JP7501161B2 - Heat exchanger - Google Patents

Description

The present invention relates to a heat exchanger, and more specifically to a heat exchanger that exchanges heat between two fluids.

Conventionally, a heat exchanger that exchanges heat between two fluids is known that is equipped with multiple heat transfer tubes, an inlet header, an outlet header, and a pressure vessel.

The heat transfer tubes are cylindrical and arranged side by side with a gap between them so that their longitudinal directions coincide with each other. The hollow portions of these heat transfer tubes form flow paths. The inlet header connects the flow paths of the heat transfer tubes together and allows the first fluid to flow into the flow paths of each heat transfer tube. The outlet header connects the outlets of the flow paths of the heat transfer tubes together and allows the first fluid to pass through the flow paths of each heat transfer tube. The pressure vessel has a storage chamber that houses the heat transfer tubes, and has an inlet port that allows the second fluid to flow into the storage chamber and an outlet port that allows the second fluid to flow out of the storage chamber.

In such a heat exchanger, heat can be exchanged between a first fluid that flows from the inlet header into each heat transfer tube and passes through the heat transfer tube, and a second fluid that flows from the inlet port into the storage chamber and passes outside the heat transfer tube (see, for example, Patent Document 1).

JP 2002-310577 A

In the above-mentioned heat exchanger, each heat transfer tube is cylindrical and needs to have a gap between them, so in order to improve the heat transfer efficiency, the number of heat transfer tubes housed in the housing chamber must be increased while reducing the diameter of each heat transfer tube. However, there is a limit in terms of dimensional accuracy to increasing the number of heat transfer tubes housed while reducing the diameter and ensuring gaps between the heat transfer tubes, and as a result, it has been difficult to improve the heat transfer efficiency.

In view of the above, the present invention aims to provide a heat exchanger that can improve heat transfer efficiency.

In order to achieve the above object, the heat exchanger according to the present invention is a heat exchanger that exchanges heat between a first fluid and a second fluid inside a pressure vessel, the pressure vessel having a flow path in which a plurality of holes are arranged in parallel for the flow of the first fluid, and a cylindrical housing tube that houses a plurality of flat perforated tubes having a plurality of protrusions arranged on the front and back surfaces in parallel, the protrusions extending along the longitudinal direction of the holes, in a manner in which the extension direction of the holes coincides with the axial direction of the tube, a first end plate that is attached in a manner that connects the inlets of the flow paths of the plurality of flat perforated tubes to each other and closes one end of the housing tube, and that allows the first fluid introduced from a first inlet formed in the first end plate to flow into the flow paths of each flat perforated tube, and a second end plate that connects the outlets of the flow paths of the plurality of flat perforated tubes to each other, The device is characterized by comprising a second end plate attached in a manner that closes the other end of the storage tube and discharges the first fluid flowing out of the flow path of each flat porous tube from a first discharge port formed in the second end plate, a second inlet port formed on the side periphery of the storage tube and introducing the second fluid into the storage tube, a second outlet port formed on the side periphery of the storage tube and discharging the second fluid that has passed through the inside of the storage tube, and a spacer member disposed in a manner that surrounds a storage area that contains the multiple flat porous tubes inside the storage tube, allowing the second fluid introduced from the second inlet port to pass toward the storage area and allowing the second fluid that has passed through the storage area to pass toward the second outlet port.

The present invention is also characterized in that in the above heat exchanger, the spacer member is formed by arranging a plurality of spacer components side by side in the circumferential direction.

The present invention is also characterized in that the heat exchanger includes a stopper member that is attached to the outer peripheral surface of the spacer member in a manner that extends in the circumferential direction, and a part of the stopper member abuts against the inner peripheral surface of the storage tube and elastically deforms to press the spacer member toward the central axis of the storage tube.

The present invention is also characterized in that in the above heat exchanger, the stopper member is formed by arranging a plurality of stopper components in parallel along the circumferential direction, and the stopper components have a base portion attached to the outer circumferential surface of the spacer member, and an enlarged diameter portion that is continuous with the edge of the base portion and gradually extends radially outward as it moves away from the base portion.

The present invention is also characterized in that in the above heat exchanger, the stopper component has an enlarged diameter portion that is continuous with an edge portion of the base that is adjacent to the second inlet.

