JP2022118413A - Heat exchanger - Google Patents

Abstract

To improve heat transfer efficiency.SOLUTION: A pressure vessel 20 comprises: an accommodation pipe 21 having a flow passage 32 in which a plurality of hole parts 321 for making a first fluid circulate therein are arranged in parallel, and accommodating a plurality of flat porous pipes 30 in which a plurality of fins 33 are arranged in parallel at a front surface 31a and a rear surface 31b; a first mirror plate 22 for making the first fluid flow into the flow passage 32 by blocking one end part of the accommodation pipe; and a second mirror plate 23 for discharging the first fluid which flows out of the flow passage 32 by blocking the other end part of the accommodation pipe. The accommodation pipe 21 has a second introduction port 211 for introducing a second fluid therein, and a second discharge port 212 for discharging a second fluid which has passed the inside of the first introduction port. The plurality of flat porous pipes 30 are accommodated in a form that the second fluid is permitted to flow between adjacent pseudo flow passages GR while making the second fluid circulate in the pseud flow passages GR which are formed by connecting fins 33 which approximate one another between the adjacent flat porous pipes 30 by a virtual line K in a form that the front surface 31a and the rear surface 31b oppose each other.SELECTED DRAWING: Figure 11

Description

TECHNICAL FIELD The present invention relates to a heat exchanger, and more particularly to a heat exchanger for exchanging heat between two fluids.

Conventionally, as a heat exchanger for exchanging heat between two fluids, there is known one that includes a plurality of heat transfer tubes, an inlet header, an outlet header, and a pressure vessel.

The plurality of heat transfer tubes have a cylindrical shape and are arranged side by side with a space therebetween so that their longitudinal directions are aligned with each other. The hollow portions of these heat transfer tubes form flow paths. The inlet header allows passages of the heat transfer tubes to communicate with each other and allows the first fluid to flow into the passages of the heat transfer tubes. The outlet header communicates the outlets of the flow paths of the heat transfer tubes with each other and allows the first fluid flowing out of the flow paths of the heat transfer tubes to pass therethrough. The pressure vessel includes an accommodation chamber that accommodates a plurality of heat transfer tubes, and has an inlet port that allows the second fluid to flow into the accommodation chamber and an outlet port that allows the second fluid to flow out of the accommodation chamber.

In such a heat exchanger, the first fluid flows from the inlet header into each heat transfer tube and passes through the heat transfer tubes, and the second fluid flows from the inlet port into the housing chamber and passes outside the heat transfer tubes. It is possible to exchange heat with a fluid (see, for example, Patent Document 1).

Japanese Patent Application Laid-Open No. 2002-310577

By the way, in the heat exchanger described above, each heat transfer tube has a cylindrical shape, and it is necessary to provide a gap between the heat transfer tubes. The number of heat transfer tubes accommodated in the accommodation chamber must be increased while the diameter of the heat tubes is reduced. However, there is a limit in terms of dimensional accuracy in increasing the number of heat transfer tubes while securing a gap between the heat transfer tubes while reducing the diameter of the heat transfer tubes. It was difficult.

SUMMARY OF THE INVENTION An object of the present invention is to provide a heat exchanger capable of improving heat transfer efficiency.

To achieve the above object, a heat exchanger according to the present invention is a heat exchanger for exchanging heat between a first fluid and a second fluid inside a pressure vessel, wherein the pressure vessel comprises: and a plurality of fins extending along the longitudinal direction of the holes on the front surface and the back surface are arranged in parallel in the parallel direction of the holes. A cylindrical accommodation tube that accommodates the flat perforated tubes in such a manner that the extending direction of the hole matches the axial direction of the tube, and the accommodation while communicating the inlets of the flow paths of the plurality of flat perforated tubes. a first end plate that is attached in a manner that closes one end of the pipe and allows the first fluid introduced from a first inlet formed therein to flow into the flow channel of each of the flat perforated pipes; It is attached in such a manner that the outlets of the channels of the perforated tubes are communicated with each other and the other ends of the storage tubes are closed, and the first fluid that has flowed out from the channels of the flat perforated tubes is formed in itself. a second end plate for discharging from one discharge port, the containing pipe is formed at an arbitrary location on the side circumference of the containing pipe, and a second inlet for introducing the second fluid into the inside of the containing pipe; a second discharge port formed at a portion of the periphery spaced apart from the second inlet and adapted to discharge the second fluid that has passed through the housing tube, the front surface and the back surface facing each other; While the second fluid is circulated in a pseudo flow channel formed by connecting fins that are close to each other between adjacent flat perforated tubes with a virtual line, between the pseudo flow channels that are adjacent to each other The plurality of flat perforated tubes are accommodated in a manner that allows the second fluid to flow.

Further, according to the present invention, in the heat exchanger described above, a gap is provided between the fins adjacent to each other between the flat perforated tubes that are adjacent to each other with the front surface and the back surface facing each other. The present invention is characterized in that the plurality of flat perforated tubes are accommodated in a mode.

Further, in the above heat exchanger, the second heat exchanger is arranged in a manner surrounding a housing area for housing the plurality of flat perforated tubes inside the housing tube, and introduced from the second inlet. a spacer member that allows the fluid to pass toward the accommodation area and allows the second fluid that has passed through the accommodation area to pass toward the second discharge port; and an outer surface of the spacer member. are provided at predetermined intervals along the axial direction of the storage tube in a manner projecting toward the inner peripheral surface of the storage tube, and when the outer end portion thereof contacts the inner peripheral surface, the and a plurality of joint members for restricting the spacer member from approaching the inner peripheral surface.

