JP4905266B2 - Heat exchanger, refrigeration cycle apparatus and water heater - Google Patents

Description

  The present invention relates to a heat exchanger, a refrigeration cycle apparatus including the heat exchanger, and a water heater.

  Conventionally, as shown in FIGS. 10 to 12, a heat exchanger is known in which a meandering path is formed inside a box and a heat transfer tube is wound around the outside of the box (for example, (See Patent Documents 1 and 2). FIG. 10 is an exploded perspective view showing a heat exchanger according to the prior art. FIG. 11 is a plan view of the heat exchanger shown in FIG. FIG. 12 is a diagram illustrating a meandering channel formed inside the heat exchanger.

  As shown in FIG. 10, the heat exchanger 200 includes a thin rectangular parallelepiped box 220. The box body 220 includes two plates 221 and 222 formed by drawing. Moreover, the heat exchanger 200 includes a corrugated corrugated plate 240 having openings 243 formed at left and right alternating side end positions. The corrugated plate 240 is housed in the box 220 with the upper and lower folded surfaces 241 joined to the plates 221 and 222, respectively. Thereby, the meandering flow path 230 is formed inside the box 220 (see FIG. 12).

As shown in FIG. 11, the heat exchanger 200 includes a heat transfer tube 250 spirally wound around the outer surface of the box 220 along the meandering flow path 230 (see FIG. 12). According to this heat exchanger 200, it is possible to reduce the size by using the flow path inside the box 220 as a meandering path.
JP 2003-314975 A JP 2004-205060 A

  However, the heat exchanger 200 described above has problems as described below. That is, by winding the heat transfer tube 250 around the box 220 in a spiral shape, the heat transfer tube 250 is placed above and below (the front side and the back side in FIG. 12) the flow path part 233 (see FIG. 12) extending in the left-right direction in the meandering flow path 230. Will be placed. That is, as shown in FIG. 11, the heat transfer tube 250 includes an upper surface portion 250 a (solid line portion) extending in the left-right direction on the upper surface of the box body 220 and a lower surface portion 250 b (broken line portion) extending in the left-right direction on the lower surface of the box body 220. And. Of these two parts (the upper surface part 250a and the lower surface part 250b), the fluid flowing through one of them is opposed to the fluid flowing through the channel part 233 (see FIG. 12), but the fluid flowing through the other is the channel. It becomes a parallel flow with the fluid flowing through the portion 233. However, if the two fluids that undergo heat exchange are in parallel flow, the efficiency of heat exchange will be reduced. Therefore, the heat exchangers described in Patent Documents 1 and 2 described above have room for improvement in heat exchange performance.

  Here, it is possible to make the fluid in the meandering flow path and the fluid in the heat transfer tube all counter flow by diverting the fluid in the heat transfer tube. That is, one heat transfer tube is branched into two, and one of the branched heat transfer tubes is disposed on the upper surface of the box along the meandering flow path, and the other heat transfer tube is disposed along the meandering flow path. By disposing on the lower surface, the fluid in the meandering channel and the fluid in the heat transfer tube can all be counterflowed. However, when the fluid in the heat transfer tubes is divided, it is difficult to equalize the pressure loss in both heat transfer tubes. As a result, the heat exchange performance may be reduced. In addition, a shunt is required separately, which increases the number of parts.

  The present invention has been made in view of the above points, and provides a heat exchanger that can substantially improve the heat exchange performance by making the two fluids that exchange heat substantially counterflow without using a flow divider. The purpose is to provide.

  In the heat exchanger according to the present invention, an introduction port for introducing the first fluid and an outlet port for extracting the first fluid are formed, and the first heat transfer plate and the opposite side of the first heat transfer plate. And a space between the inner surface of the first heat transfer plate and the inner surface of the second heat transfer plate inside the box. A plurality of first partition plates each having a plurality of regions extending in a predetermined direction and arranged in a direction intersecting the predetermined direction and forming a meandering flow path from the inlet to the outlet, It is provided in at least one of the plurality of regions, and the region is partitioned into a first flow path portion on the first heat transfer plate side and a second flow path portion on the second heat transfer plate side. A second partition plate that forms a reciprocating path composed of the first flow path portion and the second flow path portion in the region, A heat transfer tube for guiding a second fluid that exchanges heat with the first fluid, the heat transfer tube being in contact with an outer surface of the first heat transfer plate in the first flow path section and along the first flow path section. A first heat transfer tube component extending; and a second heat transfer tube component contacting the outer surface of the second heat transfer plate in the second flow channel and extending along the second flow channel. And a heat transfer tube wound around the box so that the flow direction of the first heat transfer tube component and the flow direction of the second heat transfer tube component are opposed to each other.

  In the heat exchanger, the first channel portion and the second channel portion are formed in the plurality of regions, respectively, and are arranged in a direction intersecting the predetermined direction. The first channel portion of the first region and the first channel portion of the second region communicate with each other, and the second channel portion of the second region and the third channel portion The area | region 2nd flow-path part may be connected.

