DE112015005686T5 - heat exchangers - Google Patents

Abstract

It is envisaged that the heat exchanger will have improved heat exchange efficiency from a high temperature fluid to a low temperature fluid. The heat exchanger (30) comprises a plurality of plates (32) and a lamella (50). The blade comprises at least a first portion (52) and at least a second portion (54). The at least one first portion is a wall surface that includes the at least one first opening (56). The at least one second portion paired with the first portion is a wall surface different from the first portion. The second portion includes a second opening (60) mated with a corresponding one of the at least one first opening. The blade further includes at least one pair of openings that is a pair of the first opening and the second opening. The at least one aperture pair has a non-overlapping positional relationship in which the paired first aperture and second aperture are at least partially non-overlapping along a flow direction of a second fluid.

Description

CROSS-REFERENCE TO RELATED APPLICATION

This international application claims the advantage of Japanese Patent Application Number 2014-255334 , filed on Wednesday, December 17, 2014, at Japanese Patent Office, and the entire disclosure of patent application number 2014-255334 to which reference is made in this document.

FIELD OF THE INVENTION

The present disclosure relates to a heat exchanger.

GENERAL PRIOR ART

Known is an exhaust heat recovery device which is provided with a heat exchanger to exchange heat between exhaust gas from an internal combustion engine as a high-temperature fluid and a low-temperature fluid, and the waste heat recovered (see Patent Document 1 below). The heat exchanger described in Patent Document 1 is a stacked plate heat exchanger comprising a plurality of stacked plates having a flow space through which the low-temperature fluid flows. The plate of the heat exchanger described in Patent Document 1 includes a convex portion that protrudes from an outer surface of the plate.

DOCUMENTS OF THE STATE OF THE ART

PATENT DOCUMENTS

• Patent Document 1: International Publication WO2014 / 014080 ,

BRIEF SUMMARY OF THE INVENTION

TASKS TO BE SOLVED BY THE INVENTION

In the heat exchanger described in Patent Document 1, by providing a convex portion to the outer surface of the plate, a surface area of the outer surface of the plate is increased to thereby improve a heat exchange rate between the low-temperature fluid and the high-temperature fluid.

In general, heat exchangers must achieve an improvement in heat exchange rate from a high-temperature fluid to a low-temperature fluid, and a heat exchanger that achieves a higher heat exchange rate than that of the heat exchanger described in Patent Document 1 may be desired.

Accordingly, according to one aspect of the present disclosure, it is preferred to provide a heat exchanger that allows for an improved heat exchange rate from a high temperature fluid to a low temperature fluid.

MEANS TO SOLVE THE TASKS

One aspect of the present disclosure is a heat exchanger that exchanges heat between a first fluid and a second fluid. The heat exchanger comprises a plurality of plates and a lamella. The plurality of plates includes a flow path through which the first fluid flows. The fin couples mutually adjacent plates of the plurality of plates. Moreover, the blade comprises at least a first portion and at least a second portion.

Of these sections, the first section is a wall surface that includes at least a first opening. The second portion is a wall surface paired with the first portion and different from the first portion. The second portion includes a second opening that mates with a corresponding one of the at least one first opening.

In the fin of the one aspect of the present disclosure, the paired first portion and second portion provide a wave-shaped part. Moreover, the fin is such that the first portion and the second portion are each arranged in a direction orthogonal to a flow direction of the second fluid. The blade further includes at least one pair of openings that is a pair of the first opening and the second opening. The at least one aperture pair has a non-overlapping positional relationship in which the paired first aperture and second aperture are at least partially non-overlapping along the flow direction of the second fluid.

That is, the fin of one aspect of the present disclosure expands such that the wall surfaces are orthogonal to the flow direction of the second fluid. Thus, the second fluid contacts the entire wall surfaces of the fin, and a large contact area can be obtained.