Further, in the heat exchanger according to the present invention, the spacer member is attached to the outer surface of the spacer member so as to extend along the circumferential direction, and a part of the spacer member contacts the inner peripheral surface of the accommodation tube and is elastically deformed. a stopper member for restricting passage of the second fluid between the spacer member and the storage tube along the axial direction of the storage tube, wherein the stopper member surrounds the spacer member and a packing supporting portion that sandwiches the packing vertically in such a manner that the outer peripheral edge of the packing protrudes radially outward and is joined to the outer surface of the spacer member by welding. , and the outer peripheral edge of the packing is elastically deformed by coming into contact with the inner peripheral surface of the accommodating tube.

Further, according to the present invention, in the heat exchanger described above, each of the plurality of flat perforated tubes has a fine rectangular cross-sectional shape perpendicular to the longitudinal direction of the hole.

Further, according to the present invention, in the above heat exchanger, the plurality of flat perforated tubes are made of aluminum.

According to the present invention, the pressure vessel has a flow path in which a plurality of holes for circulating the first fluid are arranged in parallel, and a plurality of fins extending along the longitudinal direction of the holes are arranged on the front surface and the back surface. A cylindrical storage tube that accommodates the plurality of flat perforated tubes so that the extending direction of the hole matches the axial direction of the tube, and the inlets of the flow paths of the plurality of flat perforated tubes are communicated with each other. a first end plate that is attached in a manner that closes one end of the storage tube and allows the first fluid introduced from the first inlet formed therein to flow into the flow path of each of the flat perforated tubes; and a plurality of flat perforated tubes. The first fluid flowing out of the flow path of each flat perforated tube is discharged from the first discharge port formed in itself. a second end plate that allows the second fluid to be introduced into the interior of the storage tube, and a second inlet that is formed at an arbitrary location on the side periphery of the storage tube to introduce the second fluid into the interior of the storage tube; Since the second discharge port is formed at an isolated location and discharges the second fluid that has passed through the inside of the accommodation tube, the heat transfer area can be increased by the plurality of flat perforated tubes. This has the effect of improving the transmission efficiency.

In addition, the storage pipe allows the second fluid to flow through a pseudo flow path formed by connecting fins close to each other between flat perforated pipes adjacent to each other with the front surface and the back surface facing each other with imaginary lines. Since a plurality of flat perforated tubes are accommodated in a manner that allows the second fluid to flow between the pseudo flow paths adjacent to each other, the second fluid flows only in a part of the pseudo flow paths. It is possible to suppress the occurrence of the heat, and the second fluid can be evenly passed through the pseudo-flow paths, thereby achieving an effect that the heat transfer efficiency can be improved.

FIG. 1 is a schematic diagram schematically showing the overall configuration of a refrigeration cycle apparatus to which a heat exchanger according to an embodiment of the invention is applied. FIG. 2 is a right side view showing the heat exchanger according to the embodiment of the invention. FIG. 3 is an exploded perspective view showing a heat exchanger that is an embodiment of the present invention. FIG. 4 is an exploded perspective view showing a heat exchanger that is an embodiment of the present invention. FIG. 5 is a cross-sectional view showing the internal structure of the heat exchanger according to the embodiment of the invention. FIG. 6 is a cross-sectional view showing the internal structure of the heat exchanger according to the embodiment of the invention. FIG. 7 is a cross-sectional view showing an enlarged main part of the internal structure of the heat exchanger according to the embodiment of the invention. FIG. 8 is a cross-sectional view showing an enlarged main part of the internal structure of the heat exchanger according to the embodiment of the invention. FIG. 9 is a perspective view showing the flat perforated tube shown in FIGS. 3 to 8. FIG. 10 is a cross-sectional view showing a cross section of the flat perforated tube shown in FIG. 9. FIG. FIG. 11 is a cross-sectional view enlarging the arrangement of the perforated flat tubes in the storage area shown in FIGS. 7 and 8. FIG. FIG. 12 is a perspective view showing a perforated flat tube housed inside the housing tube shown in FIGS. 2 to 8, and a spacer member and a stopper member as peripheral structures thereof. 13 is an exploded perspective view of the spacer member shown in FIG. 12; FIG. FIG. 14 is a cross-sectional view of the interior of the containment tube shown in FIGS. 2-8. 15 is an exploded perspective view of the stopper member shown in FIG. 12. FIG. FIG. 16 is a longitudinal sectional view of a main portion of the containing tube for explaining the function of the stopper member shown in FIG. 15;

Preferred embodiments of a heat exchanger according to the present invention will be described in detail below with reference to the accompanying drawings.

FIG. 1 is a schematic diagram schematically showing the overall configuration of a refrigeration cycle apparatus to which a heat exchanger according to an embodiment of the invention is applied. The refrigerating cycle device 1 exemplified here has a first refrigerating cycle 1a in which a first fluid circulates and a second refrigerating cycle 1b in which a second fluid circulates. It is a dual refrigeration cycle configured to exchange heat with a second fluid, which is a refrigerant, in a heat exchanger 10 .

This refrigerating cycle apparatus 1 can use the cold heat generated, for example, by the first evaporator 5 of the first refrigerating cycle 1a for various refrigerating devices such as air conditioners and showcases.

