arrow g in the EGR gas pipe 112 is provided so as to surround the EGR gas pipe 112. The cooling jacket 114 is cooled by a cooling medium (for example, cooling water) flowing in the direction of the arrow c in each flat tubular cooling medium flow path 113-2 of the core 113. Also in the case of this double pipe type EGR gas cooling device, the EGR gas flowing in the EGR gas pipe 112 is the flat tubular cooling medium flow path 113 of the core 113 disposed so as to intersect the gas flow, as described above. -2 not only makes the gas flow turbulent, but also transfers heat by plate fins 113-1 parallel to the gas flow (arrow g) flowing in the gas pipe and perpendicular to the flat tubular coolant flow path 113-2. In addition to the increase in area, heat transfer is performed more quickly, and higher heat exchange performance is obtained.

  It should be noted that the number, thickness, etc. of the plate fin projecting cylinders 103-3, 113-3 constituting the cooling medium flow path in the EGR gas cooling apparatus shown in FIGS. 16 to 23 are not particularly limited. Rather, it is appropriately determined according to the size of the EGR gas pipes 102 and 112, the scale of the cooling device, and the like. In addition, the plate fins are subjected to various processes shown in FIG. 9 (corrugated processes, through holes, louvers, irregularities, etc.) for the purpose of improving heat transfer performance by gas turbulence, diffusion, mixing, etc. Also good. Further, the cooling medium flow path has a perfect circle or ellipse here, but the present invention is not limited to this, and it goes without saying that the same effect can be obtained even with a rectangular or polygonal cross section. . Furthermore, in the apparatus of this embodiment, the entire EGR gas pipes 102 and 112 are configured by the same cooling medium flow path, but the entire EGR gas pipe has a cross-sectional shape and size on the inlet side or the outlet side. Needless to say, the cooling medium flow paths may be different.

  The EGR gas cooling device 201 shown in FIG. 24 includes a cooling jacket 202-1 having an inlet P1 of a cooling medium c mainly using engine cooling water on both sides of a trunk pipe 206 having a substantially rectangular cross section. , A cooling jacket 202-2 having an outlet P2 is arranged in a face-to-face relationship, between the two cooling jackets 202-1 and 202-2, passing through the body tube 206, and with respect to the gas flow direction g. A plurality of cross-sections that intersect at right angles are circular, oval, elliptical, rectangular or the like, and heat transfer tubes 203 are disposed to form a flow path for cooling water c. Furthermore, the gas cooling apparatus 201 according to the present embodiment is parallel to the gas flow direction g on the wall surface except for the portion covered by the two cooling jackets 202-1 and 202-2 of the trunk pipe 6. Thus, a plurality of flexible moldings are performed to form a recess as shown in FIG. In FIG. 25, 205 is a flexible molding part.

  The gas passing through the device by the delicate recess formed by the flexible molding causes turbulent flow on the wall surface and increases the outer surface area, and a considerable heat dissipation effect is recognized, but in this example, Further, as shown in FIG. 24, a plurality of plate fins 204-1 are arranged in parallel to the gas flow direction g on the outer wall surface except for the portions covered by the two cooling jackets 202-1 and 202-2. And a plurality of plate fins 204-2 are also joined to the outer surface of the heat transfer tube 203 in parallel to the gas flow direction g. In addition, in this embodiment, as shown in FIG. 24, the other end of the plate fin 204-3 joined to the outer surface of the heat transfer tube 203 disposed on the wall surface side is inserted into the recess formed by the flexible molding. And by sandwiching them as a unit, the heat transfer effect is increased, and the high heat transfer coefficient of the cooling water flowing between the two cooling jackets through the plurality of heat transfer tubes acts synergistically and is excellent. Cooling efficiency can be obtained.

  The two large and small flexible molded portions shown in FIG. 26 are an application example of the present embodiment, in which deep concave portions 205-1 and shallow concave portions 205-2 are alternately formed, and the heat transfer tube 3 is formed in the deep inner concave portion 205-1. The other end of the plate fin 204-4 joined to the outer surface is inserted and held together. With the above configuration, the heat transfer performance provided by the flexible molded part and the plate fins is further improved.

The EGR gas cooling device 201-1 shown in FIG. 27 has a cooling jacket 202-3 having a cooling medium inlet P1-1 and a cooling jacket 202-4 having an outlet P2-2 facing each other vertically. A plurality of heat transfer tubes 203-1 that are arranged and pass through the middle thereof and intersect at right angles to the gas flow direction g are arranged. This EGR gas cooling device 201-1 has a plurality of flexible moldings in parallel to the gas flow direction on the side wall portion excluding the portion covered with the two facing cooling jackets 202-3 and 202-4. Part 205-1 is formed, a plate fin 204-6 is joined to the outer surface of the heat transfer tube 203-1 in parallel to the gas flow direction g, and the heat transfer tube adjacent to the flexible molding part 205-1 The other end 204-5 of the plate fin 204-6 joined to the 203-1 is inserted and held in the concave portion of the flexible molding part 205-1.
The EGR gas cooling device 201-1 configured as described above includes a plurality of concave portions formed by the flexible molding portion 205-1 formed on the wall surface and a plurality of plate fins 204- joined to the outer surface of the heat transfer tube 203-1. 6 and the other end 204-5 of the plate fin 204-6 are inserted into the concave portion of the flexible molding portion 205-1 so that the heat of the gas flowing into the apparatus is effectively exchanged. Thus, excellent cooling efficiency can be obtained.

The EGR gas cooling apparatus shown in FIGS. 28 and 29 has a wall surface not covered by the cooling jackets 202-5 and 202-6, 202-7 and 202-8, and FIG. 28 shows the gas flow direction g. In FIG. 29, a plurality of flexible molding portions 205-2 that are parallel to the gas flow direction g are formed.
Although the EGR gas cooling devices 201-2 and 201-3 have a simple structure, the flexible molding portions 205-2 and 205-3 cause turbulent flow in the gas passing through the wall surface, The contact area with the outer wall portion is widened by the concave portion formed by molding, and the heat dissipation action is promoted, so that effective cooling efficiency can be obtained.

In addition, the EGR gas cooling device shown in FIG. 30 further improves the effect of the present invention by arbitrarily joining a heat radiating plate fin to a wall surface not covered by a facing cooling jacket. A plurality of heat radiating plate fins 204-7 intersecting at right angles to the gas flow direction g are joined to the wall surface not covered with the cooling jackets 202-9 and 202-10, or as shown in FIG. A plurality of heat dissipating plate fins 204-8 parallel to the gas flow direction g are joined to the wall surfaces not covered by the opposing cooling jackets 202-11 and 202-12.
The EGR gas cooling devices 201-4 and 201-5 are configured so that the heat of the gas passing through the vicinity of the wall surface that is not in direct contact with the cooling jacket is improved due to the heat dissipation action of the heat dissipation plate fins 204-7 and 204-8. Thus, it is possible to obtain an excellent cooling efficiency.
In the present invention, it does not prevent the direction of the heat dissipating plate fins 204-7 and 204-8 from intersecting. The heat dissipating plate fins 204-7 and 204-8 may be provided inclined with respect to the gas flow direction g.