According to the present invention, the pressure vessel is provided with a cylindrical storage tube having a flow path in which a plurality of holes for passing a first fluid are arranged in parallel, and a plurality of flat perforated tubes having a plurality of protrusions arranged on the front and back surfaces in parallel and extending along the longitudinal direction of the holes, the extension direction of the holes being aligned with the axial direction of the tube itself; a first head plate which is attached in such a manner that it connects the inlets of the flow paths of the plurality of flat perforated tubes to each other while closing one end of the storage tube, and which allows the first fluid introduced through a first inlet formed in the first head plate to flow into the flow paths of the flat perforated tubes; and a first head plate which connects the inlets of the flow paths of the plurality of flat perforated tubes to each other while closing one end of the storage tube, the first head plate being attached in such a manner that it ... The second end plate is attached in a manner that connects the outlets of the flow paths to each other while blocking the other end of the housing tube, and discharges the first fluid flowing out of the flow paths of each flat porous tube from the first discharge port formed in the second end plate, a second inlet port formed on the side periphery of the housing tube for introducing the second fluid into the housing tube, and a second discharge port formed on the side periphery of the housing tube for discharging the second fluid that has passed through the inside of the housing tube. This has the effect of expanding the heat transfer area by the flat porous tubes and improving the heat transfer efficiency. Moreover, the spacer member arranged in a manner surrounding the storage area that stores the flat porous tubes inside the housing tube allows the second fluid introduced from the second inlet port to pass toward the storage area, and allows the second fluid that has passed through the storage area to pass toward the second discharge port, so that the second fluid introduced from the second inlet port can be reliably passed through the storage area, which also has the effect of improving the heat transfer efficiency.

FIG. 1 is a schematic diagram showing an overall configuration of a refrigeration cycle device to which a heat exchanger according to an embodiment of the present invention is applied. FIG. 2 is a front view of a heat exchanger according to an embodiment of the present invention. FIG. 3 is an exploded perspective view of a heat exchanger according to an embodiment of the present invention. FIG. 4 is an exploded perspective view of a heat exchanger according to an embodiment of the present invention. FIG. 5 is a cross-sectional view showing the internal structure of a heat exchanger according to an embodiment of the present invention. FIG. 6 is a cross-sectional view showing the internal structure of a heat exchanger according to an embodiment of the present invention. FIG. 7 is an enlarged cross-sectional view showing a main part of the internal structure of a heat exchanger according to an embodiment of the present invention. FIG. 8 is an enlarged cross-sectional view showing a main part of the internal structure of a heat exchanger according to an embodiment of the present invention. FIG. 9 is a perspective view showing the flat perforated pipe shown in FIGS. FIG. 10 is a cross-sectional view showing a transverse section of the flat perforated pipe shown in FIGS. FIG. 11 is an enlarged cross-sectional view showing a main part of the internal structure of a heat exchanger according to an embodiment of the present invention. FIG. 12 is an enlarged cross-sectional view showing a main part of the internal structure of a heat exchanger according to an embodiment of the present invention. FIG. 13 is an enlarged cross-sectional view showing a main part of the internal structure of a heat exchanger according to an embodiment of the present invention. FIG. 14 is an enlarged cross-sectional view showing a main part of the internal structure of a heat exchanger according to an embodiment of the present invention. FIG. 15 is a perspective view showing the flat porous tube housed inside the housing tube shown in FIGS. 2 to 8, and the spacer member and stopper member which are the peripheral structure thereof. FIG. 16 is a perspective view showing the flat porous tube housed inside the housing tube shown in FIGS. 2 to 8, and the spacer member and stopper member which are the peripheral structure thereof. 17 is an exploded perspective view of the flat porous pipe, the spacer member, and the stopper member shown in FIGS. 15 and 16. FIG. 18 is an exploded perspective view of the flat porous pipe, the spacer member, and the stopper member shown in FIGS. 15 and 16. FIG. FIG. 19 is a cross-sectional view of the stopper member shown in FIGS. FIG. 20 is an enlarged view of the stopper component shown in FIGS. FIG. 21 is an enlarged cross-sectional view showing a main part of the internal structure of a heat exchanger according to an embodiment of the present invention. FIG. 22 is a cross-sectional view showing the internal structure of a heat exchanger according to an embodiment of the present invention.

The following describes in detail a preferred embodiment of the heat exchanger according to the present invention with reference to the attached drawings.

Figure 1 is a schematic diagram showing the overall configuration of a refrigeration cycle device to which a heat exchanger according to an embodiment of the present invention is applied. The refrigeration cycle device 1 shown here is a two-way refrigeration cycle that has a first refrigeration cycle 1a in which a first fluid circulates and a second refrigeration cycle 1b in which a second fluid circulates, and is configured to exchange heat between the first fluid, which is one refrigerant, and the second fluid, which is the other refrigerant, in a heat exchanger 10.