The first refrigerating cycle 1a includes a first compressor 2, a first condenser 3, a heat exchanger 10, a first expansion mechanism 4, and a first evaporator 5, which are sequentially connected by pipes HK. The second refrigerating cycle 1b is constructed by connecting a second compressor 6, a second condenser 7, a second expansion mechanism 8, and a heat exchanger 10 in sequence with a pipe HK.

The heat exchanger 10 exchanges heat between the high-pressure first fluid that has passed through the first condenser 3 of the first refrigerating cycle 1a and the low-pressure second fluid that has passed through the second expansion mechanism 8 of the second refrigerating cycle 1b. It is an intermediate heat exchanger that In this heat exchanger 10, the first fluid condenses and the second fluid evaporates. The configurations of the first refrigerating cycle 1a and the second refrigerating cycle 1b can be changed as appropriate, and the heat exchanger 10 may be used other than the intermediate heat exchanger of such a binary refrigerating cycle.

The first fluid, which is the refrigerant that circulates through the first refrigerating cycle 1a, and the second fluid, which is the refrigerant that circulates through the second refrigerating cycle 1b, are, for example, natural refrigerants, CFC alternative refrigerants, and the like. In the present embodiment, when the second fluid flows into the heat exchanger 10, the pressure is higher than the atmospheric pressure, and the first fluid flows into the heat exchanger 10 under a higher pressure than the second fluid. is.

2 to 6 show a heat exchanger 10 according to an embodiment of the present invention, wherein FIG. 2 is a right side view, FIGS. 3 and 4 are exploded perspective views, and FIGS. It is a sectional view showing a structure. As shown in FIGS. 2 to 6, the heat exchanger 10 has a pressure vessel 20. The pressure vessel 20 is configured with a housing tube 21, a first end plate 22 and a second end plate 23. ing.

The housing tube 21 is made of steel, for example, and has a cylindrical shape. The axial direction of this housing tube 21 coincides with the vertical direction. The containing tube 21 is provided with a first reinforcing ring 24a and a second reinforcing ring 24b.

As shown in FIG. 7, the first reinforcing ring 24a is made of a high-strength material such as stainless steel and has an annular shape. The outer diameter of the first reinforcing ring 24a is slightly smaller than the inner diameter of the housing tube 21, and a part of the outer peripheral surface is joined to the inner peripheral surface of the upper end portion of the housing tube 21 via an interposing member. It is attached by being More specifically, the first reinforcing ring 24a is attached so as to protrude upward from the upper end opening of the containing tube 21 .

A disc-shaped first end plate 251 is joined by welding or the like so as to close the upper opening of the first reinforcing ring 24a. The first end plate 251 is made of a metal material such as aluminum.

As shown in FIG. 8, the second reinforcing ring 24b is made of a high-strength material such as stainless steel and has an annular shape. The outer diameter of the second reinforcing ring 24b is slightly smaller than the inner diameter of the housing tube 21, and a part of the outer peripheral surface of the second reinforcing ring 24b is joined to the inner peripheral surface of the lower end of the housing tube 21 via an interposing member. It is attached by being More specifically, the second reinforcing ring 24b is attached so as to protrude downward from the opening at the lower end of the housing tube 21 .

A disk-shaped second end plate 252 is joined by welding or the like so as to close the opening of the lower surface of the second reinforcing ring 24b. Like the first end plate 251, the second end plate 252 is made of a metal material such as aluminum.

The first reinforcing ring 24a and the second reinforcing ring 24b are formed so that the thickness dimension (thickness dimension in the radial direction) is larger than the thickness dimension of the containing tube 21, and has sufficiently high strength. . Also, the vertical dimension of the first reinforcing ring 24a and the second reinforcing ring 24b is determined by the first end plate 251 and the second reinforcing ring 24b when the first reinforcing ring 24a and the second reinforcing ring 24b are joined to the housing tube 21 by welding or the like. The temperature is adjusted to such an extent that the second end plate 252 does not melt.

The first end plate 251 and the second end plate 252 form a pair of upper and lower ends, and through holes 251a and 252a corresponding to each other are formed. In the accommodation area 26 between the first end plate 251 and the second end plate 252, a plurality of flat perforated tubes 30 are accommodated so as to pass through the through holes 251a and 252a.

As shown in FIGS. 9 and 10, the flat perforated tube 30 is made of a metal material such as aluminum, and includes a base portion 31, a flow path 32, and a plurality of fins 33. .

The base portion 31 is a strip-shaped flat elongated plate-like member. The flow path 32 has a plurality of holes 321 penetrating through the base body 31 along the longitudinal direction, and is configured by arranging a plurality of these holes 321 in parallel in the width direction. Each hole 321 forming the flow path 32 is a path having a fine rectangular cross-sectional shape orthogonal to the longitudinal direction, and is a fine path called a mini-channel or a micro-channel. A plurality of fins 33 are formed on the front surface 31a and the rear surface 31b of the base portion 31 except for the upper end portion 31c and the lower end portion 31d. These fins 33 are elongated and extend along the longitudinal direction of the hole 321 and are arranged side by side along the width direction.