  Moreover, as a fin used for the EGR gas cooling device, there is, for example, a rectangular corrugated plate 204a having a swell as shown in FIG. Furthermore, also in the EGR gas cooling device, various fins shown in FIGS. 9 to 12, that is, plate fins provided with a large number of through holes, plate fins provided with louvers, plate fins provided with pin fins, continuous fins, Or the plate fin provided with the intermittent unevenness | corrugation and the corrugated fin shown to the said Fig.15 (a) (b) can be used.

The EGR gas cooling apparatus shown in FIGS. 24 to 32 is provided with a plurality of heat transfer tubes arranged between two opposing cooling jackets and penetrating at right angles to the gas flow direction, and by the two cooling jackets. By applying multiple flex molded parts to the wall surface excluding the covered part in parallel or intersecting with the gas flow direction, or by selectively joining various plate fins, In addition to the expansion of the heat transfer area provided by the plate fins and the turbulent flow of the gas flow provided by the formed recess (outer surface is a protrusion), the outer surface of the cooling jacket or heat transfer tube cooled by the engine cooling water The heat transfer coefficient is approximately 10 times that of EGR gas, and so on, synergistically acting so that the heat exchange is carried out quickly and almost perfectly. It obtained an excellent cooling efficiency. Further, the flexible molded part also has an effect of relaxing thermal stress, and the durability of the EGR gas cooling device can be improved.
In addition, as shown in FIG.24 and FIG.27 for demonstrating the said EGR gas cooling device 201,201-1, the plate fins 204-3,204-4,204-5 joined to the outer surface of a heat exchanger tube are as follows. The other end is inserted into a concave portion formed by flexible molding on the smooth wall surface of the trunk tube 206 and is tightly sandwiched, and the heat transfer tubes 203 and 203-1 are similarly plate fins 204-2, 204-6 is joined to each other, so that they are supported by each other. As a result, a support body that reinforces the heat transfer tubes 203 and 203-1 and the trunk tube 206 is formed, thereby reducing the size of the apparatus. Also contributes.

  The EGR gas cooling device 301 shown in FIG. 33 includes a cooling medium inlet P1 and an outlet P2 for cooling medium mainly using engine cooling water above and below an EGR gas pipe 302 having a substantially rectangular cross section. Jackets 304-1 and 304-2 are disposed, and a plurality of flat transmissions intersecting the EGR gas pipe 302 between the cooling jackets 304-1 and 304-2 and intersecting at right angles to the gas flow direction. A heat pipe 303 is provided to form a flow path for the cooling water. Further, the EGR gas cooling device 301 includes a large number of channels divided between the flat outer surface of the flat heat transfer tube 303 and between the flat heat transfer tube 303 and the gas pipe 302 over the entire length or in the length direction. Basically, by fixing the fin 305 having a shape substantially parallel to the gas flow direction, a gas flow path is formed between the flat heat transfer tubes 3 or between the flat heat transfer tubes 303 and the gas pipe 302. It has a simple structure.

  The channel-shaped fins 305 are characterized by having a substantially U-shaped cross-section and having a length that extends over the entire length or is shortly divided, whereby the flat heat transfer tubes 303 or the flat heat transfer tubes are arranged. As shown in FIGS. 33 and 34, a large number of heat pipes 303 and gas pipes 302 are arranged at arbitrary positions and at arbitrary pitches in parallel with the gas flow direction. Fixed by attaching. As shown in FIG. 34, the channel-shaped fins 305 are brought into close contact with each other by bringing flat both side surfaces bent into a channel shape into contact with the flat outer peripheral surface of the flat heat transfer tube 303. Therefore, it is possible to obtain a wide heat transfer area and ensure mutual heat transfer in an ideal state, and the EGR gas passing through the gas cooling device having such a structure is quickly heat-exchanged and excellent Cooling efficiency is obtained.

  The channel-shaped fins 305 flow between the gas pipe 302 and a plurality of flat heat transfer pipes 303 that pass through the gas pipe 302 and intersect at right angles to the gas flow direction. The position and pitch are arbitrary as long as they are arranged and fixed substantially parallel to the direction, but the shape can be freely changed in design.

  For example, in the embodiment apparatus shown in FIG. 35, a part of the belt-like fin is cut and raised in accordance with the width of the flat heat transfer tube 303 to form a partly raised belt-like fin 305-1 as shown in FIG. The fins 305-1 are arranged and fixed so as to cooperate with each other as shown in FIG. 36 in the gaps between the flat heat transfer tubes 3 or between the flat heat transfer tubes 303 and the gas pipe 302, and thereby the heat transfer performance. It has been confirmed that this can be further improved.

In another embodiment, a channel-shaped fin 305-4 having a through hole as shown in FIG. 38 (a) is formed on a part of the channel-shaped fin as desired, as shown in FIG. 38 (b). ), A channel-shaped fin 305-5 provided with semicircular irregularities in cross section, as shown in FIG. 38C, and a channel-shaped fin 305-6 provided with pleats in cross-sectional unevenness as shown in FIG. It is also possible to form channel-shaped fins 305-7 provided with lip-shaped bent portions as shown in FIG. 38 (d), and various louvers as shown in FIGS. 39 (a) to (c) are provided. The channel-shaped fins 305-8 to 305-10 are formed and employed as part or all of the channel-shaped fins incorporated in the EGR gas cooling device according to the present invention. It can be achieved initial results by the stirring action of the scan. In addition, the louvers of different forms shown in FIGS. 39A to 39C are examples, respectively. For that purpose, turbulence and vortex flow are generated in the gas flow path, and the heat transfer area is expanded. The design can be freely changed as long as the cooling efficiency can be increased by promoting effective heat exchange. These fins can be used alone or in combination with other fins including various channel fins used in the above embodiments.
The channel-shaped fins that are arbitrarily adopted in each of these embodiments have a flat bent portion only at the junction with the flat heat transfer tube 303, and the flat bent portion and the flat heat transfer tube. By abutting the flat surface of 303, the joining is facilitated, and at the same time, mutual adhesion is ensured and the excellent heat transfer performance is maintained.