This refrigeration cycle device 1 can use the cold generated, for example, in the first evaporator 5 of the first refrigeration cycle 1a for various refrigeration equipment such as air conditioners and showcases.

The first refrigeration cycle 1a is configured by connecting a first compressor 2, a first condenser 3, a heat exchanger 10, a first expansion mechanism 4, and a first evaporator 5 in sequence with piping HK. The second refrigeration cycle 1b is configured by connecting a second compressor 6, a second condenser 7, a second expansion mechanism 8, and a heat exchanger 10 in sequence with piping HK.

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

The first fluid, which is a refrigerant circulating through the first refrigeration cycle 1a, and the second fluid, which is a refrigerant circulating through the second refrigeration cycle 1b, are, for example, natural refrigerants or alternative fluorocarbon refrigerants. In this embodiment, the second fluid is at a higher pressure than atmospheric pressure when it flows into the heat exchanger 10, and the first fluid flows into the heat exchanger 10 at a normal pressure higher than that of the second fluid.

Figures 2 to 6 each show a heat exchanger 10 according to an embodiment of the present invention, with Figure 2 being a front view, Figures 3 and 4 being exploded perspective views, and Figures 5 and 6 being cross-sectional views showing the internal structure. As shown in Figures 2 to 6, the heat exchanger 10 has a pressure vessel 20, which is configured with a housing tube 21, a first end plate 22, and a second end plate 23.

The housing tube 21 is formed, for example, from steel material and has a cylindrical shape. The axial direction of the housing tube 21 coincides with the vertical direction. The housing tube 21 is provided with a first reinforcing ring (reinforcing ring member) 24a and a second reinforcing ring (reinforcing ring member) 24b.

As shown in FIG. 7, the first reinforcing ring 24a is made of a high-strength material such as stainless steel and has a circular ring shape. The outer diameter of the first reinforcing ring 24a is a size that fits the inner diameter of the storage tube 21, and it is attached by joining a part of its outer peripheral surface to the inner peripheral surface of the upper end of the storage tube 21 by welding or the like. More specifically, the first reinforcing ring 24a is attached in a manner that protrudes upward from the upper end opening of the storage tube 21.

A disk-shaped first end plate 251 is joined by welding or the like in such a manner as to close the upper opening of the first reinforcing ring 24a. This first end plate 251 is formed of a metal material such as aluminum.

As shown in FIG. 8, the second reinforcing ring 24b is formed of a high-strength material such as stainless steel and has a circular ring shape. The outer diameter of the second reinforcing ring 24b is a size that fits the inner diameter of the storage tube 21, and is attached by joining a portion of the outer circumferential surface to the inner circumferential surface of the lower end of the storage tube 21 by welding or the like. More specifically, the second reinforcing ring 24b is attached in a manner that protrudes downward from the lower end opening of the storage tube 21.

A disk-shaped second end plate 252 is joined by welding or the like in such a manner as to close the bottom opening of the second reinforcing ring 24b. This second end plate 252, like the first end plate 251, is formed of a metal material such as aluminum.

The first reinforcing ring 24a and the second reinforcing ring 24b are formed with a thickness dimension (radial thickness dimension) larger than the thickness dimension of the housing tube 21, and have a sufficiently large strength. Furthermore, the vertical dimensions of the first reinforcing ring 24a and the second reinforcing ring 24b are adjusted to a magnitude that causes a temperature rise without melting the first end plate 251 and the second end plate 252 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 first end plate 251 and the second end plate 252 form a pair, one above the other, and have corresponding through holes 251a, 252a formed therein. A plurality of flat perforated pipes 30 are accommodated in the accommodation area 26 between the first end plate 251 and the second end plate 252, passing through the through holes 251a, 252a.

As shown in Figures 9 and 10, the flat porous pipe 30 is made of a metal material such as aluminum, and is configured with a base portion 31, a flow path 32, and multiple protrusions 33.

The base 31 is a flat, long, strip-shaped plate-like member. The flow path 32 has a plurality of holes 321 formed through the base 31 in the longitudinal direction, and is configured by arranging a plurality of these holes 321 in parallel in the width direction. Each hole 321 constituting the flow path 32 is a path having a minute rectangular cross section perpendicular to the longitudinal direction, and is a minute path known as a mini-channel or micro-channel. A plurality of protrusions 33 are formed on the front surface 31a and back surface 31b of the base 31 except for the upper end portion 31c and the lower end portion 31d. These protrusions 33 are elongated and extend along the longitudinal direction of the holes 321, and are arranged in parallel along the width direction.