A plurality of flat perforated tubes 30 having such a configuration are housed in the housing area 26 such that the longitudinal direction (longitudinal direction of the holes 321 ) is along the axial direction of the housing tube 21 . More specifically, the upper end portion 31c and the lower end portion 31d of the front surface 31a and the rear surface 31b of the base portion 31 are cut to form a step between them and the portion where the fins 33 are formed. The upper end portion 31c passes through the corresponding through hole 251a of the first end plate 251 from below and is joined by brazing, while the lower end portion 31d passes through the corresponding through hole 252a of the second end plate 252 from above. By being joined by brazing in a penetrating state, the plurality of flat perforated tubes 30 are accommodated in the accommodation tube 21 while being slightly separated from each other in a manner that the width direction (parallel direction of the holes 321) coincides with the front-rear direction. It is

11, between two flat perforated tubes 30 adjacent to each other such that the front surface 31a of the base portion 31 and the back surface 31b of the base portion 31 face each other, fins that are close to each other are formed. A gap S is provided between 33 . A pseudo flow path GR is formed by connecting the fins 33 that are close to each other with a virtual line K through the gap S. The pseudo flow path GR is a flow path that allows the second fluid to flow, although the details will be described later.

The size of the gap S, that is, the size of the separation distance α between the fins 33 adjacent to each other is about 0.5 mm, and the distance between the fins 33 from the front surface 31a of the base portion 31 or the back surface 31b of the base portion 31 is approximately 0.5 mm. The ratio to the projecting length (length in the horizontal direction) β is about 0.2 to 0.4.

In this way, the separation distance α has a ratio of about 0.2 to 0.4 with respect to the protruding length β of the fins 33, so that the second fluid flows between the pseudo flow paths GR adjacent to each other. allowing it to flow. Incidentally, if the ratio of the separation distance α to the protrusion length β of the fins 33 is less than 0.2, the flow of the second fluid between the adjacent pseudo flow paths GR is restricted. On the other hand, if the ratio of the separation distance α to the protrusion length β of the fins 33 exceeds 0.4, it is difficult to form the pseudo flow path GR, which is not preferable.

The first end plate 22 is, for example, a hemispherical one made of steel or the like, and is attached in a manner that closes the upper end of the storage tube 21 . The first end plate 22 forms a distribution flow path 221 facing the upper end openings of the holes 321 of the plurality of flat perforated tubes 30 between the housing tube 21 and a first inlet 222 formed at the top. .

A first reinforcing attachment tube 41 is provided in the first introduction port 222 . The first reinforcing attachment tube 41 is formed of, for example, steel and has a substantially cylindrical shape, and is attached such that a part of the lower end portion 41a is inserted into the first introduction port 222 from above. That is, the first reinforcing attachment tube 41 is attached in a state in which the remaining portion of the lower end portion 41a and the upper end portion 41b protrude upward (outside the housing tube 21) from the first inlet 222. As shown in FIG.

The inner diameter of the upper end portion 41b of the first reinforcing mounting cylinder 41 matches the outer diameter of the pipe HK to be connected, that is, the outer diameter of the pipe HK connected to the outlet side of the first condenser 3 of the first refrigerating cycle 1a. The inner diameter of the lower end portion 41a is smaller than the outer diameter of the pipe HK.

As a result, a step 41c is formed at the boundary between the upper end portion 41b and the lower end portion 41a inside the first reinforcing mounting tube 41, and the end face of the pipe HK inserted into the first reinforcing mounting tube 41 is The outer surface is joined to the inner surface of the upper end portion 41b by brazing or the like while being in contact with the step 41c.

Thus, the distribution channel 221 distributes the first fluid introduced from the first inlet 222 to each hole 321 . That is, the first end plate 22 allows the inlets of the flow paths 32 of the plurality of flat perforated tubes 30 to communicate with each other through the distribution flow paths 221, and allows the first fluid to flow into the flow paths 32 of the flat perforated tubes 30. .

The second end plate 23 is made of, for example, steel and has a hemispherical shape, and is attached to close the lower end of the housing tube 21 . The second end plate 23 forms a collective flow path 231 facing the lower end openings of the holes 321 of the plurality of flat perforated tubes 30 between the storage tube 21 and a first discharge port 232 formed at the top. .

A second reinforcing mounting tube 42 is provided at the first discharge port 232 . The second reinforcing mounting cylinder 42 is formed of, for example, a steel material and has a substantially cylindrical shape, and is mounted such that a part of the upper end portion 42a is inserted into the first discharge port 232 from below. That is, the second reinforcing mounting cylinder 42 is mounted in a state in which the remaining portion of the upper end portion 42a and the lower end portion 42b protrude downward (outside the housing tube 21) from the first discharge port 232. As shown in FIG.

The inner diameter of the lower end portion 42b of the second reinforcing mounting cylinder 42 matches the outer diameter of the pipe HK to be connected, that is, the pipe HK connected to the inlet side of the first expansion mechanism 4 of the first refrigerating cycle 1a. The inner diameter of the upper end portion 42a is smaller than the outer diameter of the pipe HK.

As a result, a step 42c is formed at the boundary between the upper end portion 42a and the lower end portion 42b inside the second reinforcing mounting tube 42, and the end face of the pipe HK inserted into the second reinforcing mounting tube 42 is The outer surface is joined to the inner surface of the lower end portion 42b by brazing or the like while being in contact with the step 42c.

As a result, the collecting flow path 231 collects the first fluid that has flowed out through the holes 321 and passes it through the pipe HK connected to the inlet side of the first expansion mechanism 4 of the first refrigerating cycle 1a. It is. That is, the second end plate 23 communicates the outlets of the flow paths 32 of the plurality of flat perforated tubes 30 with each other, and discharges the first fluid flowing out of the flow paths 32 of the flat perforated tubes 30 from the first discharge port 232. be.

By the way, a second introduction port 211 and a second discharge port 212 are formed in the side peripheral portion of the accommodation tube 21 . The second introduction port 211 is formed in the lower end side front portion of the accommodation tube 21, as also shown in FIG. A third reinforcing attachment tube 43 is provided in the second introduction port 211 .