Moreover, according to one aspect of the present disclosure, the second fluid that has passed through the first opening of the fin encounters a surface of the second portion that is the first Opposite opening. In the region of the second section, which is hit by the fluid, a flow of the second fluid is disturbed; thus, it is possible to inhibit the formation of a boundary layer in the region of the second portion to which the fluid impinges. Accordingly, according to one aspect of the present invention, the heat exchanger allows for inhibiting the formation of the boundary layer between the second fluid and the fin, and enables efficient heat transfer from the second fluid to the first fluid.

In other words, according to one aspect of the present disclosure, the heat exchanger enables further improvement of the heat exchange rate from a high-temperature fluid to a low-temperature fluid. According to one aspect of the present disclosure, the heat exchanger may be configured as a heat exchanger in which cylindrical plates are stacked in an axial direction. In this case, according to one aspect of the present disclosure, the sipe may be arranged along a circumferential direction of the plates.

In the aforementioned heat exchanger, the flow direction of the second fluid may be in a direction along a radial direction. Moreover, in the heat exchanger according to one aspect of the present disclosure, the first fluid flows along the circumferential direction of the plates. Thus, according to one aspect of the present disclosure, according to the heat exchanger, the flow direction of the second fluid may be in a direction orthogonal to the flow direction of the first fluid. Moreover, according to the heat exchanger according to one aspect of the present disclosure, it is achieved that the flow direction of the second fluid is in a direction orthogonal to the flow direction of the first fluid over all radial directions of the plates, that is, over a complete flow area of the second fluid ,

In the at least one opening pair of the heat exchanger according to one aspect of the present disclosure, the paired first opening and second opening along the flow direction of the second fluid may be completely non-overlapping. According to the aforementioned heat exchanger, a large area of the second portion may be struck by the second fluid having passed through the first opening. Thus, according to one aspect of the present disclosure, the heat exchanger enables the formation of the boundary layer around a portion of the second portion opposite to the first opening over a large area.

According to one aspect of the present disclosure, the fin in the heat exchanger may be such that all aperture pairs each have a non-overlapping positional relationship. According to the aforementioned heat exchanger, a much larger area of the second portion may be struck by the second fluid having passed through the first opening. Thus, according to one aspect of the present disclosure, the heat exchanger allows the formation of the boundary layer around a portion of the second portion opposite to the first opening on a much larger area.

BRIEF DESCRIPTION OF THE DRAWINGS

1 FIG. 15 is a perspective view showing a schematic external appearance of an exhaust heat recovery device in an embodiment. FIG.

2 FIG. 12 is a cross-sectional view of the exhaust valve closed loop heat recovery device taken along a line II-II in FIG 1 ,

3 is a side view of a heat exchanger.

4 Fig. 15 is a perspective view showing an outer appearance of a plate and a fin.

5 FIG. 12 is a perspective view showing an external appearance of a fin. FIG.

6 is a plan view of the slat.

DECLARATION OF THE REFERENCE SIGNS

• 1 ... exhaust heat recovery unit, 2 ... exhaust section, 4 ... casing member, 6 ... heat exchange section, 8th ... inflow, 10 ...Valve, 12 . 14 ... exhaust pipe, 16 ... upstream end, 18 ... downstream exhaust end, 20 ... outer jacket element, 22 ... cover element, 24 ... holding element, 28 ... heat exchange chamber 30 ... Heat exchanger, 32 ...Plate, 34 ... first plate section, 36 ... second plate section, 38 ... first communication section, 39 ... second communication section, 40 ... first cylindrical section, 42 ... second cylindrical section, 44 ... inflow, 46 ... outflow, 50 ... lamella 52 ...first section, 54 ...second part, 56 ... first opening, 58 ... first opening section, 60 ... second opening, 62 ... second opening section, 64 . 66 ...Gap, 80 ... introduction element, 102 ... valve body, 104 ... valve seat 108 ... sieve, 110 ... internal combustion engine, 112 ... exhaust (second fluid), 114 ... coolant (first fluid)

EMBODIMENT OF THE INVENTION

Hereinafter, an embodiment as an example of the present disclosure will be explained with reference to the drawings.