The flat porous tubes 30 having such a configuration are accommodated in the accommodation area 26 with their longitudinal direction (the longitudinal direction of the holes 321) aligned with the axial direction of the accommodation tube 21. In more detail, the flat porous tubes 30 are accommodated in the accommodation tube 21 while being slightly spaced apart from one another with their width direction (the parallel direction of the holes 321) coinciding with the front-rear direction. These flat porous tubes 30 are supported with the upper end portion 31c of the base portion 31 penetrating the corresponding through hole 251a of the first end plate 251, and the lower end portion 31d of the base portion 31 penetrating the corresponding through hole 252a of the second end plate 252.

The first end plate 22 is hemispherical and made of, for example, steel, and is attached in a manner that closes the upper end of the storage tube 21. Between the first end plate 22 and the storage tube 21, a distribution flow path 221 is formed that faces the upper end openings of the holes 321 of the multiple flat porous tubes 30, and a first inlet 222 is formed at the top.

As shown in FIG. 11, the first inlet 222 is provided with a first reinforcing mounting tube (reinforcing mounting member) 41. The first reinforcing mounting tube 41 is formed, for example, from a steel material or the like, in a substantially cylindrical shape, and is attached with a part of the lower end 41a inserted through the first inlet 222 from above. In other words, the first reinforcing mounting tube 41 is attached with the remaining part of the lower end 41a and the upper end 41b protruding upward from the first inlet 222 (outside the storage tube 21).

The inner diameter of the upper end 41b of this first reinforcing mounting tube 41 matches the outer diameter of the pipe HK to be connected, i.e., the pipe HK connected to the outlet side of the first condenser 3 of the first refrigeration cycle 1a, and the inner diameter of the lower end 41a is smaller than the outer diameter of the pipe HK.

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

As a result, the distribution flow path 221 distributes the first fluid introduced from the first inlet 222 to each hole 321. In other words, the first end plate 22 connects the inlets of the flow paths 32 of the multiple flat porous pipes 30 with each other via the distribution flow path 221, and allows the first fluid to flow into the flow paths 32 of each flat porous pipe 30.

The second end plate 23 is hemispherical and made of, for example, steel, and is attached in such a manner as to close the lower end of the storage tube 21. Between the second end plate 23 and the storage tube 21, a collecting flow path 231 is formed to which the lower end openings of the holes 321 of the multiple flat porous tubes 30 face, and a first discharge port 232 is formed at the top.

As shown in FIG. 12, the first discharge port 232 is provided with a second reinforcing mounting tube (reinforcing mounting member) 42. The second reinforcing mounting tube 42 is formed, for example, from a steel material or the like, in a substantially cylindrical shape, and is attached with a part of the upper end 42a inserted through the first discharge port 232 from below. In other words, the second reinforcing mounting tube 42 is attached with the remaining part of the upper end 42a and the lower end 42b protruding downward (outside the storage tube 21) from the first discharge port 232.

The inner diameter of the lower end 42b of this second reinforcing mounting tube 42 matches the outer diameter of the pipe HK to be connected, i.e., the pipe HK connected to the inlet side of the first expansion mechanism 4 of the first refrigeration cycle 1a, and the inner diameter of the upper end 42a is smaller than the outer diameter of the pipe HK.

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

As a result, the collecting passage 231 collects the first fluid that has passed through each hole 321 and passes it through the pipe HK connected to the inlet side of the first expansion mechanism 4 of the first refrigeration cycle 1a. In other words, the second end plate 23 connects the outlets of the passages 32 of the multiple flat porous pipes 30 to each other, and discharges the first fluid that has flowed out of the passages 32 of each flat porous pipe 30 from the first discharge port 232.

Meanwhile, a second inlet 211 and a second outlet 212 are formed on the circumferential side of the housing tube 21. The second inlet 211 is formed on the left part of the lower end side of the housing tube 21. As shown in FIG. 13, a third reinforcing mounting tube (reinforcing mounting member) 43 is provided on this second inlet 211.

The third reinforcing mounting cylinder 43 is formed, for example, from a steel material or the like, in a generally cylindrical shape, and is attached with a portion of the right end 43a inserted through the second inlet 211 from the left. In other words, the third reinforcing mounting cylinder 43 is attached with the remaining portion of the right end 43a and the left end 43b protruding from the second inlet 211 toward the left (outside the storage tube 21).