  Further, in each of the above embodiments, the means for assembling the channel-shaped fins is not particularly limited and is arbitrary, but as an example, a flat fin material is temporarily bent as shown in FIG. As shown in 40 (b) and (d), a bent portion is provided in accordance with the gap between the flat heat transfer tubes 305, and then pushed into the gap between the flat heat transfer tubes 303, so that the flat surfaces of each other are provided. As shown in FIGS. 40 (c) and (e), channel fins 305-2 or 305-3 are formed as shown in FIGS. 40 (c) and 40 (e), and the respective welded portions 306 are fixed by brazing, for example. The

The EGR gas cooling apparatus shown in FIGS. 33 to 40 is added to the flat outer surface of the flat heat transfer tube 303 that passes through the expanded gas pipe 302 and intersects the gas flow direction at a right angle. A plurality of preferably channel-shaped fins 305 that are fixed at random, with their flat bent portions closely contacting the flat outer surface of the flat heat transfer tube 303 in parallel with the gas flow direction. The heat transfer area is further expanded, the edge effect is obtained and the shape of the outer surface of the flat heat transfer tube 303, the turbulent flow of the gas flow caused by the channel shape fins 305 fixed at random, and the engine cooling water Synergistically, the heat transfer coefficient of the inner surface of the flat heat transfer tube 3 to be cooled is about 10 times that of the EGR gas as in the EGR gas cooling device shown in FIGS. Acts on, the heat exchange is rapidly and almost completely carried out, obtain a superior cooling efficiency.
33 to 40 are fixed between the flat heat transfer tubes 303 or between the flat heat transfer tubes 203 and the gas pipe 202 to form a core. Therefore, the flat heat transfer pipes 203 and the gas pipe 202 are connected to each other. This contributes to the downsizing of the device.

  An EGR gas cooling device 401 shown in FIG. 41 has an inlet (not shown) for a coolant mainly using engine cooling water and an outlet (not shown) on both sides of an EGR gas pipe 403 having a substantially rectangular cross section. A plurality of flat heat transfer tubes 404 that intersect between the cooling jackets 402 and pass through the EGR gas pipe 403 and intersect at right angles to the gas flow direction. The cooling water flow path (c) is formed. Further, the EGR gas cooling device 401 is configured such that the corrugated fins 405 are alternately interposed in parallel to the gas flow direction on the flat outer surface of the flat heat transfer tubes, thereby fixing the flat heat transfer tubes 404 or The basic structure is to form a gas flow path (g) between the flat heat transfer tube 4 and the gas pipe 3 as one segment of the core.

  The core composed of each segment is designed so as to increase the cooling efficiency as much as possible by defining the length of the EGR gas flow path (g) with respect to the flat heat transfer tube 404, but the aspect ratio is the length of the flat heat transfer tube 404. In the ratio of length / length of EGR gas flow path (g), a range of 1: 1.5 to 1: 7, preferably 1: 2.5 to 1: 5 is desirable, and its aspect ratio is 1: 1. In the case of 5 or less, since the gas flow path is short, the contact time between the gas and the heat transfer surface is too short, and sufficient heat transfer performance cannot be obtained. In this example shown in FIG. 41, the space is set to 1: 3. Note that a flat heat transfer tube 404 disposed in the cooling jacket 402 passes through the gas pipe 403 at a right angle to the gas flow direction, and an outer surface of the flat heat transfer tube 404 is parallel to the gas flow direction. In this example, the corrugated fins 405 interposed and fixed to each other are fixed by brazing. However, the fixing means may not select the heat transfer performance, for example, welding or the like can be selected.

  According to the EGR gas cooling apparatus 401 configured as described above, the flow rate of the cooling medium flowing between the cooling jackets 402, that is, the flow path (c) of the engine cooling water is narrowed by flattening the heat transfer pipe 404. On the other hand, the flow of the EGR gas is extended by the multiple fins formed by the corrugated fins 405, and the flow path (g) is extended to increase the contact time between the flat heat transfer tubes 404 and the fins 405. Expansion of the heat transfer area due to the flat outer surface of the heat transfer tube 404, turbulence of the gas flow caused by the shape of the outer surface, and the heat transfer coefficient of the inner surface of the flat heat transfer tube 404 cooled by engine cooling water However, it is about 10 times the heat transfer coefficient on the fin side (gas side) with respect to EGR gas, and so on. And is almost perfectly implemented, it was confirmed that the resulting superior cooling efficiency. As shown in FIG. 41, the corrugated fins 405 according to this example are alternately interposed between the flat heat transfer tubes 404 and fixed to form a core, so that the flat heat transfer tubes 404 and the gas pipe 403 are reinforced. This contributes to the compactness of the device.

  FIG. 42 is an enlarged perspective view partially showing the flat heat transfer tube 404-1 and the corrugated fin 405-1 fixed to the heat transfer tube. A substantially S-shaped rib 406 is provided at an arbitrary position on the inner surface, and functions to reinforce the flat heat transfer tube 404-1 and rectify the flow of the cooling medium.

  Further, a plurality of flat heat transfer tubes 404-2 are installed in parallel in the horizontal direction as shown in FIG. As a result, the strength of the individual flat heat transfer tubes 404-2 in the vertical direction is increased, and the flat width of the flat tubes 404-2 is small, so that the manufacture is easy.

  Furthermore, as shown in FIG. 44, the flat heat transfer tube 404-3 is formed by deforming the flat heat transfer tube 404-3 itself into a corrugated shape, and the corrugated fins 405-2 fixed thereto are also formed in a corrugated shape. . By adopting such a structure, the flow of the cooling medium is also turbulent, and at the same time, the gas flow is further complicated, heat exchange through the fins 405-2 is promoted, and excellent cooling efficiency is obtained. At the same time, since thermal deformation was possible, it was confirmed that the thermal stress was relaxed and the durability was excellent. In addition, the deformation | transformation to the waveform of the flat heat exchanger tube 404-3 is not limited to FIG. 49, You may deform | transform in the flow direction of a cooling medium, or may deform | transform in combination.

  FIG. 45 is a plan view partially showing the flat heat transfer tube 404-4 and the corrugated fin 405-3 fixed to the flat heat transfer tube 404-4. The corrugated fin 405-3 includes the flat heat transfer tube 404-. The outer surface of 4 is fixed so as to meander. With this structure, the gas flow is changed to a turbulent flow or a vortex flow, and the gas flow path is further extended. Therefore, the heat exchange through the fins 405-3 is promoted, and the cooling efficiency is improved. Further improvement has been confirmed. The flat heat transfer tubes 404-1 and the corrugated fins 405-1 shown in FIG. 42 can be used to replace the gas cooling device 401 shown in FIG. Is possible.

  The embodiment apparatus shown in FIG. 46 has an outer shell diffuser shape in the structure of the cooling jacket 402-1 disposed in the gas pipe 403-1 as shown in the respective drawings (a), (b), and (c). A partition plate 407 made of a tube sheet is provided at the boundary between the cooling jacket 402-1 and the gas flow path, and the flat heat transfer tubes 404-5 or between the flat heat transfer tubes 404-5 and the outer shell are provided. The corrugated fins 405-4 to be mounted and fixed are substantially the same as the embodiment apparatus shown in FIG. 41 except that the corrugated fins 405-4 have a corrugated shape, but the performance such as cooling efficiency is the same as that of the embodiment apparatus shown in FIG. It is almost the same.