The third reinforcing mounting tube 43 is formed of, for example, steel and has a substantially cylindrical shape, and is mounted with a part of the rear end portion 43a inserted into the second inlet 211 from the front. . That is, the third reinforcing mounting tube 43 is mounted in a state in which the remaining portion of the rear end portion 43a and the front end portion 43b protrude forward (outside the housing tube 21) from the second inlet 211. As shown in FIG.

The inner diameter of the front end portion 43b of the third reinforcing mounting cylinder 43 matches the outer diameter of the piping HK to be connected, that is, the piping HK connected to the outlet side of the second expansion mechanism 8 of the second refrigerating cycle 1b. The inner diameter of the rear end portion 43a is smaller than the outer diameter of the pipe HK.

As a result, a step 43c is formed at the boundary between the front end portion 43b and the rear end portion 43a inside the third reinforcing mounting tube 43, and the end face of the pipe HK inserted into the third reinforcing mounting tube 43 is in contact with the step 43c, the outer surface thereof is joined to the inner surface of the front end portion 43b by brazing or the like. Therefore, the second inlet 211 introduces the second fluid into the housing tube 21 .

The second discharge port 212 is formed in the rear portion of the upper end side of the housing tube 21, as shown in FIG. A fourth reinforcing mounting tube 44 is provided at the second discharge port 212 .

The fourth reinforcing attachment tube 44 is formed of, for example, steel and has a substantially cylindrical shape, and is attached such that a part of the front end portion 44a is inserted into the second discharge port 212 from behind. That is, the fourth reinforcing mounting tube 44 is mounted in a state in which the remaining portion of the front end portion 44a and the rear end portion 44b protrude rearward (outside the housing tube 21) from the second discharge port 212. As shown in FIG.

The inner diameter of the rear end portion 44b of the fourth reinforcing mounting cylinder 44 matches the outer diameter of the pipe HK to be connected, that is, the pipe HK connected to the inlet side of the second compressor 6 of the second refrigerating cycle 1b. , the inner diameter of the front end portion 44a is smaller than the outer diameter of the pipe HK.

As a result, a step 44c is formed at the boundary between the front end portion 44a and the rear end portion 44b inside the fourth reinforcing mounting tube 44, and the end face of the pipe HK inserted into the fourth reinforcing mounting tube 44 is formed. is in contact with the step 44c, the outer surface of the rear end portion 44b is joined to the inner surface of the rear end portion 44b by brazing or the like. Therefore, the second discharge port 212 discharges the second fluid that has passed through the inside of the accommodation tube 21 .

A spacer member 50 and a stopper member 60 are provided inside the housing tube 21 as shown in FIG.

The spacer member 50 is provided so as to surround the accommodation area 26 that accommodates the plurality of flat perforated tubes 30 . As shown in FIG. 13, the spacer member 50 includes a pair of left and right spacer constituent members 51. As shown in FIG.

The two spacer members 51 are made of sheet metal or the like and have the same shape, and have recesses 51a formed in their inner surfaces facing each other to form hat-shaped cross sections. These spacer constituent members 51 are elongated members whose longitudinal direction is the vertical direction. is defining.

As shown in FIG. 8, such a spacer member 50 allows the second fluid introduced from the second inlet to pass toward the storage area 26, and as shown in FIG. It allows the second fluid that has passed through the storage area 26 to pass toward the second discharge port.

A plurality of stiffening joints (joint members) 52 are provided on the outer surface of such a spacer member 50 . The stiffening joints 52 are attached to the outer surface of each spacer member 51 in the vertical direction of the spacer member 51, i.e., along the axial direction of the housing tube 21, in such a manner that they are joined to the outer surface portion forming the recess 51a. are provided at predetermined intervals.

The height level of the stiffening joint 52 attached to the outer surface of one spacer constituent member 51 and the height level of the stiffening joint 52 attached to the outer surface of the other spacer constituent member 51 should be the same. is preferably provided in

That is, these stiffening joints 52 have outer ends 52a that are substantially arc-shaped, and as shown in FIG. They are provided at predetermined intervals along the axial direction of the containing tube 21 in a manner projecting toward the surface. More specifically, the stiffening joint 52 is provided on the outer surface of the spacer-constituting member 51 so as to protrude in a direction perpendicular to the width direction of the perforated flat tube 30 (the parallel direction of the holes 321), Each outer end portion 52 a is close to the inner peripheral surface of the containing tube 21 . The stiffening joint 52 restricts the spacer member 50 from approaching the inner peripheral surface of the housing tube 21 when the outer end portion 52a is in contact with the inner peripheral surface.

The stopper member 60 is provided on the outer surface of the spacer member 50 along the circumferential direction at an intermediate height position of the spacer member 50, specifically, at an approximately intermediate position between the first end plate 251 and the second end plate 252. It is an annular one arranged in the same direction.

15, the stopper member 60 includes a packing 61, an inner support member 62, a lower support member 63, and an upper support member 64. As shown in FIG.

The packing 61 is an annular one made of a resin material such as rubber, and has an outer diameter slightly larger than the inner diameter of the housing tube 21 .

The inner support member 62 includes a pair of left and right inner support components 62a. Each of the inner support members 62a has a substantially semicircular shape, an outer edge 621 having an arc shape, and a notch 622 corresponding to the outer shape of the spacer member 51 corresponding to the inner edge. ing. The inner supporting member 62 formed by the inner supporting structural members 62 a has an outer diameter that matches the inner diameter of the packing 61 .

