JP6140541B2 - Multi-tube heat exchanger - Google Patents

Description

  The present invention includes a heat transfer tube group, an inner tube portion having a rectifying tube portion disposed at one or both ends of the heat transfer tube group, and an outer tube portion having a body portion covering the outside of the heat transfer tube group. The present invention relates to a multi-tube heat exchanger in which a first fluid can be introduced into and led out from the inner cylinder part, and a second fluid can be introduced into and led out from the outer cylinder part. In particular, a heat exchanger that exchanges heat by passing a high-speed high-temperature gas (gas) through the inner cylinder and cooling water (liquid) through the outer cylinder, for example, exhaust that cools the exhaust gas of an internal combustion engine with cooling water The invention is suitable for a cooler (which requires a high degree of heat exchange capability), a heat exchanger for cooling an exhaust gas recirculation device (EGR), and the like.

  As the multitubular heat exchanger, there are those described in Patent Documents 1 and 2 previously filed by the present applicant, and a plurality of heat transfer tube groups 101 through which the first fluid (hot gas) passes, An outer tube 102 through which fluid (cooling water) passes, and a heat transfer tube group 101 having both ends thereof positioned on the first fluid introduction side and the first fluid discharge side, respectively, an introduction side / discharge side holding plate (not shown) It is held and arranged. A heat transfer tube group is disposed inside the outer tube 102 via introduction / discharge side holding plates at both ends of the outer tube. At both ends of the outer tube 102, a connection pipe 104 with a flange 105 is provided via a frustoconical inlet / outlet rectifying cylinder portion 103, and the first fluid (hot gas) passes through the heat transfer tube group 101. It is possible. Further, an introduction / discharge nozzle 106 is disposed above and below the outer tube 102 so that the second fluid (cooling water) can pass outside the heat transfer tubes. The connection pipe 104 that introduces / leads out the high temperature gas (gas) and the introduction / discharge nozzle 106 that introduces / leads out the cooling water (liquid) to / from the outer pipe are connected along the direction in which the protruding directions are orthogonal to each other. Are arranged.

  In the multi-tube heat exchangers of Patent Documents 1 and 2, the introduction / discharge nozzle 106 through which the second fluid (cooling water) passes and the connection pipe 104 through which the first fluid (hot gas) passes are shared. In the case of joining using the flange 105, the introduction / discharge nozzle 106 is bent and joined to the flange 105 as shown in FIG.

  As a joint structure for joining a heat exchanger (double pipe structure) constituting a part of an EGR passage in an internal combustion engine to a flange, there is one described in Patent Document 3, and a double structure comprising an inner pipe and an outer pipe. An inner pipe extending from the end of the pipe and a branch pipe for introducing a coolant into a passage between the inner pipe and the outer pipe are integrally joined to one flange.

  Moreover, although it does not affect the patentability of this invention, there existed what was described in patent document 4 as a heat exchanger for cooling of the conventional exhaust-gas recirculation apparatus (EGR).

JP 2004-69255 A JP 2002-350081 A JP 2003-220465 A JP 2004-116913 A

  However, when bending a pipe (introduction / discharge nozzle 106) at a right angle, the minimum bending radius must be greater than the diameter of the pipe to be bent in order to avoid the occurrence of blockage of the pipe and reduction in cross-sectional area. There is. For this reason, under the restriction due to the bending of the pipe, it has to be projected from the cooling heat exchanger at least as much as the diameter of the pipe, which causes an increase in the space occupied by the cooling heat exchanger.

  Also in the joint structure of Patent Document 3, the outer tube is dead end just before the end portion to be joined with the flange of the inner tube, and the outer tube and the flange are joined using a bent branch pipe (pipe). Joined to increase the occupied space.

  Moreover, in the cooling heat exchanger of Patent Document 4, there is no disclosure about reducing the occupied space.

  The present invention is a structure that does not use a bent pipe when forming a passage for cooling water (second fluid), enables a design that is not restricted by bending of the pipe, and can reduce the occupied space. A heat exchanger is provided.