The inner diameter of the left end 43b of this third reinforcing mounting tube 43 matches the outer diameter of the pipe HK to be connected, i.e., the pipe HK connected to the outlet side of the second expansion mechanism 8 of the second refrigeration cycle 1b, and the inner diameter of the right end 43a is smaller than the outer diameter of the pipe HK.

As a result, a step 43c is formed inside the third reinforcing mounting tube 43 at the boundary between the left end 43b and the right end 43a, and the end face of the pipe HK inserted into the third reinforcing mounting tube 43 abuts against the step 43c, and the outer surface is joined to the inner surface of the left end 43b by brazing or the like. Therefore, the second inlet 211 introduces the second fluid into the inside of the storage tube 21.

The second discharge port 212 is formed in the upper right portion of the storage tube 21. As shown in FIG. 14, the second discharge port 212 is provided with a fourth reinforcing mounting tube (reinforcing mounting member) 44.

The fourth reinforcing mounting cylinder 44 is formed, for example, from a steel material or the like, in a generally cylindrical shape, and is attached with a portion of the left end 44a inserted into the second discharge port 212 from the right. In other words, the fourth reinforcing mounting cylinder 44 is attached with the remaining portion of the left end 44a and the right end 44b protruding from the second discharge port 212 to the right (outside the storage tube 21).

The inner diameter of the right end 44b of this fourth reinforcing mounting tube 44 matches the outer diameter of the pipe HK to be connected, i.e., the pipe HK connected to the inlet side of the second compressor 6 of the second refrigeration cycle 1b, and the inner diameter of the left end 44a is smaller than the outer diameter of the pipe HK.

As a result, a step 44c is formed inside the fourth reinforcing mounting cylinder 44 at the boundary between the left end 44a and the right end 44b, and the end face of the pipe HK inserted into the fourth reinforcing mounting cylinder 44 abuts against the step 44c, and the outer surface is joined to the inner surface of the right end 44b by brazing or the like. Therefore, the second discharge port 212 discharges the second fluid that has passed through the inside of the container tube 21.

In addition, a spacer member 50 and a stopper member 60 are provided inside the housing tube 21, as shown in Figures 15 and 16.

The spacer member 50 is provided in such a manner that it surrounds the storage area 26 that stores the multiple flat porous pipes 30. As shown in Figures 17 and 18, the spacer member 50 is configured with multiple spacer components 51 (two in the illustrated example).

The two spacer components 51 are of the same shape and are semi-cylindrical. The inner surfaces of these spacer components 51 define the storage area 26, and recesses 51a are formed to match the shape of the storage area 26. The spacer component 51 on the right side is upside down compared to the spacer component 51 on the left side. In other words, the opening on the top surface of the left spacer component 51 is closed, and a notch 51b that continues to the opening on the bottom surface is formed on the outer circumferential surface, while the opening on the bottom surface of the right spacer component 51 is closed, and a notch 51b that continues to the opening on the top surface is formed on the outer circumferential surface.

The stopper member 60 is made of a resin material such as polyoxymethylene, and is annular and disposed circumferentially on the outer circumferential surface of the spacer member 50 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. The stopper member 60 is configured with a plurality of stopper components 61 (two in the illustrated example).

The two stopper components 61 have the same shape and are semicircular. Of these two stopper components 61, the left stopper component 61 is disposed on the outer peripheral surface of the left spacer component 51, and the right stopper component 61 is disposed on the outer peripheral surface of the right spacer component 51.

Such a stopper component 61 is formed by integrally molding a base 611 and an enlarged diameter portion 612. As shown in FIG. 19, when the base 611 and the other stopper component 61 form a circular stopper member 60, the base 611 is an arc-shaped portion whose inner diameter is slightly larger than the outer diameter of the spacer member 50. The base 611 is attached to the outer circumferential surface of the spacer component 51 (spacer member 50) by fastening it via a fastening member such as a spring pin.

The enlarged diameter portion 612 is continuous with the lower end edge of the base 611, i.e., the end edge of the base 611 that is close to the second inlet 211, and gradually extends radially outward as it heads downward (as it moves away from the base 611). The lower end edge 612a, which is the extending end of the enlarged diameter portion 612, is curved as shown in FIG. 20.

As shown in FIG. 19, when the enlarged diameter portion 612 is used together with the other stopper component 61 to form a circular stopper member 60, its maximum outer diameter is slightly larger than the inner diameter of the housing tube 21.