The lower support member 63 includes a pair of left and right lower support components 63a. Each of these lower support component members 63a has a substantially semicircular shape, an outer edge portion 631 is arc-shaped, and a notch 632 corresponding to the outer shape of the spacer component member 51 corresponding to the inner edge portion is formed. It is The lower support member 63 formed by these lower support constituent members 63 a has an outer diameter larger than the inner diameter of the packing 61 and smaller than the inner diameter of the housing tube 21 .

The upper support member 64 constitutes the packing support portion of the present invention together with the inner support member 62 and the lower support member 63, and includes a pair of left and right upper support members 64a. Each of the upper support component members 64a has a substantially semicircular shape, an outer edge portion 641 having an arc shape, and a notch 642 corresponding to the outer shape of the spacer component member 51 corresponding to the inner edge portion. ing. In addition, in the upper support component member 64a, a welding margin 643 is provided by extending a part of the edge portion forming the notch 642 upward. The upper support member 64 formed by the upper support component members 64 a has an outer diameter larger than the inner diameter of the packing 61 and smaller than the inner diameter of the housing tube 21 .

In such a stopper member 60, the inner support member 62 is arranged inside the packing 61, the lower support member 63 is arranged below the packing 61 and the inner support member 62, and the upper support member 64 is arranged above. By inserting the rivets 65 from below into the mounting holes 624, 634, 644 formed in the inner support member 62, the lower support member 63 and the upper support member 64, the outer peripheral edge of the packing 61 is radially outward. It is sandwiched between the lower support member 63 and the upper support member 64 so as to protrude outward. Then, the spacer member 50 is relatively inserted into the hollow portion formed by the notch 622, and the welding allowance 643 is welded to the outer surface of the recess 51a in the spacer component member 51 at the intermediate height position of the spacer member 50. By doing so, the stopper member 60 can be arranged in such a manner that the packing 61 surrounds the spacer member 50 .

Since the outer diameter of the packing 61 of the stopper member 60 is formed to be larger than the inner diameter of the housing tube 21, the outer peripheral edge of the packing 61 conforms to the inner peripheral surface of the housing tube 21, as shown in FIG. They are placed in contact and elastically deformed.

In the heat exchanger 10 configured as described above, the first fluid introduced from the outside is introduced from the first inlet 222 into the distribution channel 221, passes through the distribution channel 221, and passes through each flat perforated tube. 30 into the flow path 32 . The first fluid that has flowed into the channel 32 of each flat perforated tube 30 in this way flows through the channel 32 from top to bottom, passes through the collective channel 231, and exits from the second outlet 212 to the outside. is discharged to

On the other hand, the second fluid (liquid) introduced from the second inlet 211 flows into the housing area 26 from between the second reinforcing ring 24b and the spacer member 50, as shown in FIG. The second fluid that has flowed into the storage area 26 passes upward through the pseudo flow paths GR between the flat porous tubes 30 adjacent to each other, and passes through the flow paths 32 of the flat porous tubes 30 . Heat is exchanged between the first fluid and the second fluid passing outside each flat perforated tube 30, the first fluid condenses, and the second fluid evaporates into gas. After that, the second fluid that has passed through the housing area 26 flows out from between the first reinforcing ring 24 a and the spacer member 50 to the outside of the spacer member 50 , and is then discharged to the outside through the second outlet 212 .

According to the heat exchanger 10 of the embodiment of the present invention, the plurality of flat perforated tubes 30 housed in the housing tube 21 of the pressure vessel 20 have the plurality of holes 321 through which the first fluid passes. Since the flow passages 32 are arranged in parallel, and the plurality of fins 33 extending along the longitudinal direction of the hole 321 are arranged side by side on the front surface 31a and the back surface 31b, the heat transfer area can be expanded. It is possible to improve the heat transfer efficiency. Since the heat transfer efficiency can be improved in this way, the size of the heat exchanger 10 itself can be reduced if the same amount of heat exchange as in the conventional case is secured. In particular, in the plurality of flat perforated tubes 30, the cross-sectional shape orthogonal to the longitudinal direction of the hole portions 321 is a fine rectangular shape, so that the first fluid passing through each hole portion 321 is caused to flow through the hole portion due to surface tension. They gather at the corners of 321, making it easy to expose the central regions of the sides, thereby promoting heat exchange between the first fluid and the second fluid.

Moreover, according to the heat exchanger 10, the fins 33 adjacent to each other between the adjacent flat perforated tubes 30 in such a manner that the front surface 31a of the base portion 31 and the back surface 31b of the base portion 31 face each other are defined by the imaginary line K. Since the second fluid is allowed to flow between the adjacent pseudo flow paths GR while allowing the second fluid to flow through the pseudo flow paths GR formed by connecting with It is possible to suppress the occurrence of a so-called one-way flow in which the second fluid flows only in the passage GR, and the second fluid can be evenly passed through the pseudo passages GR, thereby improving the heat transfer efficiency.

Further, according to the heat exchanger 10 , the spacer member 50 is arranged in a manner surrounding the housing area 26 that houses the plurality of flat perforated tubes 30 inside the housing tube 21 , and is introduced from the second inlet 211 . The outer surface of the spacer member 50 is provided with a The stiffening joints 52 protrude toward the inner peripheral surface of the storage tube 21 and are provided at predetermined intervals along the axial direction of the storage tube 21, and their outer ends 52a are in contact with the inner peripheral surface. In this case, since the spacer member 50 restricts the proximity of the inner peripheral surface, each flat perforated tube 30 whose longitudinal direction is the vertical direction is thermally expanded and contracted by the passage of the first fluid and the second fluid. Buckling can be suppressed.