In invention of Claim 1, the inner cylinder part which has a heat exchanger tube group, the rectification | straightening cylinder part distribute | arranged to the one end or both ends of a heat exchanger tube group, the outer cylinder part which has a trunk | drum part which covers the outer side of a heat exchanger tube group, the provided, an inner cylindrical portion multitubular heat exchanger the first fluid and the second fluid to the outer cylindrical portion are respectively capable introduced and derived, the first and second fluid in at least one of the side position In the configuration in which introduction or derivation is performed via a common flange, the outer cylinder portion includes a second fluid passage forming wall portion that extends from the body portion to the flange portion and forms a second fluid passage between the outer cylinder portion and the rectifying cylinder portion. The tip of the second fluid passage forming wall is a flange coupling neck.

  According to this, the outer cylinder portion is configured to include the second fluid passage forming wall portion that extends from the trunk portion to the flange portion and forms the second fluid passage between the outer cylinder portion and the second fluid passage. By forming the tip of the forming wall portion as a flange coupling neck that is integrally coupled with the flange, a bent pipe is not used. For this reason, it becomes possible to design a multi-tube heat exchanger that is not restricted by pipe bending, and the occupied space can be reduced.

  In addition, the cross-sectional area of the second fluid passage viewed from the longitudinal direction of the multi-tube heat exchanger at the connection portion between the heat transfer tube group and the rectifying cylinder is the inside of the flange coupling neck as viewed from the longitudinal direction of the multi-tube heat exchanger. The second fluid passage forming wall portion is formed so as to be in the same range or up to five times the cross-sectional area.

  According to this, the protrusion to the outer side of the outer cylinder part which covers the outer side of the connection part of the heat transfer tube group and the rectifying cylinder part and forms the outer wall of the second fluid passage is restricted, and the length of the multi-tube heat exchanger The projected area of the outer cylinder part seen from the direction can be suppressed, which contributes to reducing the occupied space of the multitubular heat exchanger. Furthermore, it is possible to prevent a decrease in heat exchange efficiency by suppressing a deviation in the flow rate of the second fluid flowing through the second fluid passage.

  Further, the flange coupling neck is formed by plastic working by edge forming. If the flange joint neck is formed by using a pipe as in the prior art, both ends must be brazed, and the second fluid must be joined in a sealable manner by some method such as welding. In the present invention, at least the end of the flange coupling neck on the base portion side that is edged by edge forming does not have to be integrated and joined, so in addition to the above effects, the number of manufacturing steps and the number of parts can be reduced. Reductions can be made. Here, “border molding” refers to a material that is plastically processed by stretching a material, and includes stretch flange molding, burring, and the like.

  Also, the first neck portion is disposed on the rectifying tube portion at both ends, the tubular outer fitting tube portion protruding in the same direction as the first neck portion from each second fluid passage forming wall portion is disposed, and the flange is penetrated. The outer tube portion is fitted into the hole, and the first neck portion is fitted inside the outer tube portion, thereby integrally coupling the inner tube portion with the flange.

  According to this, an inner cylinder part is fixed with respect to an outer cylinder part by inserting a 1st neck part inside an outer fitting cylinder part, and it inserts in the through-hole of each flange via an outer fitting cylinder part. Thus, it is possible to reduce the number of manufacturing steps for the multi-tube heat exchanger.

  In addition, the second fluid is prevented from leaking because there are many close contact portions and there are few gaps between the first neck and the outer fitting cylinder, and between the outer fitting cylinder and the flange. Can be made easier.

  Further, in the invention of claim 4, if the connecting portion between the heat transfer tube group and the rectifying tube portion and at least a part of the body portion are overlapped and joined, the joining portion between the inner tube portion and the outer tube portion is obtained. Since it increases and the thickness of the said junction part increases, the rigidity of a multitubular heat exchanger can be improved.

It is a perspective view of the multitubular heat exchanger of one embodiment in the present invention. It is a top view of the multitubular heat exchanger of one embodiment in the present invention. It is a side view of the multitubular heat exchanger of one embodiment in the present invention. It is IV-IV sectional drawing in FIG. FIG. 5 is a cross-sectional view taken along VV in FIG. 3. It is a perspective view of the multi-tubular heat exchanger of other embodiment in this invention. It is a top view of the multitubular heat exchanger of other embodiments in the present invention. It is a side view of the multitubular heat exchanger of other embodiment in this invention. It is IX-IX sectional drawing in FIG. It is XX sectional drawing in FIG. It is a rough sectional view of the conventional multi-tube heat exchanger.