Therefore, when the stopper member 60 is accommodated inside the accommodation tube 21 together with the spacer member 50, as shown in FIG. 21, the lower edge 612a of the enlarged diameter portion 612, which constitutes the maximum outer diameter, abuts against the inner peripheral surface of the accommodation tube 21 and elastically deforms, thereby pressing the spacer member 50 toward the central axis of the accommodation tube 21 by its own elastic restoring force. Also, as shown in FIG. 5 etc., the spacer member 50 is accommodated in the accommodation tube 21 in such a manner that the notch 51b of the left spacer component 51 faces the second inlet 211, and the notch 51b of the right spacer component 51 faces the second outlet 212.

In the heat exchanger 10 having the above configuration, as shown in FIG. 22, the first fluid introduced from the outside is introduced into the distribution flow path 221 from the first inlet 222, passes through the distribution flow path 221, and flows into the flow path 32 of each flat porous pipe 30. The first fluid thus flowing into the flow path 32 of each flat porous pipe 30 flows from top to bottom through the flow path 32, passes through the collecting flow path 231, and is discharged to the outside from the second discharge port 212.

Meanwhile, the second fluid (liquid) introduced from the second inlet 211 enters the interior of the left spacer component 51 through the notch 51b formed in the left spacer component 51 and passes downward through the interior. Since the opening on the underside of the left spacer component 51 is open, the second fluid flows from this opening into the storage area 26. However, since the opening on the underside of the right spacer component 51 is closed, the second fluid that flows into the storage area 26 from the opening on the underside of the left spacer component 51 does not enter the interior of the right spacer component 51.

The second fluid that flows into the storage area 26 passes upward between the adjacent flat porous pipes 30 and between the flat porous pipes 30 and the spacer member 50, and heat is exchanged between the first fluid passing through the flow paths 32 of each flat porous pipe 30 and the second fluid passing outside each flat porous pipe 30, causing the first fluid to condense and the second fluid to evaporate into gas. The second fluid that then passes through the storage area 26 enters the interior of the right spacer component 51, whose top opening is not blocked, and is discharged to the outside from the second discharge port 212 through the notch 51b.

According to the heat exchanger 10 of the embodiment of the present invention, the flat porous tubes 30 housed in the housing tube 21 of the pressure vessel 20 have a flow path 32 in which a plurality of holes 321 for passing the first fluid are arranged in parallel, and a plurality of protrusions 33 extending along the longitudinal direction of the holes 321 are arranged in parallel on the front surface 31a and the back surface 31b, so that the heat transfer area can be enlarged and the heat transfer efficiency can be improved. Since the heat transfer efficiency can be improved in this way, if the same amount of heat exchange as in the past is ensured, the heat exchanger 10 itself can be made smaller. In particular, the flat porous tubes 30 have a fine rectangular cross-sectional shape perpendicular to the longitudinal direction of the holes 321, so that the first fluid passing through each hole 321 gathers at the corners of the holes 321 due to surface tension, making it easier to expose the central areas of each side portion, and promoting heat exchange between the first fluid and the second fluid.

In addition, 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 portion of the outer circumferential surface is joined to the inner circumferential surface of the upper end 42a and the lower end 42b of the storage tube 21, respectively. Therefore, when a very high-pressure first fluid flows in, the internal pressure of the distribution flow path 221 and the collecting flow path 231 becomes very high, and there is a risk that the first end plate 251 and the second end plate 252 will bend. However, the first reinforcing ring 24a and the second reinforcing ring 24b can suppress the upper and lower end portions of the side circumferential portion of the storage tube 21 from deforming toward the central axis of the storage tube 21, and the strength of the pressure vessel 20 can be improved without increasing the wall thickness of the storage tube 21, etc.

In addition, according to the heat exchanger 10, the first reinforcing ring 24a and the second reinforcing ring 24b are formed of a high-strength material such as stainless steel. Even when joined to the first end plate 251 and the second end plate 252 made of aluminum that function as headers for the multiple flat porous tubes 30, the 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 improving strength.