Furthermore, according to the heat exchanger 10, the stopper member 60 disposed at the intermediate height position of the spacer member 50 is attached to the outer surface of the spacer member 50 in a manner extending along the circumferential direction, and itself is elastically deformed by contacting the inner peripheral surface of the housing tube 21, the second packing 61 is elastically deformed along the axial direction of the housing tube 21 between the spacer member 50 and the housing tube 21. Fluid passage can be restricted. Since the packing 61 of the stopper member 60 has an annular shape surrounding the spacer member 50 , the entire outer peripheral edge of the packing 61 is in contact with the inner peripheral surface of the housing tube 21 . , the passage of the second fluid can be well regulated. In addition, the packing support portion composed of the inner support member 62, the lower support member 63, and the upper support member 64 vertically sandwiches the packing 61 in such a manner that the outer peripheral edge portion of the packing 61 protrudes radially outward, and Since it is joined to the outer surface of the spacer member 50 by welding, the arrangement with respect to the spacer member 50 can be made strong, and the passage of the second fluid can also be well regulated.

Furthermore, according to the heat exchanger 10, the first reinforcing ring 24a and the second reinforcing ring 24b are provided in such a manner that a part of the outer peripheral surface is joined to the inner peripheral surface of each of the upper end portion and the lower end portion of the accommodation tube 21. Therefore, the inflow of the very high-pressure first fluid causes the internal pressure of the distribution channel 221 and the collective channel 231 to become very high, and the first end plate 251 and the second end plate 252 may bend. However, the first reinforcing ring 24a and the second reinforcing ring 24b can suppress deformation of the upper end portion and the lower end portion of the side peripheral portion of the accommodation tube 21 toward the central axis of the accommodation tube 21, The strength of the pressure vessel 20 can be improved without increasing the wall thickness of the housing tube 21 .

Further, according to the heat exchanger 10, the first reinforcing ring 24a and the second reinforcing ring 24b are made of a high-strength material such as stainless steel. Even when the first end plate 251 and the second end plate 252 are joined together, nickel and chromium in the stainless steel inhibit the diffusion of aluminum and iron, suppressing the growth of intermetallic compounds that cause a decrease in strength, thereby increasing the strength. can be improved.

Furthermore, according to the heat exchanger 10, since the first reinforcing mounting tube 41, the second reinforcing mounting tube 42, the third reinforcing mounting tube 43, and the fourth reinforcing mounting tube 44 are provided, the following effects can be obtained. Play.

That is, the first reinforcing mounting cylinder 41 attached to the first introduction port 222 with a part of the lower end portion 41a inserted therein is joined to the outer surface of the pipe HK at the inner surface of the upper end portion 41b by brazing. Therefore, even if the thickness dimension of the first end plate 22 is small, a sufficient joint area with the pipe HK can be secured, and joint strength can be improved. Moreover, the inner diameter of the lower end portion 41a of the first reinforcing mounting tube 41 is smaller than the outer diameter of the pipe HK, and the inner diameter of the upper end portion 41b is adapted to the outer diameter of the pipe HK. The end face of the pipe HK inserted into the pipe 41 can be connected while being in contact with the step 41c, and the pipe HK can be easily aligned.

The second reinforcing mounting cylinder 42 attached with the upper end portion 42a partly inserted into the first discharge port 232 is joined to the outer surface of the pipe HK at the inner surface of the lower end portion 42b by brazing and connected to the pipe HK. Therefore, even if the thickness dimension of the second end plate 23 is small, a sufficient joint area with the pipe HK can be secured, and joint strength can be improved. Moreover, the inner diameter of the upper end portion 42a of the second reinforcing mounting tube 42 is smaller than the outer diameter of the pipe HK, and the inner diameter of the lower end portion 42b is adapted to the outer diameter of the pipe HK. The end face of the pipe HK inserted in 42 can be connected while being in contact with the step 42c, and the pipe HK can be easily aligned.

The third reinforcing mounting cylinder 43 attached to the second inlet 211 with a portion of the rear end portion 43a inserted therein is joined to the outer surface of the pipe HK at the inner surface of the front end portion 43b by brazing. Since it is connected, even if the wall thickness dimension of the accommodation pipe 21 is small, a sufficient joint area with the pipe HK can be ensured, and joint strength can be improved. Moreover, the inner diameter of the rear end portion 43a of the third reinforcing mounting cylinder 43 is smaller than the outer diameter of the pipe HK, and the inner diameter of the front end portion 43b is adapted to the outer diameter of the pipe HK. The end face of the pipe HK inserted into the cylinder 43 can be connected while being in contact with the step 43c, and the pipe HK can be easily aligned.

The fourth reinforcing mounting cylinder 44 attached to the second discharge port 212 with a part of the front end portion 44a inserted therein is joined to the outer surface of the pipe HK at the inner surface of the rear end portion 44b by brazing. Since it is connected, even if the wall thickness dimension of the accommodation pipe 21 is small, a sufficient joint area with the pipe HK can be ensured, and the joint strength can be improved. Moreover, the fourth reinforcing mounting cylinder 44 has a front end portion 44a whose inner diameter is smaller than the outer diameter of the pipe HK, and a rear end portion 44b whose inner diameter matches the outer diameter of the pipe HK. The end face of the pipe HK inserted into the cylinder 44 can be connected while being in contact with the step 44c, and the pipe HK can be easily aligned.