  An embodiment of a multi-tube heat exchanger according to the present invention will be described with reference to the drawings. The multitubular heat exchanger of the present invention is not limited to this configuration. That is, various design changes can be made without departing from the gist of the present invention. In the following description, F of the arrow in FIG. 1 is front, B is back, R is right, L is left, U is up, and D is down.

  As shown in FIGS. 1 to 5, the multitubular heat exchanger (hereinafter referred to as “heat exchanger”) 10 includes an inner cylinder portion 20, an outer cylinder portion 30, a front flange 41, a rear flange 42, and the like. ,have.

  The inner cylinder part 20 includes a heat transfer tube group 21, a front rectification cylinder part 23, and a rear rectification cylinder part 24.

  The heat transfer tube group 21 includes a plurality of heat transfer tubes 22, and the first fluid can pass through the heat transfer tubes 22 along the front-rear direction. In the illustrated example, the heat transfer tube 22 is formed as a flat tube having a long cross section in the left-right direction, and is stacked and disposed with a gap along the vertical direction. The heat transfer tube group 21 in which the heat transfer tubes 22 are stacked has a rectangular parallelepiped shape as a whole.

  The front rectification cylinder part 23 and the rear rectification cylinder part 24 are respectively disposed at both ends of the heat transfer tube group 21, and the front rectification cylinder part 23 is formed in a quadrangular frustum shape so that the front side is narrow, and in the forward direction It has a cylindrical first neck portion 23a that protrudes, and the rear flow straightening cylinder portion 24 has a quadrangular pyramid shape and is formed so that the rear side is narrow, and has a cylindrical first neck portion 24a that protrudes in the right direction. ing.

  The front rectifying tube portion 23 and the rear rectifying tube portion 24 are fitted into both ends of the heat transfer tube group 21 from the outside, respectively, and the heat transfer tube group 21, the front rectifying tube portion 23, and the rear rectifying tube portion 24 are connected to each other, and the inner tube portion 20 is formed, and the inner side of the inner cylinder part 20 is a first fluid passage 25 through which the first fluid passes.

  The outer cylinder part 30 is integrally formed in a rectangular box shape by joining an upper half part 30a and a lower half part 30b which are divided into two parts in the vertical direction. A front second fluid passage forming wall portion (hereinafter referred to as “front forming wall portion”) 31, a rear second fluid passage forming wall portion (hereinafter referred to as “rear forming wall portion”) 32, and a front forming wall. A body portion 33 that connects the portion 31 and the rear forming wall portion 32.

  The front forming wall portion 31 is disposed so as to cover the outer side of the front flow straightening cylinder portion 23, and is formed in a cylindrical flange coupling neck portion 31a projecting in the front direction and having a larger diameter than the flange coupling neck portion 31a. A cylindrical outer fitting cylindrical portion 31b protruding in the same direction as the coupling neck portion 31a.

  The external fitting cylinder part 31b is formed so that the 1st neck part 23a can be inserted.

  The front forming wall portion 31 has a cross-sectional area of the second fluid passage 34 as viewed from the front and rear (longitudinal) direction of the heat exchanger 10 at the connection portion between the heat transfer tube group 21 and the front rectifying cylinder portion 23. It is formed so as to be the same as the inner cross-sectional area of the flange coupling neck portion 31a viewed from the front and rear (longitudinal).

  The rear forming wall portion 32 is disposed so as to cover the outer side of the rear rectifying cylinder portion 24, and is formed in a cylindrical flange coupling neck portion 32a protruding rightward and having a diameter larger than that of the flange coupling neck portion 32a. A cylindrical outer fitting cylindrical portion 32b protruding in the same direction as the coupling neck portion 32a.

  The external fitting cylinder part 32b is formed so that the 1st neck part 24a can be inserted.