  Also, in each of the embodiments shown in FIGS. 41 and 46, the corrugated fins shown in FIG. 15 can be used as an alternative to the corrugated fins, as shown in FIGS. 47 (a) to 47 (c). I-shaped fins 405a-1 (FIG. A), S-shaped fins 405a-2 (FIG. B), U-shaped fins 405a-37 (FIG. C), and the various fins shown in FIG. 48 (a) to 48 (e), that is, plate fins 405b-2 (FIG. A) provided with a large number of through holes, plate fins 405b-3 (FIG. B) provided with louvers, and deformed louvers. Plate fins 405b-4 (FIG. C) provided with pin fins, plate fins 405b-5 (FIG. D) provided with pin fins, plate fins 405b-6 (FIG. E) provided with irregularities, and the like can be used. These fins can be used alone or in combination with other fins including various corrugated fins used in the above embodiments.

An EGR gas cooling device 501 shown in FIG. 49 includes a cooling medium inlet P1 and an outlet P2 that are mainly used for engine cooling water above and below an EGR gas pipe 502 having a substantially rectangular cross section. Jackets 504-1 and 504-2 are arranged, and pass between the cooling jackets 504-1 and 504-2 through the EGR gas pipe (hereinafter, simply referred to as “gas pipe”) 502, and A plurality (12 in this example) of heat transfer tubes 503 intersecting at right angles to the flow direction (arrow g) are provided to form a cooling water flow path between the cooling jackets 504-1 and 504-2. doing.
Here, it is an essential requirement that the heat transfer tube 503 be formed so that its cross-sectional shape gradually expands toward the rear in the gas flow direction. That is, the heat transfer tube 503 in this example has a so-called wedge shape in which the cross-sectional shape gradually increases in width from the front end portion 503-2 toward the rear end portion 503-3 as shown in FIG. The entire outer peripheral surface of the heat transfer tube 3 including the inclined surface 503-1 is formed as a wide heat transfer surface, and the wedge-shaped heat transfer tube 503 intersects the gas flow direction at a right angle as shown in FIG. A plurality of pipe ends are arranged while maintaining an interval, and the pipe ends penetrate the inside of the gas pipe 502 and are fixed to the cooling jackets 504-1 and 504-2 with respective openings.

  In the EGR gas cooling apparatus 501 according to the present example configured as described above, the engine coolant C serving as a cooling medium flows in from the inlet P1 provided in the lower cooling jacket 504-1, and the cooling jacket 504- 1, then flows through each of the wedge-shaped heat transfer tubes 503, passes through the upper cooling jacket 504-2, and then flows out of the system through the outlet P2. On the other hand, the EGR gas that has flowed into the cooling device 501 from the upstream side of the gas pipe 502 has an outer peripheral surface of a heat transfer pipe 503 that is disposed in a plurality of positions in the pipe so as to intersect at right angles to the gas flow direction (arrow g). In addition, it flows down to the downstream side while repeating contact and flows out of the system. At this time, the heated EGR gas flowing into the cooling device 1 moves in the downstream direction while repeatedly colliding with the heat transfer surface centering on the inclined surface 503-1 of the heat transfer tube 503. Due to repeated collisions with the heat transfer surface, particularly the inclined surface 503-1, the gas boundary layer repeats peeling one after another, and effective heat exchange is performed, and the EGR gas is cooled as quickly as possible. The EGR gas that has flowed out of the system while repeatedly contacting the heat transfer tubes 503 arranged in a row is cooled to a temperature range that does not hinder the recirculation after returning to the intake system of the engine. The

  Further, in another EGR gas cooling device shown in FIGS. 52 to 53, the wedge-shaped heat transfer tube 503 is changed to the shape shown in FIG. 56, and the wedge-shaped heat transfer tube 503a is changed to FIG. As shown in the figure, the structure is a plurality of positions that intersect with the gas flow direction at right angles while maintaining the interval, and substantially the first embodiment except that the shape of the wedge-shaped heat transfer tube is partially changed. The same multi-tubular gas heat exchange device 501a as that of FIG. Also in the case of this EGR gas cooling device 501a, substantially the same cooling performance as that of the EGR gas cooling device shown in FIGS. 49 to 51 can be obtained.

  Further, also in the EGR gas cooling device shown in FIGS. 49 to 54, the gap between the wedge-shaped heat transfer tubes 503 or 503a or the wedge-shaped heat transfer tubes 503 or 503a and the gas pipes 502 or 502a as required. It is also possible to adopt a preferred embodiment in which a plate fin is fixed to the gap in parallel with the gas flow direction (arrow g). The shape of the plate fin is appropriately selected from the plate fin shown in FIG. 9, that is, a plate fin provided with a through hole, a louver provided, a pin fin attached, and an uneven provided. Can be used.

  In the EGR gas cooling apparatus shown in FIGS. 49 to 54, in addition to the wedge-shaped heat transfer tubes 503 and 503a, the above-described various plate fins are optionally fixed, thereby further promoting the gas flow stirring effect in the cooling apparatus. In addition, expansion of the heat transfer area by the plate fin itself is expected, and the cooling efficiency can be further improved, and the heat transfer tubes 503 or 503a, or between the heat transfer tubes 503 or 503a and the gas pipe 502 or 502a, Since a strong support is formed between them and an excellent reinforcing effect is obtained, other reinforcing means are not required, contributing to the compactness of the apparatus.

  In addition, in the EGR gas cooling apparatus shown in FIGS. 49 to 54, the shape of the heat transfer tube having a wedge-shaped cross-section that extends through the expanded gas pipe and intersects at right angles to the gas flow direction. Is not constrained by the shape of the heat transfer tubes 503 and 503a, and the width increases from the front end portions 503-2 and 503a-2 to the rear end portions 503-3 and 503a-3 that hit the rear in the gas flow direction. And a wide heat transfer surface including inclined surfaces 503-1 and 503a-1 from the upstream side to the downstream side in the gas flow direction, and by a sudden cross-sectional change on the downstream side of the heat transfer tubes 503 and 503a If the shape is expected to generate a “Kalman vortex street”, the inclination angles of the inclined surfaces 503-1 and 503a-1, the arrangement positions and pitches of the heat transfer tubes 503 and 503a, and the heat transfer tubes 503 and 5 are determined. Including the number of 3a group, in particular it can be freely modified in design tradeoff restrict not its effect as installation space.