<Exhaust heat recovery unit>

An in 1 shown exhaust heat recovery device is installed in a moving body, which is an internal combustion engine 110 includes. The exhaust heat recovery device 1 exchanges heat between exhaust gas 112 from the internal combustion engine 110 as a high-temperature fluid and a coolant 114 of the internal combustion engine 110 as a low-temperature fluid to thereby heat from the exhaust gas 112 recover. The exhaust 112 In the present embodiment, an example of "a second fluid" of the present disclosure, and the coolant 114 is an example of "a first fluid" of the present disclosure. The coolant 114 The present embodiment may be cooling water or oil.

The exhaust heat recovery device 1 The present embodiment includes an exhaust section 2 , a sheath element 4 a heat exchange section 6 (please refer 2 ), an inflow section 8th (please refer 2 ) and a valve 10 , The exhaust section 2 includes a path that exhaust 112 from the internal combustion engine 110 downstream leads. The sheath element 4 is an element that has an outside of the exhaust section 2 covers.

The heat exchange section 6 includes a heat exchanger 30 (please refer 2 ), which is between the exhaust section 2 and the sheath element 4 is arranged, and it performs heat exchange between the exhaust gas 112 as a high temperature fluid and the low temperature fluid inside plates 32 of the heat exchanger 30 flows.

The inflow section 8th is a section where the exhaust gas 112 from the exhaust section 2 in the heat exchange section 6 flows. The valve 10 , which is a known valve that opens and closes a path, is downstream of the inflow section 8th along a flow path of the exhaust gas 112 in the exhaust section 2 arranged.

<Design of the exhaust heat recovery device>

Hereinafter, a description will be given of an embodiment of the exhaust heat recovery device 1 given.

As in 2 shown, includes the exhaust section 2 an exhaust pipe 12 , The exhaust pipe 12 is a cylindrical element. The exhaust 112 from the internal combustion engine 110 flows into the exhaust pipe 12 ,

The sheath element 4 includes an exhaust pipe 14 , an outer sheath element 20 , a lid element 22 and a holding element 24 , The exhaust pipe 14 is a generally cylindrical member having an upstream end 16 as an end having an opening with an inner diameter that is larger than an outer diameter of the exhaust pipe 12 , In an interior of the exhaust pipe 14 at the upstream end 16 is a downstream exhaust end 18 the exhaust pipe 12 which is an opposite end of an upstream end in a non-contact state with the sheath member 4 arranged.

The outer sheath element 20 is a cylindrical member having an inner diameter larger than a diameter of the exhaust pipe 12 , A downstream end of the outer jacket member 20 is at the upstream end 16 the exhaust pipe 14 coupled. The cover element 22 closes an upstream opening of the outer sheath element 20 along the flow path of the exhaust gas 112 in the exhaust pipe 12 ,

In other words, make the outer sheath element 20 , the lid element 22 and the exhaust pipe 12 a heat exchange chamber 28 ready, which is an annular space formed by the outer shell element 20 , the cover element 22 and the exhaust pipe 12 is surrounded. The heat exchanger 30 who is in the heat exchange chamber 28 is arranged, is a heat exchanger, in which the coolant 114 flows, and which is arranged so that it has an outer periphery of the exhaust pipe 12 covers.

<Configuration of the heat exchanger>

As in 3 shown includes the heat exchanger 30 In the present embodiment, a plurality of plates 32-1 to 32-N , an inflow line 44 , an outflow line 46 and a variety of slats 50-1 to 50-M , That is, the heat exchanger is a so-called stacked plate heat exchanger.

A symbol "N", which is an identifier representing the number of plates 32 indicates here is a positive integer of 2 or greater. Moreover, in the present embodiment, a symbol M is an identifier that the number of slats 50 indicates. For example, the symbol M is a positive integer smaller by "1" than N.

Each of the plates 32 includes a flow path through which the coolant 114 flows. The slat 50 couples mutually adjacent plates 32 from the variety of plates. The inflow line 44 is a conduit that causes the coolant 114 from outside the heat exchanger 30 in a plate 32 flows. The discharge line 46 is a conduit that causes the coolant 114 from a plate 32 from the heat exchanger 30 flows.