  The cross-sectional area of the second fluid passage 34 viewed from the front-rear (longitudinal) direction of the heat exchanger 10 at the connecting portion between the heat transfer tube group 21 and the rear flow straightening cylinder portion 24 is a flange connection viewed from the front-rear (longitudinal) of the heat exchanger 10. The rear forming wall portion 32 is formed so as to be the same as the inner cross-sectional area of the neck portion 32a.

  The flange coupling neck part 31a, the outer fitting cylinder part 31b, the flange coupling neck part 32a, and the outer fitting cylinder part 32b are positioned at the boundary between the upper half 30a and the lower half 30b that are divided into two in the vertical direction. It is formed into a semi-cylindrical shape by molding, and is formed into a cylindrical shape by joining the upper half body 30a and the lower half body 30b.

  The body portion 33 is formed in a rectangular tube shape having a reduced diameter with respect to the front forming wall portion 31 and the rear forming wall portion 32, and is disposed so as to cover the outside of the heat transfer tube group 21.

  A space portion formed between the outer cylinder portion 30 and the inner cylinder portion 20 serves as a second fluid passage 34 through which the second fluid passes.

  As shown in FIG. 4, the body portion 33 joins the connecting portions of the heat transfer tube group 21, the front rectifying cylinder portion 23, and the rear rectifying cylinder portion 24 in the vertical direction from the outside. As shown in FIG. 5, the connecting portion between the heat transfer tube group 21 in the left-right direction, the front rectifying cylinder portion 23, and the rear rectifying cylinder portion 24 is not joined to the body portion 33 and is opened so that the second fluid can pass therethrough. .

  The second fluid passage 34 communicates with an end portion in the left-right direction of a boundary portion between the front forming wall portion 31, the rear forming wall portion 32, and the body portion 33 when viewed in the vertical direction.

  The front flange 41 and the rear flange 42 are flat plate-shaped first through holes 41a and 42a into which the flange coupling neck portions 31a and 32a are fitted, and second through holes 41b and 42b into which the outer fitting cylinder portions 31b and 32b are fitted. Each has.

  The outer fitting cylinder part 31b is fitted into the second through hole 41b of the front flange 41, the first neck part 23a is fitted inside the outer fitting cylinder part 31b, and the second through hole of the rear flange 42. When the outer fitting cylinder part 32b is fitted into 42b and the first neck part 24a is fitted inside the outer fitting cylinder part 32b, the inner cylinder part 20 is connected to the outer cylinder part 30, the front flange 41, and the rear flange 42. Are connected together.

  By inserting the flange coupling neck portion 31a into the first through hole 41a of the front flange 41 and by inserting the flange coupling neck portion 32a into the first through hole 42a of the rear flange 42, the outer cylinder portion 30 is moved forward. The flange 41 and the rear flange 42 are integrally coupled.

  An example of a method for manufacturing the heat exchanger 10 will be described.

  As shown in FIGS. 4 and 5, a plurality of heat transfer tubes 22 are stacked along the vertical direction to form a heat transfer tube group 21 having a rectangular parallelepiped shape. The front rectification cylinder part 23 and the rear rectification cylinder part 24 are fitted into the front and rear ends of the heat transfer tube group 21 from the outside to form the inner cylinder part 20.

  Next, the upper half 30a and the lower half 30b are joined to the inner cylinder portion 20 and covered from the outside by hand. At this time, the outer fitting cylinder part 31b is arranged at the position of the first neck part 23a, the outer fitting cylinder part 32b is arranged at the position of the first neck part 24a, and the first neck part 23a is arranged at the outer fitting cylinder part 31b. The inserted first neck portion 24a is in a state of being fitted into the outer fitting cylindrical portion 32b.

  After fitting the flange coupling necks 31a and 32a into the first through holes 41a and 42a of the front flange 41 and the rear flange 42, respectively, and fitting the outer fitting cylinders 31b and 32b into the second through holes 41b and 42b, respectively. Each is joined, and the assembly of the heat exchanger 10 is completed. In addition, joining between each part is performed by selecting welding, brazing, etc. suitably.