57. The EGR gas cooling device 601 shown in FIG. 57 has a cooling medium (hereinafter simply referred to as “cooling medium”) in which engine cooling water is mainly used above and below an EGR gas pipe 602 having a substantially rectangular cross section as shown in FIGS. The cooling jackets 604-1 and 604-2 each having a C inlet P1 and an outlet P2 are disposed between the cooling jackets 604-1 and 604-2, and the EGR gas. A plurality of heat transfer tubes 603 made of a cylindrical tube that penetrates the pipe 602 and intersects at right angles to the gas flow direction (arrow g) are fixed and arranged, and a plurality of heat transfer tubes from the upstream to the downstream in the gas flow direction. A heat transfer tube row group is formed, and a cooling water flow path is formed between the cooling jackets 604-1 and 604-2.
Here, in the cooling water flow path of the heat transfer tube row group, a weir is provided in the cooling jacket 604-1 between the first row and the second row on the upstream side in the gas flow direction, and then the second row and the third row. A weir 606-1 is provided in the cooling jacket 604-2 between the rows, the cooling jacket 604-1 between the third row and the fourth row, and a cooling jacket 604 between the fourth row and the fifth row. The weir 606 is formed in the upper and lower cooling jackets 604-1 and 604-2 alternately so-called each heat transfer tube row group in which the weir 606-X is provided in each of the two, so that the cooling water flowing in from the inlet P1 flows. It is an essential requirement to forcibly control the flow path from the outlet P2 until it flows out of the system. In other words, when the cooling water in this example flows into the cooling jacket 604-1 from the inflow port P1, it is blocked by the weir 606-1 to form the first row of heat transfer tube rows from the cooling jacket 604-1. Each heat transfer tube 603 flows and flows into the other cooling jacket 604-2, but here again is blocked by the weir 606-X to form the second heat transfer tube row group from the cooling jacket 604-2. A path of passing through each heat transfer tube 603 and flowing into the cooling jacket 604-1 is repeated, and finally, it flows out of the system from the outlet P2 via the cooling jacket 604-2.

  In the EGR type gas cooling apparatus 601 configured as described above, the engine coolant C serving as a cooling medium flows in from the inlet P1 provided in the upper cooling jacket 604-1, and at the same time, the first row of heat transfer tubes. It repeats the route of reaching the cooling jacket 604-2 in the lower stage through the row group, and flowing into the cooling jacket 604-1 through the second row of heat transfer tube rows to maintain a high flow rate and a large amount of flow rate. While flowing out from the outlet P2 through all the heat transfer tube rows, the EGR gas flowing into the gas cooling device 601 from the upstream side in the gas flow direction (arrow g) of the EGR gas pipe 602 during this period The heat is effectively exchanged while repeating contact with each of the heat transfer tubes 603 in the heat transfer tube row group in order to cool as quickly as possible, and from the downstream side of the gas cooling device 601, EGR When returning to the scan pipe, the recirculation of the returned to the intake system of the engine, is cooled at all to a temperature range not interfering.

  As shown in FIG. 58, the EGR gas cooling device 601 passes through the EGR gas pipe 602 between the cooling jackets 604-1 and 604-2, and adheres to the gas at a right angle with respect to the flow (arrow g). -By arranging the heat transfer tubes 603 that are arranged to form a heat transfer tube array so that the interval between the heat transfer tubes 603 is narrowed with respect to the gas flow path, the flow rate and the amount of cooling water amplified by the weir interact with each other. Thus, more effective heat exchange is promoted, no bubbles are generated due to boiling, and excellent cooling efficiency is obtained.

In addition, the EGR gas cooling device 611 shown in FIGS. 60 to 61 has sparse heat transfer tubes 613-1 and 613-2 that form a heat transfer tube array group, and the heat transfer tubes 613-1 and 613-2 A gas cooling device 611 substantially similar to the EGR gas cooling device 601 was configured except that the spiral fins 613-1a and the disk-shaped fins 613-2a were previously attached. Reference numeral 612 denotes an EGR gas pipe.
Also in the case of this EGR gas cooling device 611, the cooling water whose flow path is restricted by the weirs 616-1 and 616-X is maintained in the heat transfer tubes 613-1 and 613-2 while maintaining a high flow rate and a large amount of water. In addition, the stirring of the gas flow by the spiral fins 613-1a and the disk-shaped fins and the expansion of the heat transfer area act synergistically, and a cooling performance substantially equivalent to that of the EGR gas cooling device 611 is obtained.

Further, in the EGR gas cooling device 621 shown in FIGS. 62 to 63, the number of the heat transfer tubes 623 forming the heat transfer tube array group is slightly sparse, and a plurality of heat transfer tubes 623 are arranged in parallel with the gas flow direction. The gas cooling device 621 was substantially the same as the EGR gas cooling device 601 except that the plate fins 625 were attached. Reference numeral 622 denotes an EGR gas pipe.
Also in the case of this EGR gas cooling device 621, the cooling water whose flow path is regulated by the weirs 626-1 and 626-X flows through the heat transfer pipe 623 while maintaining a high flow rate and a large amount of water, and in addition to the plate It was confirmed that the turbulent flow of the gas flow by the fins 625 and the expansion of the heat transfer area act synergistically to obtain a cooling performance substantially equivalent to that of Example 1.

Also, in the EGR gas cooling apparatus shown in FIGS. 64 to 66, 631 covers the entire circumference of the outer periphery of the EGR gas pipe 632 in which the heat transfer tube 633 forming the heat transfer tube row group is formed of a flat tube and the cooling jacket 634 is expanded. It is a so-called double pipe type, and is substantially the same as the EGR gas cooling device 601 except that the double pipe type cooling jacket 634 has a structure vertically divided by a separator 634-1. A gas cooling device 631 was configured.
Also in the case of this cooling device 631, the cooling water whose flow path is regulated by the weirs 636-1 and 636-X flows through the heat transfer pipe 623 while maintaining a high flow rate and a large amount of water, and in addition, the flat heat transfer pipe Further acceleration of the flow velocity by 633 and expansion of the heat transfer area act synergistically, and a cooling performance substantially equivalent to that of the EGR gas cooling device 601 is obtained.

67 to 68, the EGR gas cooling device 641 is arranged in the gap between the flat heat transfer tubes 643 forming the heat transfer tube row group or the gap between the flat heat transfer tubes 643 and the inner wall of the EGR gas pipe 642. A gas cooling device 641 that is substantially the same as the EGR gas cooling device 601 is configured except that corrugated fins as shown in FIG.
Also in the case of this EGR gas cooling device 641, the cooling water whose flow path is regulated by the weirs 646-1 and 646-X flows through the heat transfer pipe 643 while maintaining a high flow rate and a large amount of water, and in addition, is flat. Further acceleration of the flow velocity by the heat transfer tube 633 and turbulent gas flow and expansion of the heat transfer area by the joined corrugated fins act synergistically, and efficient cooling performance can be obtained by rapid heat exchange.

Furthermore, in the EGR gas cooling device 651 shown in FIGS. 69 to 71 and the EGR gas cooling device 661 shown in FIGS. 72 to 74, the shape of each of the heat transfer tubes 653 and 663 forming the heat transfer tube row group is the flow of gas. Direction (arrow g) is a so-called wedge shape that expands in width from the upstream tip to the downstream rear end, and uses the wedge-shaped heat transfer tubes 653 and 663 and arranges the cooling jacket vertically. Except for the so-called header type, the EGR gas cooling devices 651 and 661 were substantially configured.
Also in the EGR gas cooling devices 651 and 661, the cooling water whose flow path is restricted by the weirs 656-1, 656-X and 666-1, 666-X maintains a high flow rate and a large amount of water, and is wedge-shaped. The thin boundary layer is formed by flowing through the heat transfer tubes 653 and 663 having a shape and, in addition, the gas flow is separated from the heat transfer surfaces formed in the wedge-shaped heat transfer tubes 653 and 663 while sequentially colliding with each other. Is maintained and heat exchange is effectively promoted, and extremely excellent cooling performance is obtained.