In addition, the heat exchanger 10 has the first reinforcing mounting cylinder 41, the second reinforcing mounting cylinder 42, the third reinforcing mounting cylinder 43, and the fourth reinforcing mounting cylinder 44, and therefore has the following effects:

That is, the first reinforcing mounting tube 41, which is attached with a part of the lower end 41a inserted into the first inlet 222, is connected to the pipe HK by brazing the inner surface of the upper end 41b to the outer surface of the pipe HK, so that 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 the joint strength can be improved. Moreover, the inner diameter of the lower end 41a of the first reinforcing mounting tube 41 is configured to be smaller than the outer diameter of the pipe HK, and the inner diameter of the upper end 41b matches the outer diameter of the pipe HK, so that the end face of the pipe HK inserted into the first reinforcing mounting tube 41 can be connected in a state of abutting against the step 41c, and the pipe HK can be easily aligned.

The second reinforcing mounting tube 42, which is attached with a part of its upper end 42a inserted into the first discharge port 232, is connected to the pipe HK by brazing the inner surface of the lower end 42b to the outer surface of the pipe HK, so that even if the thickness dimension of the second mirror plate 23 is small, a sufficient joint area with the pipe HK can be secured, and the joint strength can be improved. Moreover, the inner diameter of the upper end 42a of the second reinforcing mounting tube 42 is configured to be smaller than the outer diameter of the pipe HK, and the inner diameter of the lower end 42b matches the outer diameter of the pipe HK, so that the end face of the pipe HK inserted into the second reinforcing mounting tube 42 can be connected in abutment with the step 42c, and the pipe HK can be easily aligned.

The third reinforcing mounting tube 43, which is attached with a part of its right end 43a inserted into the second inlet 211, is connected to the pipe HK by brazing the inner surface of the left end 43b to the outer surface of the pipe HK, so that even if the wall thickness dimension of the storage pipe 21 is small, a sufficient joint area with the pipe HK can be secured, and the joint strength can be improved. Moreover, the third reinforcing mounting tube 43 is configured so that the inner diameter of the right end 43a is smaller than the outer diameter of the pipe HK, and the inner diameter of the left end 43b matches the outer diameter of the pipe HK, so that the end face of the pipe HK inserted into the third reinforcing mounting tube 43 can be connected in abutment with the step 43c, and the pipe HK can be easily aligned.

The fourth reinforcing mounting tube 44, which is attached with a portion of the left end 44a inserted into the second discharge port 212, is connected to the pipe HK by brazing the inner surface of the right end 44b to the outer surface of the pipe HK, so that even if the wall thickness dimension of the storage tube 21 is small, a sufficient joint area with the pipe HK can be secured, and the joint strength can be improved. Moreover, the inner diameter of the left end 44a of the fourth reinforcing mounting tube 44 is smaller than the outer diameter of the pipe HK, and the inner diameter of the right end 44b matches the outer diameter of the pipe HK, so that the end face of the pipe HK inserted into the fourth reinforcing mounting tube 44 can be connected in abutment with the step 44c, and the pipe HK can be easily aligned.

In addition, according to the heat exchanger 10, the spacer member 50 arranged inside the storage tube 21 in a manner surrounding the storage area 26 that contains the multiple flat porous tubes 30 allows the second fluid introduced from the second inlet 211 to pass toward the storage area 26 and allows the second fluid that has passed through the storage area 26 to pass toward the second outlet 212, so that the second fluid introduced from the second inlet 211 can be reliably passed through the storage area 26, which also improves the heat transfer efficiency.

In addition, according to the heat exchanger 10, the stopper member 60 attached to the outer peripheral surface of the spacer member 50 in a manner extending in the circumferential direction presses the spacer member 50 toward the central axis of the storage tube 21 by elastically deforming when a portion (the lower edge 612a of the enlarged diameter portion 612) abuts against the inner peripheral surface of the storage tube 21, so that the spacer member 50 can be well aligned and the second fluid can be prevented from passing between the spacer member 50 and the inner peripheral surface of the storage tube 21. Moreover, since the lower edge 612a of the enlarged diameter portion 612 is curved, stress concentration on the lower edge 612a can be suppressed.

The heat exchanger 10 has multiple flat perforated tubes 30 made of aluminum, which is relatively inexpensive and helps reduce manufacturing costs.

The above describes a preferred embodiment of the present invention, but 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 head plate 22 provided above the storage tube 21 and the second head plate 23 provided below the storage tube 21, but in the present invention, the first head plate may be provided below the storage tube and the second head plate may be provided above the storage tube.

In the above-described embodiment, the central axis of the storage tube 21 of the pressure vessel 20 coincides with the vertical direction, but in the present invention, the central axis of the storage tube may coincide with the front-back direction or the left-right direction, and the direction is not particularly limited.