According to the heat exchanger 10, since the plurality of flat perforated tubes 30 are made of aluminum, the cost is relatively low, and the manufacturing cost can be reduced.

Although the preferred embodiment of the present invention has been described above, the present invention is not limited to this, and various modifications can be made.

In the above-described embodiment, the pressure vessel 20 has the first end plate 22 provided above the containing pipe 21 and the second end plate 23 provided below the containing pipe 21. However, in the present invention, The first end plate may be provided on the lower side of the accommodation tube, and the second end plate may be provided on the upper side of the accommodation tube.

In the above-described embodiment, the direction of the center axis of the containing tube 21 of the pressure vessel 20 coincides with the vertical direction. The direction is not particularly limited.

REFERENCE SIGNS LIST 1 Refrigeration cycle device 10 Heat exchanger 20 Pressure vessel 21 Accommodating pipe 211 Second inlet 212 Second discharge port 22 First end plate 222 First inlet 23 2nd end plate 232 1st discharge port 24a 1st reinforcing ring 24b 2nd reinforcing ring 251 1st end plate 252 2nd end plate 26 accommodation area 30 flat perforated tube , 31 ... base portion 31a ... front surface 31b ... back surface 32 ... flow path 321 ... hole 33 ... fin 41 ... first reinforcing mounting tube 42 ... second reinforcing mounting tube 43 ... third reinforcing mounting Cylinder 44 Fourth reinforcing mounting cylinder 50 Spacer member 51 Spacer constituent member 52 Stiffening joint 60 Stopper member 61 Packing 62 Inner support member 63 Lower support member 64...Upper supporting member, GR... Pseudo flow path, HK... Piping, K... Virtual line, S... Gap.

Claims (6)

A heat exchanger for exchanging heat between a first fluid and a second fluid inside a pressure vessel,
The pressure vessel is
A flow path in which a plurality of holes for circulating the first fluid are arranged in parallel, and a plurality of fins extending along the longitudinal direction of the holes on the front surface and the back surface are arranged in parallel in the parallel direction of the holes. a cylindrical storage tube that stores the plurality of flat perforated tubes in such a manner that the extending direction of the holes coincides with the axial direction of the tube;
The plurality of flat perforated tubes are attached in such a manner that one end of the storage tube is closed while the inlets of the flow paths of the plurality of flat perforated tubes are communicated with each other, and the first fluid introduced from the first inlet formed therein is introduced into each of the tubes. a first end plate that flows into the flow path of the flat perforated tube;
The plurality of flat perforated tubes are attached in such a manner that the outlets of the flow paths of the plurality of flat perforated tubes are communicated with each other and the other ends of the storage tubes are closed, and the first fluid flowing out of the flow paths of the flat perforated tubes is supplied to itself. a second end plate for discharging from the formed first discharge port,
The accommodation tube is
a second inlet that is formed at an arbitrary location on the side periphery and that introduces the second fluid into the interior of the containing tube;
a second discharge port that is formed at a portion of the side peripheral portion separated from the second inlet and that discharges the second fluid that has passed through the inside of the containing tube;
While the second fluid is circulated in a pseudo flow path formed by connecting fins adjacent to each other by imaginary lines between flat perforated tubes that are adjacent to each other in such a manner that the front surface and the back surface are opposed to each other, A heat exchanger, wherein the plurality of flat perforated tubes are accommodated in a manner that allows the second fluid to flow between the adjacent pseudo flow paths. The storage tube accommodates the plurality of flat perforated tubes in such a manner that a gap is provided between adjacent fins between adjacent flat perforated tubes in such a manner that the front surface and the back surface are opposed to each other. The heat exchanger according to claim 1, characterized by: The second fluid introduced from the second introduction port is arranged in the interior of the storage pipe so as to surround the storage region that stores the plurality of flat perforated tubes, and the second fluid passes toward the storage region. and a spacer member that allows the second fluid that has passed through the accommodation area to pass toward the second discharge port;
Spacers are provided on the outer surface of the spacer member at predetermined intervals along the axial direction of the storage tube in a manner of protruding toward the inner peripheral surface of the storage tube, and the outer ends of the spacer members are in contact with the inner peripheral surface of the storage tube. 3. The heat exchanger according to claim 1, further comprising a plurality of joint members that restrict the spacer member from approaching the inner peripheral surface when the spacer member is closed. It is attached to the outer surface of the spacer member so as to extend along the circumferential direction, and a part of itself contacts the inner peripheral surface of the storage tube and is elastically deformed, thereby separating the spacer member and the storage tube. a stopper member that restricts passage of the second fluid along the axial direction of the storage tube between the
The stopper member is
an annular packing disposed so as to surround the spacer member;
a packing supporting portion that sandwiches the packing vertically in such a manner that the outer peripheral edge portion of the packing protrudes radially outward, and is joined to the outer surface of the spacer member by welding, wherein the outer peripheral edge portion of the packing is 4. The heat exchanger according to claim 3, wherein the heat exchanger is elastically deformed in contact with the inner peripheral surface of the housing pipe. The heat exchanger according to any one of claims 1 to 4, wherein the plurality of perforated flat tubes have a fine rectangular cross-sectional shape perpendicular to the longitudinal direction of the holes. . The heat exchanger according to any one of claims 1 to 5, wherein the plurality of flat perforated tubes are made of aluminum.

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