  In the EGR gas cooling apparatus shown in FIGS. 57 to 74, the plate fins exemplified in FIG. 9 and the corrugated fins exemplified in FIG. The stirring effect of the gas flow is further promoted, and the expansion of the heat transfer area by the fin itself is expected, and the cooling efficiency can be further improved, and the heat transfer tubes, or between the heat transfer tubes and the gas piping, Since a strong support is formed between them and an excellent reinforcing effect is obtained, other reinforcing means are not required, contributing to the compactness of the apparatus.

  In addition, as the heat transfer tube in each EGR gas cooling device shown in FIGS. 57 to 74, a metal tube is preferably adopted in consideration of its excellent heat transfer property, ease of processing, mechanical strength, and the like. The weir that regulates the cooling water flow path in the heat transfer tube array group is not particularly limited as long as it can withstand the water pressure of the flowing cooling water and can arbitrarily regulate the flow path, and can be arbitrarily placed in the cooling jacket. It is more preferable that the structure is removable. In addition, although the weir in each said Example provided alternately in the boundary for every heat exchanger tube row group, and restricted the cooling water flow path to one flow, this invention is not restrained by this, The 1st row It is possible to manipulate the desired flow arbitrarily and arbitrarily by slowing the flow from the current flow to the rear flow, intentionally speeding the flow in the middle basin, or moving the position where the weir is provided. With this configuration, the EGR gas cooling device of the present invention can prevent the phenomenon in which effective heat exchange is hindered by bubbles caused by continuous boiling in the device, and can obtain excellent cooling efficiency.

  Furthermore, in the present invention, even if the EGR gas pipe, the trunk pipe, the cooling pipe, or the heat transfer pipe wall surface is formed as necessary on all the EGR gas cooling apparatuses described above, the turbulence and the heat transfer area can be increased. Good. FIG. 75 and FIG. 76 show an example, in which unevenness is formed on each wall surface of the EGR gas pipe 2 and the cooling pipe 3 of the EGR gas cooling apparatus shown in FIGS. Needless to say, the unevenness is provided as necessary.

  In addition, as described above, so-called welding means by welding or brazing is preferably used as the fixing means of these members in the present invention, but the adhesion ensures mutual excellent adhesion, and the heat transfer action is hindered. This is because reliable bonding is expected in a harsh operating environment, such as not being performed and repeated intense vibrations.

  As is clear from the above embodiments, the gas cooling device according to the present invention exhibits excellent cooling efficiency despite its simple structure. Therefore, in order to make the device lighter and smaller, it can be widely used as an EGR gas cooling device for automobiles, as well as widely used as a heat recovery device from exhaust gas and other gas cooling devices. Applications are expected.

It is a vertical side view which abbreviate | omits and shows the apparatus of 1st Example of this invention. FIG. 2 is a cross-sectional plan view on the easy line of FIG. 1. It is a vertical front view on the roll line of FIG. It is a vertical side view which abbreviate | omits and shows the apparatus of 2nd Example of this invention. It is a cross-sectional plan view on the ha ha line of FIG. It is a vertical side view which abbreviate | omits and shows the apparatus of 3rd Example of this invention. FIG. 7 is a cross-sectional plan view on the Nini line in FIG. 6. It is sectional drawing which shows an example of the joining structure of the cooling piping (heat-transfer tube) and plate fin in the 3rd Example apparatus shown in FIG. 6, FIG. 6 and 7 are sectional views showing various structural examples of plate fins in the apparatus of the third embodiment, wherein (a) is a plate fin provided with a through hole, and (b) and (c) are plate fins provided with a louver. , (D) shows plate fins provided with pin fins, and (e) shows plate fins provided with unevenness by press molding. It is a vertical side view which abbreviate | omits and shows the apparatus of 4th Example of this invention. It is a cross-sectional plan view on the Hoho line of FIG. It is a vertical front view on the hae line of FIG. It is a vertical side view which abbreviate | omits and shows the apparatus of 5th Example of this invention. It is a vertical front view on the tote line of FIG. It is the fragmentary perspective view which expands and shows an example of the corrugated sheet part in this invention apparatus, (a) shows the corrugated sheet part of an arc-shaped cross section, (b) shows the corrugated sheet part of a trapezoidal cross section, respectively. It is a vertical side view which shows the 6th Example apparatus of this invention. It is a perspective view which shows the plate fin in the 6th Example apparatus shown in FIG. FIG. 17 is a transverse plan view on the teach line in FIG. 16. FIG. 17 is a longitudinal front view on the reel line of FIG. 16. It is a vertical side view which shows the 7th Example apparatus of this invention. It is a perspective view which shows the plate fin in the 7th Example apparatus shown in FIG. FIG. 21 is a cross-sectional plan view on the Noon line of FIG. 20. It is a longitudinal front view on the rule line of FIG. It is a typical principal part perspective view which shows the 8th Example apparatus of this invention. It is a principal part perspective view which shows the flexible molding part in the 8th Example apparatus shown in FIG. It is a principal part perspective view which shows the other flexible molding part in the 8th Example apparatus shown in FIG. It is a vertical front view which shows the 9th Example apparatus of this invention. The apparatus of 10th Example of this invention is shown, (a) is a cross-sectional top view, (b) is a vertical front view. The 11th Example apparatus of this invention is shown, (a) is a cross-sectional top view, (b) is a vertical front view. The apparatus of 12th Example of this invention is shown, (a) is a cross-sectional top view, (b) is a vertical front view. The apparatus of 13th Example of this invention is shown, (a) is a cross-sectional top view, (b) is a vertical front view. It is a perspective view which shows the waveform fin with the wave | undulation in this invention apparatus. It is a vertical front view which shows the 14th Example apparatus of this invention. FIG. 34 is a partially enlarged sectional view partially showing the fourteenth embodiment apparatus shown in FIG. 33; It is a vertical front view which shows the 15th Example apparatus of this invention. FIG. 36 is a partially enlarged sectional view partially showing the fifteenth embodiment apparatus shown in FIG. 35; FIG. 36 is a perspective view showing a single partially raised belt-like fin used in the fifteenth embodiment apparatus shown in FIG. 35. Similarly, it is a perspective view showing a single unit of various fins that can be arbitrarily used in each example device, (a) is provided with a circular hole, (b) is provided with a semicircular cross section, ( c) shows a pleated portion having a concavo-convex cross section over the entire length, and (d) shows a fold formed on the lip. Similarly, the channel fins provided with different louvers that can be arbitrarily used in each embodiment apparatus are illustrated, (a) is a perspective view showing a channel fin having a louver with one end bent, (b). FIG. 5 is a perspective view showing a channel fin having a louver with both ends bent, and FIG. 5C is a perspective view showing a channel fin having a curved louver. It is a top view which shows partially the assembly | attachment state of the fin in each Example apparatus similarly. It is a typical front view which shows the 16th Example apparatus of this invention. FIG. 42 is a partially enlarged perspective view partially showing another embodiment of the heat transfer tube in the apparatus of the sixteenth embodiment shown in FIG. 41. It is a front view which shows partially another Example of the heat exchanger tube in a 16th Example apparatus similarly. It is a perspective view which shows the other Example of the heat exchanger tube in a 16th Example apparatus partially partially similarly. It is a top view which shows partially another Example of the heat exchanger tube in a 16th Example apparatus similarly. It is a schematic three-plane figure which shows the 17th Example apparatus of this invention, (a) is the top view, (b) is the vertical side view, (c) is a cross-sectional plan view on the AA line of (a). . Similarly, various fins that can be arbitrarily used in the sixteenth embodiment device and the seventeenth embodiment device are partially shown, (a) is an I-shaped fin, (b) is an S-shaped fin, (c) FIG. 3 is a perspective view showing a U-shaped fin. Similarly, it is sectional drawing which shows the structure of a plate fin, (a) what provided the through-hole in the plate fin, (b) and (c) what provided the louver, (d) what provided the pin fin, e) shows the thing which provided the unevenness | corrugation, respectively. It is a vertical side view which shows the 18th Example apparatus of this invention. FIG. 50 is a transverse plan view on the rule line of FIG. 49. FIG. 50 is a longitudinal front view on the line of FIG. 49. It is a vertical side view which shows the 19th Example apparatus of this invention. FIG. 53 is a cross-sectional plan view on the wire line of FIG. 52. FIG. 53 is a longitudinal front view on the car line in FIG. 52. It is a perspective view which similarly shows an example of the heat exchanger tube in 18th Example apparatus and 19th Example apparatus similarly. It is a perspective view which similarly shows the other example of a heat exchanger tube single-piece | unit. It is a vertical side view which abbreviate | omits and shows a 19th Example apparatus of this invention. It is a cross-sectional plan view on the yo-yo line of FIG. FIG. 58 is a longitudinal front view on the tar line of FIG. 57. It is a vertical side view which abbreviate | omits and shows a 20th Example apparatus of this invention. FIG. 61 is a transverse plan view on the rail line of FIG. 60. It is a vertical side view which abbreviate | omits and shows a 21st Example apparatus of this invention. FIG. 63 is a cross-sectional plan view on the source line of FIG. 62. It is a vertical side view which abbreviate | omits and shows a 22nd Example apparatus of this invention. FIG. 65 is a transverse plan view on the toe line of FIG. 64. FIG. 67 is a longitudinal front view on the lane line of FIG. 64. It is a vertical side view which abbreviate | omits and shows the apparatus of 23rd Example of this invention. FIG. 68 is a longitudinal sectional front view on the null line of FIG. 67. It is a vertical side view which abbreviate | omits and shows a part of apparatus of 24th Example of this invention. FIG. 70 is a cross-sectional plan view on the roller line of FIG. 69. FIG. 70 is a longitudinal front view on the moo line of FIG. 69. It is a vertical side view which abbreviate | omits and shows a part of apparatus of 25th Example of this invention. FIG. 73 is a transverse plan view on the Wu line of FIG. 72. FIG. 73 is a longitudinal front view on the non-line of FIG. 72. It is a fragmentary sectional view which shows an example of the cross-section of the wall surface of EGR gas piping in the Example apparatus shown in FIGS. It is a fragmentary sectional view which shows an example of the cross-section of the wall surface of the cooling pipe (heat exchanger tube) in the Example apparatus similarly shown in FIGS.