  In the heat exchanger 10 having the above-described configuration, the heat transfer tube group 21, the inner tube portion 20 having the front flow straightening tube portion 23 and the rear flow straightening tube portion 24 arranged at one or both ends of the heat transfer tube group 21, and the heat transfer tube group And the outer cylinder part 30 which has the trunk | drum part 33 which covers the outer side of 21, The 1st fluid can be introduce | transduced into the inner cylinder part 20, and the 2nd fluid can be introduce | transduced into the outer cylinder part 30, respectively, and the multitubular heat exchanger In the configuration in which the first and second fluids are introduced or led out through the common front flange 41 and rear flange 42, the outer cylinder portion 30 extends from the body portion 33 to the front flange 41 and the rear flange 42. , A front forming wall portion 31 that forms a second fluid passage 34 between the front rectifying cylinder portion 23 and the rear rectifying cylinder portion 24, and a rear forming wall portion 32. The front ends are flange coupling necks 31a and 32a.

  According to this, the outer cylinder part 30 is extended from the body part 33 to the front flange 41 and the rear flange 42, and the second fluid passage 34 is formed between the front rectification cylinder part 23 and the rear rectification cylinder part 24. It is set as the structure provided with the front formation wall part 31 and the rear formation wall part 32, The flange joint neck parts 31a and 32a which are integrally connected with the front flange 41 and the rear flange 42 by making the front-end | tip part of the front formation wall part 31 and the rear formation wall part 32 into. By doing so, the structure does not use a bent pipe. For this reason, it becomes possible to design the heat exchanger 10 that is not restricted by the bending process of the pipe, and the occupied space can be reduced.

  Further, the cross-sectional area of the second fluid passage 34 seen from the front and rear (longitudinal) direction of the heat exchanger 10 at the connection portion between the heat transfer tube group 21 and the front rectifying cylinder portion 23 and the rear rectifying cylinder portion 24 is The front forming wall portion 31 and the rear forming wall portion 32 are formed so as to be the same as the inner cross-sectional area of the flange coupling neck portions 31a and 32a when viewed from the front and rear (longitudinal) direction.

  According to this, the outside projection of the outer cylinder part 30 that covers the outer side of the connecting portion between the heat transfer tube group 21, the front rectification cylinder part 23, and the rear rectification cylinder part 24 and forms the outer wall of the second fluid passage 34 is prevented. The projected area of the outer cylinder part 30 seen from the front and rear (longitudinal) direction of the heat exchanger 10 can be suppressed and contributes to reducing the occupied space of the heat exchanger 10. Furthermore, it is possible to prevent the heat exchange efficiency from being lowered by suppressing the deviation of the flow rate of the second fluid flowing through the second fluid passage 34.

  Further, the flange coupling neck portions 31a and 32a are formed by plastic working by edge forming. If the flange coupling necks 31a and 32a were formed using pipes as in the conventional case, the second fluid had to be joined in a sealable manner by some method such as brazing and welding. In the present invention, at least the ends of the flange-coupled neck portions 31a and 32a on the side of the original portion that are edged by stretch flange molding do not have to be integrated and joined. In addition to the above effects, the number of manufacturing steps can be reduced. In addition, the number of parts can be reduced.

  Further, the first neck portions 23a and 24a are disposed on the front rectifying cylinder portion 23 and the rear rectifying cylinder portion 24 at both ends, and the same direction as the first neck portions 23a and 24a from the respective front forming wall portions 31 and the rear forming wall portions 32. The cylindrical outer fitting cylindrical portions 31b and 32b projecting from the outer flanged cylindrical portion 31b and 32b are disposed in the second through holes 41b and 42b of the front flange 41 and the rear flange 42. By inserting the first neck portions 23a and 24a inside the inner portions 31b and 32b, the inner cylinder portion 20 is integrally coupled to the front flange 41 and the rear flange 42.

  According to this, the inner cylinder part 20 is fixed to the outer cylinder part 30 by inserting the first neck parts 23a and 24a inside the outer fitting cylinder parts 31b and 32b, and the outer fitting cylinder parts 31b and 32b are fixed. Since the front flange 41 and the rear flange 42 are integrated with each other by being fitted into the second through holes 41b and 42b of the front flange 41 and the rear flange 42, the number of manufacturing steps of the heat exchanger 10 can be reduced. .