As in 4 shown includes each of the plates 32 a first plate section 34 and a second plate portion 36 , The first plate section 34 is an annular element. The first plate section 34 includes a wall portion extending from a periphery of the first plate portion 34 protruding in a same direction. The second plate section 36 is an annular element. The second plate section 36 includes a wall portion extending from a periphery of the second plate portion 36 protruding in a same direction.

Each of the plates 32 is achieved by engaging the wall portion of the first plate portion 34 in the wall portion of the second plate portion 36 educated. Each of the plates 32 includes a gap between an inner surface of the first plate portion 34 and an inner surface of the second plate portion 36 , The gap serves as a flow space in which the low-temperature fluid flows, that is, a flow path for the coolant 114 ,

Each of the plates 32 includes a first communication section 38 and a second communication section 39 , Of these communication sections, the first communication section comprises 38 a flow path through which the coolant 114 from the inflow line 44 from upstream to downstream along the flow path of the exhaust gas 112 in the exhaust section 2 in an adjacent plate 32 flows. The second communication section 39 includes a flow path through which the coolant 114 from downstream of the discharge line 46 along the flow path of the exhaust gas 112 in the exhaust section 2 in an adjacent plate 32 flows.

Both the first communication section 38 as well as the second communication section 39 The present embodiment includes a first cylindrical portion 40 and a second cylindrical portion 42 , The first cylindrical section 40 is a cylindrical portion erected from an opening corresponding to the first plate portion 34 is provided in a direction opposite to the wall portion. The second cylindrical section 42 is a cylindrical portion that is erected from a periphery of an opening, which is the second plate portion 36 is provided in a direction opposite to the wall portion.

When assembled, the first cylindrical sections function 40 that the first plate section 34 are provided, and the second cylindrical portions 42 that the second plate section 36 are provided as the first communication section 38 and second communication section 39 , The second cylindrical section 42 , the second plate section 36 is provided here means the second cylindrical portion 42 , the second plate section 36 is provided, which is adjacent to an outer surface of the first plate portion 35 through the slat 50 ,

An embodiment method of the first communication section 38 and the second communication section 39 is not limited to this, and any configuration in which these portions are configured may be used as the flow path for the coolant 114 through the plates 32 to act.

Each of the plates 32 is also arranged so that the the outer circumference of the exhaust pipe 12 covers. Each of the plates 32 is arranged so that it has a gap 64 between a middle side periphery of the plate 32 in a radial direction thereof and an outer surface of the exhaust pipe 12 having, wherein the gap 64 along a radial direction of the exhaust pipe 12 is positioned. Each of the plates 32 Moreover, it is arranged so that it has a gap 66 between an outer side periphery of the plate 32 in the radial direction thereof and an inner surface of the outer jacket member 20 having, wherein the gap 66 along a radial direction of the exhaust pipe 12 is positioned.

In this embodiment, the exhaust gas flows 112 in the present embodiment in a direction from the outer surface of the exhaust pipe 12 to the inner surface of the outer sheath member 20 along a radial direction of the plate 32 , The slat 50 is a truncated arch element attached to two adjacent plates 32 is coupled. As in 5 and 6 shown, includes the lamella 50 first sections 52-1 to 52-L and second sections 54-1 to 54-L , At the slat 50 are the first sections 52 and the second sections 54 coupled to thereby form a triangular wave-shaped part of the lamella 50 to provide in its entirety. A symbol "L" here is an integer of 1 or more.

The first sections 52 are each a rectangular plate section, as a wall surface of the lamella 50 acts. The first sections 52 each comprise at least a first opening section 58 who has a first opening 56 having. In the present embodiment, in the first sections 52 each the first openings 56 be arranged at equal intervals, or the first openings 56 may be arranged at unequal intervals.