Explanation of symbols

1, 11, 21, 31, 41, 101, 201, 201-1, 201-2, 201-3, 201-4, 201-5, 301, 301-1, 501, 501a, 601, 611, 621, 631, 641, 651, 661 EGR gas cooling device 2, 12, 22, 32, 42, 102, 112, 203, 203-1, 302, 403, 403-1, 502, 502a, 602, 611, 621, 631 641, 651, 661 EGR gas piping 3, 23 Cooling piping 4-1, 4-2, 14-1, 14-2, 24-1, 24-2, 34, 44, 104-1, 104-2, 114, 202-1, 202-2, 202-3, 202-4, 202-5, 202-6, 202-7, 202-8, 202-9, 202-10, 202-11, 202-12, 304 1, 304-2, 402, 402-1, 504-1, 504-2, 504a-1, 504a-2, 654-1, 654-2, 664-1, 664-2 Cooling jackets 13-1, 13 -2 finned tube 25, 103-1, 113-1, 204-1, 204-2, 204-3, 204-3, 204-4, 204-5, 204-6, 505, 505-1, 505 -2, 505-3, 505-4, 505-5, 625 Plate fin 25-1 Burring wall 25-2, 625-2, Through hole 25-3, 25-4, 625-3, 625-4 Louver 25 -5 Pin fin 25-6 Concavities and convexities 33, 43, flat tubes 45a, 45b, 204a-1, 204a-2, 204a-3 Corrugated plates 103, 113 Cores 103-3, 113-3 Projecting cylinders 205, 205 -1, 205-2, 205-3 Flexible forming portion 206 Trunk tube 305-6, 305-7, 305-8, 305-9, 305-10 Channel fin P1 Inlet P2 Outlet

Claims (37)