In the above-described embodiment, reinforcing mounting members (first reinforcing mounting tube 41, second reinforcing mounting tube 42, third reinforcing mounting tube 43, and fourth reinforcing mounting tube 44) were attached to the first inlet 222, first outlet 232, second inlet 211, and second outlet 212, but in the present invention, it is sufficient that a reinforcing mounting member is attached to at least one of the first inlet, first outlet, second inlet, and second outlet.

In the above-described embodiment, the third reinforcing mounting tube 43 attached to the second inlet 211 is configured such that the inner diameter of the right end 44b is smaller than the outer diameter of the pipe HK, but in the present invention, the inner diameter of the right end may be smaller than the inner diameter of the pipe. In this case, the orifice effect can change the state of the second fluid, which is a liquid, into a mist and cause it to flow into the storage area, improving the heat exchange efficiency.

In the above-described embodiment, the spacer member 50 is composed of two spacer components 51, but in the present invention, the spacer member may be composed of three or more spacer components arranged side by side in the circumferential direction.

In the above-described embodiment, the stopper member 60 is composed of two stopper component members 61, but in the present invention, the stopper member may be composed of three or more stopper component members arranged side by side in the circumferential direction, or may be composed of a single annular stopper component member.

1...refrigeration cycle device, 1a...first refrigeration cycle, 1b...second refrigeration cycle, 10...heat exchanger, 20...pressure vessel, 21...accommodating pipe, 211...second inlet, 212...second outlet, 22...first end plate, 222...first inlet, 23...second end plate, 232...first outlet, 24a...first reinforcing ring, 24b...second reinforcing ring, 251...first end plate, 252...second End plate, 26...accommodation area, 30...flat porous pipe, 31...base portion, 31a...surface, 31b...back surface, 32...flow path, 321...hole portion, 33...projection, 41...first reinforcing mounting tube, 42...second reinforcing mounting tube, 43...third reinforcing mounting tube, 44...fourth reinforcing mounting tube, 50...spacer member, 51...spacer component member, 60...stopper member, 61...stopper component member, HK...piping.

Claims (4)

A heat exchanger for exchanging heat between a first fluid and a second fluid inside a pressure vessel,
The pressure vessel comprises:
a cylindrical accommodation tube that accommodates a plurality of flat perforated tubes having a flow path in which a plurality of holes for passing the first fluid are arranged in parallel, and having a plurality of protrusions arranged in parallel on a front surface and a back surface thereof, the protrusions extending along the longitudinal direction of the holes, in a manner in which the extension direction of the holes coincides with the axial direction of the accommodation tube;
a first end plate that is attached in a manner that connects the inlets of the flow paths of the plurality of flat perforated tubes to each other and closes one end of the housing tube, and that allows the first fluid introduced through a first inlet formed in the first end plate to flow into the flow paths of each flat perforated tube;
a second end plate that is attached in a manner that closes the other end of the accommodation pipe while connecting the outlets of the flow paths of the plurality of flat perforated pipes to each other, and that discharges the first fluid flowing out of the flow paths of each of the flat perforated pipes from a first discharge port formed in the second end plate;
a second inlet formed on a side peripheral portion of the containing tube for introducing the second fluid into the inside of the containing tube;
a second outlet port formed on a side peripheral portion of the housing tube for discharging the second fluid that has passed through the inside of the housing tube;
a spacer member disposed inside the accommodating tube in a manner surrounding a accommodating area that accommodates the plurality of flat porous tubes, the spacer member allowing the second fluid introduced from the second inlet to pass toward the accommodating area and allowing the second fluid having passed through the accommodating area to pass toward the second outlet ;
a stopper member attached to the outer peripheral surface of the spacer member in a manner extending in a circumferential direction, the stopper member having a part thereof abutting against the inner peripheral surface of the housing tube and elastically deforming to press the spacer member toward the central axis of the housing tube;
A heat exchanger comprising : The heat exchanger according to claim 1, characterized in that the spacer member is formed by arranging a plurality of spacer components in parallel along the circumferential direction. The stopper member is configured by arranging a plurality of stopper constituent members in parallel along a circumferential direction,
The stopper component is
a base portion attached to an outer peripheral surface of the spacer member;
3. The heat exchanger according to claim 1, further comprising: an expanded diameter portion that is continuous with an edge portion of the base portion and that gradually extends radially outward as it moves away from the base portion. 4. The heat exchanger according to claim 3 , wherein the stopper component member has an enlarged diameter portion that is continuous with an end edge portion of the base portion that is adjacent to the second inlet port.

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