The second sections 54 are each a rectangular plate section, with the first section 52 is paired and acts as a wall surface extending from the first section 52 different. Moreover, the second sections include 54 in each case at least one second opening section 62 that has a second opening 60 which has the first opening 56 is paired. In the present embodiment, the second portions may each have the second openings 60 be arranged at equal intervals, or the second openings 60 may be arranged at unequal intervals.

Areas of the individual first openings 56 , Areas of each second openings 60 , a total area of the first openings 56 and a total area of the second openings 60 can take into account a pressure of the exhaust gas 112 be determined appropriately. A side in a longitudinal direction of one of the first sections 52 is at a side in a longitudinal direction of one of the second portions 54 coupled. The other side in the longitudinal direction of one of the first sections 52 is on one side in a longitudinal direction of another of the second portions 54 coupled. In the aforementioned embodiment, the triangular wave-shaped part of the sipe becomes 50 provided in its entirety.

The slat 50 is moreover so to the plate 32 coupled to a bow of the lamella 50 along a circumferential direction of the plate 32 is arranged. At the slat 50 For example, tips on one side of the triangular waveform are attached to an outer surface of one of the plates 32 coupled. Remaining tips of the triangular waveform are on an outer surface of one of the other plates 32 coupled with one of the plates 32 is adjacent. In this embodiment, in the present embodiment, the first portions 52 and the second sections 54 each arranged in a direction which is orthogonal to the flow direction of the exhaust gas 112 ,

The individual first sections 52 can have the same number of first openings 56 regardless of the positions of the individual first sections 52 in a radial direction, or they may have a larger number of the first openings 56 have since the first section 52 is arranged closer to an outer periphery. It is also preferred that the number of second openings 60 at one of the second sections 54 is provided, is equal to the number of first openings 56 that on the first section 52 is provided, the one of the second sections 54 equivalent.

Of opening pairs 70 in the lamella 50 in which each one is a pair from the first opening 56 and the second opening 60 is, being the first opening 56 and the second opening 60 at least one of the pairs of openings 70 are at least partially non-overlapping, that is, in a non-overlapping positional relationship along the flow direction of the exhaust gas 112 ,

The opening pair 70 herein means a pair of the first opening 56 and the second opening 60 where the second opening 60 meets a specified condition, from the first openings 56 and the second openings 60 representing a single couple from the first section 52 and the second section 54 are provided. The condition stipulated herein may be that the second opening 60 closest to the first opening 56 is positioned, or it may be another condition.

The non-overlapping positional relationship in the present embodiment means, in particular, that the second opening 60 completely non-overlapping with the paired first opening 56 in the opening pair 70 in a normal direction of the first section 52 , The non-overlapping positional relationship includes, for example, a ratio in which the second openings 60 and the first openings 56 arranged in zigzag. In the present embodiment, a positional relationship between the first opening 56 and the second opening 60 that are each of the opening pairs 70 form, the non-overlapping positional relationship.

In the present embodiment, the gap functions 64 , the first openings 56 , the second openings 60 and the gap 66 as a flow path for the exhaust gases 112 , Heat exchange is performed between the high temperature fluid (a second fluid), which is the exhaust gas 112 is that through the gap 64 , the first openings 56 , the second openings 60 and the gap 66 flows, and the low-temperature fluid (a first fluid) containing the coolant 114 is that through each of the plates 32 flows. That is, in the present embodiment, the heat exchange chamber functions 28 in which the heat exchanger 30 is arranged as a heat exchange section 6 ,

The holding element 24 , this in 2 is shown is an element to the heat exchanger 30 to keep that in the heat exchange chamber 28 is arranged. An introductory element 80 is a cylindrical member having a diameter larger than that of the exhaust pipe 12 , and its one end to the retaining element 24 is coupled. The other end of the introductory element 80 opposite the one end, to the holding element 24 is coupled, has a diffuser-like shape with a gradually increasing diameter.