  Further, there are many close contact portions and a small gap between the first neck portions 23a and 24a and the external fitting cylinder portions 31b and 32b, and between the external fitting cylinder portions 31b and 32b and the front flange 41 and the rear flange 42. Since it is sufficient to braze to the second fluid, the work of preventing leakage of the second fluid can be facilitated.

  Moreover, since the connection part of the heat exchanger tube group 21, the front rectification cylinder part 23, and the rear rectification cylinder part 24 and at least a part of the body part 33 are overlapped and joined, the inner cylinder part 20 and the outer cylinder are joined. Since a joint part with the part 30 increases and the thickness of the joint part increases, the rigidity of the heat exchanger 10 can be increased.

  Further, the front flange 41 and the rear flange 42 are arranged orthogonal to the first neck portions 23a and 24a and the flange coupling neck portions 31a and 32a.

  According to this, in addition to the above effects, the obliquely projecting portion of the heat exchanger 10 is reduced, the dead space is reduced, the degree of freedom in layout when the heat exchanger 10 is attached is increased, and storage is also performed. Storability of the heat exchanger 10 during transportation can be improved.

  Another embodiment of the present invention will be described with reference to FIGS. About the structure which is common in the heat exchanger 10, the same code | symbol is attached | subjected and all or one part of those description is abbreviate | omitted.

  The heat exchanger 10A is different in the arrangement of the first neck portion 23a, the flange coupling neck portion 31a, and the external fitting cylinder portion 31b, but the functional action of the portions is the same as that of the heat exchanger 10.

  The outer cylinder part 50 is a fuselage connecting the front forming wall part 51, the rear forming wall part 52, the front forming wall part 51, and the rear forming wall part 52 that cover the outer sides of the respective front rectifying cylinder parts 23 and the rear rectifying cylinder part 24. And a separate part.

  The front-forming wall portion 51 and the rear-forming wall portion 52 are respectively disposed at both ends of the heat transfer tube group 21, the front-forming wall portion 51 is formed in a square bowl shape, and the rear-forming wall portion 52 is a square frustum shape. The rear side is narrowed.

  The cross-sectional area of the second fluid passage 34 seen from the front / rear (longitudinal) direction of the heat exchanger 10 at the connection portion between the heat transfer tube group 21 and the front rectifying cylinder portion 23 and the rear rectifying cylinder portion 24 is The front forming wall portion 51 and the rear forming wall portion 52 are formed so as to be the same as the inner cross-sectional area of the flange coupling neck portions 31a and 32a as viewed from the longitudinal direction.

  The body portion 53 is formed in a rectangular tube shape by joining a left half body 53a and a right half body 53b which are divided into right and left parts.

  The body portion 33 is formed in a rectangular tube shape having a reduced diameter with respect to the front forming wall portion 31 and the rear forming wall portion 32, and is disposed so as to cover the outside of the heat transfer tube group 21.

  As shown in FIG. 9, the body portion 53 is joined by joining the front forming wall portion 51 and the rear forming wall portion 52 from the outside. As shown in FIGS. 9 and 10, the second fluid is opened so as not to be joined to the body portion 53. Unlike the heat exchanger 10, the inner cylinder part 20 is not supported in parts other than the external fitting cylinder parts 31b and 32b.

  A space portion formed between the outer cylinder portion 50 and the inner cylinder portion 20 is a second fluid passage 34 through which the second fluid passes.

  The flange coupling neck part 31a, the outer fitting cylinder part 31b, the flange coupling neck part 32a, and the outer fitting cylinder part 32b are plastically processed into a cylindrical shape by burring.

  In the heat exchanger 10A, the inner cylinder part 20 is fixed to the outer cylinder part 50 by inserting the first neck parts 23a and 24a inside the outer fitting cylinder parts 31b and 32b, and the outer fitting cylinder parts 31b and 32b. Since the front flange 41 and the rear flange 42 are integrated with each other by being fitted into the second through holes 41b and 42b of the front flange 41 and the rear flange 42 via the, the manufacturing man-hour of the heat exchanger 10A can be reduced. it can.