A large number of cooling pipes that intersect the gas pipe at right angles to the gas flow direction of the pipes are fixedly arranged through the outer peripheral wall of the gas pipes so that both pipe ends open to the outside, Further, a cooling jacket having an inflow / outlet of the cooling medium is fixed to the outer surface of the gas pipe on both sides in the pipe axis direction of the cooling medium pipe group or the entire outer surface of the gas pipe. A gas cooling device characterized in that the gas is cooled. The gas cooling device according to claim 1, wherein the cooling pipe has spiral or disk-shaped fins on an outer periphery thereof. The gas pipe in the heat exchange region in which the cooling pipes are fixedly arranged has at least one plate fin parallel to the gas flow in the gas pipe and perpendicular to the cooling pipe. The gas cooling device described in 1. The gas cooling device according to claim 3, wherein a burring wall is provided in a through hole into which the cooling pipe of the plate fin is inserted. The gas cooling device according to claim 4, wherein the plate fin is provided with at least one of a louver, a through hole, a pin fin, and unevenness. A gas pipe is subjected to burring on a single plate, and a plurality of plate fins in which a large number of protruding cylindrical bodies are formed in the same phase are overlapped, and the protruding cylindrical body portions are joined together by welding or brazing. The core in which the tubular cooling medium flow path is formed, the tubular cooling medium flow path of the core intersects at right angles to the gas flow direction of the pipe, and the end of each tubular cooling medium flow path is As it opens to the outside, it is fixedly arranged through the outer peripheral wall of the gas pipe. A gas cooling apparatus comprising: a cooling jacket having a fixed structure, wherein the gas in the gas pipe is cooled by a cooling medium flowing through the tubular cooling medium flow path. In a gas cooling apparatus having either a cooling medium inlet or an outlet and having a plurality of heat transfer tubes arranged at regular intervals between opposing cooling jackets and intersecting at right angles to the gas flow direction, An adjacent wall surface excluding a portion covered by the cooling jacket has a plurality of flexible molding portions and / or a plurality of heat radiation fins parallel to or intersecting with the gas flow direction. Gas cooling device. The gas cooling device according to claim 7, wherein a plurality of plate fins are joined in parallel to the gas flow direction on the outer peripheral surface of a plurality of the heat transfer tubes arranged while maintaining the interval. 9. The gas cooling device according to claim 7, wherein the other end of the plate fin joined to the heat transfer tube is inserted into the flexible molding portion and clamped. The gas cooling according to any one of claims 7 to 9, wherein the plate fin is processed into a corrugated shape, a corrugated rectangular corrugated shape, a through hole, an unevenness, a louver, and the like. apparatus. The gas cooling device according to any one of claims 7 to 10, wherein the joining means of each part constituting the gas cooling device is welding and / or brazing. Gas cooling in which a plurality of flat heat transfer tubes having either an inlet or an outlet for a cooling medium and disposed between opposing cooling jackets and perpendicular to the gas flow direction are arranged at intervals. An apparatus for cooling a gas, wherein a plurality of channel-shaped fins are provided on a flat outer surface of the flat heat transfer tube in parallel with a gas flow direction. The gas cooling device according to claim 12, wherein the fin has a small divided shape over the entire length of the flat heat transfer tube or in the length direction. The gas cooling device according to claim 12 or 13, wherein the fin is a band-shaped fin with a cut and raised portion. The gas cooling device according to any one of claims 12 to 14, wherein the fin is provided with a louver, a through hole, an unevenness, a corrugation, and the like. 6. The gas cooling device according to claim 12, wherein the fins are joined after being brought into pressure contact with each other between the flat heat transfer tubes or between the flat heat transfer tubes and the outer wall of the cooling device. The gas cooling device according to any one of claims 12 to 16, wherein a joining means of each part constituting the gas cooling device including the fin is welding and / or brazing. A gas having either a cooling medium inlet or an outlet and a plurality of flat heat transfer tubes arranged between the opposing cooling jackets and intersecting at right angles to the gas flow direction at intervals. A cooling device, wherein a plurality of fins are provided on a flat outer surface of the flat heat transfer tube arranged at a predetermined distance so as to be substantially perpendicular and parallel to the gas flow direction, and these fins are alternately interposed. A gas cooling device characterized in that a core is formed by fixing. 19. The gas cooling device according to claim 18, wherein the aspect ratio of the core is 1: 1.5 to 1: 7 in a flat heat transfer tube length / EGR gas flow channel length ratio. The gas cooling device according to claim 18, wherein the aspect ratio of the core is 1: 2.5 to 1: 5 in the ratio of the flat heat transfer tube length / the length of the EGR gas flow path. The gas cooling device according to any one of claims 1 to 20, wherein the flat heat transfer tube alone is constituted by a single member or a plurality of flat tubes. The gas cooling device according to claim 21, wherein the single unitary flat heat transfer tube has one to a plurality of reinforcing ribs therein. The gas cooling device according to any one of claims 18 to 22, wherein the fin fixed to the flat outer surface of the flat heat transfer tube is fixed so as to meander in the gas flow direction. . The flat heat transfer tube itself is formed in a corrugated shape in the gas flow direction, and fins fixed to the outer surface thereof are also formed in a corrugated shape. The gas cooling device according to claim 1. The gas cooling device according to any one of claims 18 to 24, wherein the fin is a corrugated fin. The gas cooling device according to any one of claims 18 to 25, wherein the fin is provided with a louver, a through hole, a pin fin, an unevenness and the like. 27. The gas cooling apparatus according to any one of claims 18 to 26, wherein a joining means of each part constituting the EGR gas cooling apparatus is welding and / or brazing. In a gas cooling apparatus in which a plurality of heat transfer tubes that have either an inlet or an outlet for a cooling medium and that intersect between the opposing cooling jackets and intersect at right angles to the gas flow direction are arranged at intervals. The cross-sectional shape of the heat transfer tube is a wedge shape whose width is gradually expanded toward the rear in the gas flow direction, and the gas is cooled by a cooling medium flowing through the heat transfer tube having the wedge shape. Gas cooling device. 29. The gas cooling apparatus according to claim 28, wherein plate fins are fixed to the wedge-shaped heat transfer tubes or in the gap between the heat transfer tube and the gas pipe in parallel with the gas flow direction. 30. The gas cooling device according to claim 28 or 29, wherein the plate fin is provided with a through hole, a louver, a pin fin, an unevenness and the like. The gas cooling device according to any one of claims 28 to 30, wherein a joining means of each part constituting the gas cooling device including the plate fin is welding and / or brazing. In the gas cooling apparatus in which a plurality of heat transfer tubes intersecting at right angles to the flow direction of the gas flowing in the gas piping are arranged at intervals, the heat transfer tubes are opened in the state where both tube ends are opened. Fixed to the outer peripheral wall of the heat transfer tube array, and the cooling medium inflow or Cooling medium to which a cooling jacket having one of the outlets is fixed, and the cooling medium flowing in from the inlet of the cooling jacket flows out from the other cooling jacket outlet through the heat transfer tube group. In the flow path, weirs are provided alternately in the flow direction of the cooling medium at the boundary between adjacent heat transfer tube row groups, and the flow path and flow rate of the cooling medium flowing through the heat transfer pipe are arbitrarily controlled, Coolant flowing through heat transfer tube group Gas cooling apparatus characterized by cooling the gas by. The gas according to claim 32, wherein the plurality of heat transfer tubes forming the heat transfer tube row group are a cylindrical tube tube, an oblong flat tube, a metal tube processed into a wedge-shaped cross section, and the like. Cooling system. A plate fin is fixed in parallel to the gas flow direction between the heat transfer tubes forming the heat transfer tube array group or between the heat transfer tubes and the inner peripheral surface of the gas pipe outer wall. The gas cooling device according to claim 32 or 33. The gas cooling device according to any one of claims 32 to 34, wherein the plate fin is provided with a through hole, a louver, a pin fin, unevenness and the like. 36. The gas cooling apparatus according to any one of claims 32 to 35, wherein a joining means of each part constituting the gas cooling apparatus including the plate fin is welding and / or brazing. The gas cooling according to any one of claims 1, 6, 7, 12, 18, 28, and 32, wherein a recess and / or a protrusion is formed on a wall surface of the gas pipe, the cooling pipe, or the heat transfer pipe. apparatus.

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