The introductory element 80 is arranged, an opening between the introduction element 80 and the exhaust pipe 12 provide. The opening acts as an inlet port for the exhaust gas 112 in the heat exchange section 6 , The valve 10 that has at least one valve body 102 and a valve seat 104 includes, closes the exhaust section 2 (the introductory element 80 ) by contact of the valve body 102 with the valve seat 104 , In the present embodiment, the diffuser-shaped end of the introduction element functions 80 as a valve seat 104 , The valve seat 104 However, the present disclosure is not limited to this configuration, but alternatively, a dedicated element may be provided.

A sieve element 108 having a screen-like configuration is on an inner peripheral surface of the valve seat 104 attached. The valve 10 The present embodiment opens the exhaust section 2 when a cooling temperature of the coolant 114 in the internal combustion engine 110 is higher than a predetermined temperature, which is determined beforehand. On the other hand, the valve closes 10 the exhaust section 2 when the cooling temperature of the coolant 114 in the internal combustion engine 110 lower than the specified temperature.

<Operation and effects of the exhaust heat recovery device>

When the valve 10 is closed, thereby the exhaust section 2 in the exhaust heat recovery device 1 to close, the exhaust gas flows 112 from the internal combustion engine 110 through the inflow section 8th in the heat exchange section 6 , and in the heat exchange section 6 will heat exchange with the coolant 114 carried out.

The slats 50 that the heat exchanger 30 are provided, extend such that the wall surfaces are orthogonal to the flow direction of the exhaust gas 112 , Thus, the exhaust gas touches 112 the entire wall surfaces of the slats 50 , Consequently, a large contact area between the slats 50 and the exhaust 112 be guaranteed, and a more effective heat transfer from the exhaust 112 to the coolant 114 can be reached.

Moreover, the exhaust gas hits 112 passing through the first opening 56 the slat 50 has reached an area of the first opening 56 of the second section 54 opposite. In the area of the second section 54 to which the exhaust 112 meets, the flow of exhaust gas 112 disturbed; thus, it is possible to form a boundary layer in the region of the second portion 54 to which the exhaust 112 meets, stop. Accordingly, the heat exchanger allows 30 a more effective heat transfer between the exhaust gas 112 that between the plates 32 flows, and the coolant 114 that through the plates 32 flows.

In the present embodiment, in particular, the first opening 56 and the second opening 60 leading to the at least one opening pair 70 are paired, completely non-overlapping along the flow direction of the exhaust gas 112 , and also all the pairs of openings 70 are in the non-overlapping positional relationship.

Thus, the heat exchanger allows 30 enlarging the area of the second section 54 to which the exhaust 112 that hits through the first openings 56 has arrived. According to the heat exchanger 30 Consequently, formation of a boundary layer in a larger area can be suppressed.

As previously described, the heat exchanger allows 30 a further improvement of the heat exchange rate from the high temperature fluid to the low temperature fluid. Moreover, the cylindrical plates 32 in the heat exchanger 30 stacked in an axial direction. The slats 50 are arranged so that their arches along the circumferential direction of the plates 32 are positioned.

Consequently, the heat exchanger allows 30 , the flow direction of the exhaust gas 112 in a direction along the radial direction of the plates 32 align. In the heat exchanger 30 With this configuration, the coolant flows 114 Moreover, along the circumferential direction of the plates 32 , Consequently, the heat exchanger allows 30 , the flow direction of the exhaust gas 112 in a direction orthogonal to the flow direction of the coolant 114 , The heat exchanger 30 allows, moreover, the flow direction of the exhaust gas 112 in a direction orthogonal to the flow direction of the coolant 114 in all radial directions of the plates 32 ,

Other Embodiments

Although the embodiment of the present disclosure has been described above, the present disclosure is not limited to the aforementioned embodiment, but may be embodied in various forms within the scope, which do not depart from the spirit of the present invention.

Although the cross-sectional shape of the lamella 50 in its entirety in the aforementioned embodiment, for example, is a triangular waveform, the cross-sectional shape of the fin 50 not limited to this shape, but may be a sinusoidal waveform, a rectangular waveform, or a sawtooth waveform. That is, the lamella 50 can have any cross-sectional shape, if the cross-sectional shape of the lamella 50 in its entirety is a waveform.