  In addition, at least the ends of the flange-coupled necks 31a and 32a on the side of the original part that are edged by burring need not be integrated and joined, and are formed in a cylindrical shape. The number of manufacturing steps can be reduced and the number of parts can be reduced.

  The heat exchangers 10 and 10A have a configuration in which the first fluid flows in from one of the front rectifying tube portion 23 and the rear rectifying tube portion 24, and the first fluid flows out from the other. (The first fluid flows in from one of the front rectifying tube portion 23 and the rear rectifying tube portion 24 and the first fluid flows in the U-turn on the other side and flows out from the inflow side). Can do.

  Further, heat exchange is performed at the connecting portion between the heat transfer tube group 21, the front rectifying cylinder portion 23, and the rear rectifying cylinder portion 24, with the front forming wall portion 31, the rear forming wall portion 32, the front forming wall portion 51 and the rear forming wall portion 52. The cross-sectional area of the second fluid passage 34 viewed from the front-rear (longitudinal) direction of the vessel 10 is the same or five times the cross-sectional area of the flange coupling necks 31a, 32a viewed from the front-rear (longitudinal) of the heat exchanger 10, 10A. It is also possible to change and form as appropriate.

10, 10A Multi-tube heat exchanger 20 Inner tube portion 21 Heat transfer tube group 22 Heat transfer tube 23 Front rectifier tube portion 23a First neck portion 24 Rear rectifier tube portion 24a First neck portion 25 First fluid passage 30 Outer tube portion 31 Second Fluid passage forming wall (front forming wall)
31a Flange joint neck part 31b Outer fitting cylinder part 32 Second fluid passage forming wall part (rear forming wall part)
32a Flange joint neck part 32b Outer fitting cylinder part 33 Body part 34 Second fluid passage 41 Front flange 41a First through hole 41b Second through hole 42 Rear flange 42a First through hole 42b Second through hole 50 Outer cylinder part 51 Second Fluid passage forming wall (front forming wall)
52 Second fluid passage forming wall (rear forming wall)
53 Torso

Claims (5)

The inner cylinder comprising: a heat transfer tube group; an inner cylinder portion having a rectifying cylinder portion disposed at one or both ends of the heat transfer tube group; and an outer cylinder portion having a body portion covering the outside of the heat transfer tube group. A multi-tubular heat exchanger in which a first fluid is introduced into a part and a second fluid is introduced into and led out from the outer cylinder part,
In the configuration via a common flange introduction or derivation of the first and second fluid in at least one of the side position,
The outer cylinder part includes a second fluid passage forming wall part that extends from the body part to a flange part and forms a second fluid passage between the outer cylinder part and the rectifying cylinder part, and the second fluid passage formation wall part The tip of the flange is the flange joint neck,
A multi-tube heat exchanger characterized by that.   A cross-sectional area of the second fluid passage viewed from the longitudinal direction of the multi-tubular heat exchanger at a connection portion between the heat transfer tube group and the rectifying cylinder portion is the flange viewed from the longitudinal direction of the multi-tubular heat exchanger. The multi-tube heat exchanger according to claim 1, wherein the second fluid passage forming wall portion is formed so as to be in the range of the same or five times the inner cross-sectional area of the coupling neck portion.   The multi-tube heat exchanger according to claim 1 or 2, wherein the flange coupling neck is formed by plastic working by edge forming. A first neck is disposed on the rectifying cylinder at both ends,
A cylindrical externally fitting tube portion protruding in the same direction as the first neck portion from each of the second fluid passage forming wall portions is disposed,
The outer tube portion is inserted into the through hole of the flange, and the first neck portion is inserted inside the outer tube portion so that the inner tube portion is integrally coupled with the flange. The multitubular heat exchanger according to any one of claims 1 to 3.   The multi-tube heat exchanger according to claim 4, wherein a connecting portion between the heat transfer tube group and the rectifying tube portion and at least a part of the body portion are overlapped and joined.

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