Moreover, in the aforementioned embodiment, the non-overlapping positional relationship is determined such that the first opening 56 and the second opening 60 that the at least one opening pair 70 form, completely non-overlapping along the flow direction of the exhaust gas 112 are; however, the non-overlapping positional relationship is not limited to this ratio, but may be a ratio at which the first opening 56 and the second opening 60 that the at least one opening pair 70 form, are at least partially non-overlapping.

Moreover, in the aforementioned embodiment, all the aperture pairs are 70 in each case the opening pair 70 having the non-overlapping positional relationship; at least one of the pairs of openings 70 However, the opening pair can 70 which has the non-overlapping positional relationship according to the present disclosure.

In the aforementioned embodiment, the opening acts between the downstream exhaust end 18 and the introduction element 88 as inflow port for exhaust gas 142 from the exhaust pipe 12 in the heat exchange section 6 ; the inlet port for exhaust gases 142 from the exhaust pipe 12 in the heat exchange section 6 can be holes in the exhaust pipe 12 are bored themselves.

The exhaust heat recovery device 1 moreover, according to the aforementioned embodiment, it is installed on a moving object which is the internal combustion engine 110 includes; however, it is not necessary that the exhaust heat recovery device of the present disclosure is installed on a moving object. That is, the exhaust heat recovery device of the present disclosure, which is configured, heat from the exhaust gas 112 by heat exchange using the exhaust gas 112 from the internal combustion engine 110 recover as high-temperature fluid can be used without being installed on a moving body. Moreover, the low-temperature fluid in the exhaust heat recovery device is not limited to the coolant 114 but may be any other fluid that acts as a low temperature fluid.

Although the heat exchanger 30 in the aforementioned embodiment, the exhaust heat recovery device 1 is applied, the heat exchanger 30 to facilities other than the exhaust heat recovery device 1 be applied. Moreover, the shape of the heat exchanger 30 not limited to a cylindrical shape. In the heat exchanger of the present disclosure, in particular, the plates 32 and the slats each having a rectangular shape or another shape, provided the slats 50 that the neighboring plates 32 are coupled so as to be orthogonal to the flow direction of the second fluid.

Any form in which a part of a configuration is omitted in the aforementioned embodiment may be an embodiment of the present disclosure. Moreover, any form in which the aforementioned embodiment and a modified example are properly combined may be one embodiment of the present disclosure. Moreover, any form conceivable within the scope, without departing from the spirit of the present disclosure, which is defined by the formulations recited in the claims, may be an embodiment of the present disclosure.

Claims (4)

A heat exchanger for exchanging heat between a first and a second fluid, wherein the heat exchanger comprises: a plurality of plates including a flow path through which the first fluid flows; and a blade configured to couple mutually adjacent plates of the plurality of plates, wherein the lamella comprises: at least a first portion that is a wall surface and includes at least a first opening; at least one second portion being a wall surface mated to the first portion and different from the first portion, the at least one second portion including a second opening mated to a corresponding one of the at least one first openings, wherein the paired first portion and second portion have a wave-shaped portion, and the first portion and the second portion are each arranged in a direction orthogonal to a flow direction of the second fluid; and at least one pair of openings that is a pair of the first opening and the second opening, wherein the at least one aperture pair has a non-overlapping positional relationship in which the paired first aperture and second aperture are at least partially non-overlapping along the flow direction of the second fluid. The heat exchanger according to claim 1, wherein each of the plurality of plates has a cylindrical shape, wherein the plurality of plates are arranged along an axial direction, and wherein the fin is disposed along a circumferential direction of the plates. Heat exchanger according to claim 1 or 2, wherein the at least one pair of openings is such that the paired first opening and second opening are completely non-overlapping along the flow direction of the second fluid. A heat exchanger according to any one of claims 1 to 3, wherein the fin is such that each of the pairs of apertures has the non-overlapping ratio.

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