  In the heat exchanger, the second partition plate may be provided in each of the plurality of regions.

  Further, in the heat exchanger, the first and second heat transfer plates are formed by first and second dish-like bodies with rising peripheral edges, and the box body is the first dish-like body. And the second dish-shaped body may be formed by joining the peripheral edges of the first and second dish-shaped bodies with the first partition plate sandwiched between them.

  In the heat exchanger, fins are provided on the inner side of the first heat transfer plate, the inner side of the second heat transfer plate, the first partition plate, or the second partition plate. Also good.

  In the heat exchanger, the fin may be provided with a turbulence promoting portion that disturbs the flow of the first fluid.

  Moreover, the said heat exchanger WHEREIN: The hole may be formed in the said fin.

  Further, in the heat exchanger, the plurality of regions include an inlet side region facing the inlet and an outlet side region facing the outlet, and the flow path cross-sectional area of the outlet side region is the inlet side It may be larger than the channel cross-sectional area of the region.

  Further, in the heat exchanger, the plurality of first partition plates are arranged in parallel to each other and have an outlet side flow path width that is a length along the arrangement direction of the first partition plates in the outlet side region. May be wider than the inlet-side channel width which is the length along the arrangement direction of the first partition plate in the inlet-side region.

  In the heat exchanger, the plurality of first partition plates are arranged in parallel to each other, each of the first partition plates is provided with one or more fins, and the number of fins in the outlet side region May be larger than the number of fins in the inlet side region.

  Further, the first fluid may be water heated by the second fluid.

  Further, the second fluid may be carbon dioxide.

  Another heat exchanger according to the present invention includes a box body in which a first fluid flows, and a heat transfer tube wound around the outside of the box body and in which a second fluid flows. A heat exchanger for exchanging heat between the second fluid and the second fluid, the meandering flow having a plurality of regions extending in a predetermined direction and arranged in a direction intersecting the predetermined direction inside the box A path is formed, and the heat transfer tube is arranged along the longitudinal direction of each region on both the front side and the back side of the box, and in each region, the first fluid flowing through the box is placed. A reciprocating path composed of front and back flow paths is formed so that the flow direction and the flow direction of the second fluid flowing in the heat transfer tube are opposed to each other.

  The heat exchanger, a compressor that compresses the refrigerant, a first pipe that guides the refrigerant compressed by the compressor to the heat transfer pipe as the second fluid, and a refrigerant that has flowed through the heat transfer pipe A second pipe for guiding, a pressure reducing mechanism for depressurizing the refrigerant flowing through the second pipe, a third pipe for guiding the refrigerant depressurized by the pressure reducing mechanism, and evaporating the refrigerant flowing through the third pipe A refrigeration cycle apparatus including an evaporator and a fourth pipe that guides the refrigerant evaporated in the evaporator to the compressor is also included in the present invention.

  Further, the present invention includes a water heater that includes the refrigeration cycle apparatus, wherein the first fluid is water, and generates hot water in the heat exchanger.

  According to the present invention, in a heat exchanger in which a heat transfer tube is wound around the outside of a box, the heat exchange fluids are substantially counterflowed without using a flow divider, and heat exchange performance is improved. Is possible.

<First Embodiment>
Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 is a diagram illustrating a schematic configuration of a water heater 100 according to the embodiment. As shown in FIG. 1, a water heater 100 is a water heater that uses a heat pump refrigerant circuit 50 as a heat source. The water heater 100 includes a refrigerant circuit 50, a water heating circuit 60, and a water utilization circuit 70.

  The refrigerant circuit 50 is configured by sequentially connecting a compressor 51, a hot water supply heat exchanger 10, an expander 52, and an outdoor heat exchanger 53 via a refrigerant pipe 54. The refrigerant circuit 50 is filled with carbon dioxide as a refrigerant. Carbon dioxide as a refrigerant is in a supercritical state in the high-pressure side portion of the refrigerant circuit 50 (the portion from the compressor 51 through the hot water supply heat exchanger 10 to the expander 52). However, the type of refrigerant is not particularly limited, and may be a refrigerant that does not enter a supercritical state. The refrigerant in the refrigerant circuit 50 is compressed by the compressor 51, then dissipates heat in the hot water supply heat exchanger 10, is decompressed by the expander 52, evaporates in the outdoor heat exchanger 53, and then returns to the compressor 51 again. Return.

  The water heating circuit 60 is a circuit that heats the water in the hot water storage tank 61. The water heating circuit 60 includes a circulation pump 62, a hot water storage tank 61, and the hot water supply heat exchanger 10 described above. The water flowing out of the hot water storage tank 61 exchanges heat with the refrigerant in the hot water supply heat exchanger 10 and is heated by this refrigerant. The heated water becomes hot water and returns to the hot water storage tank 61 through the circulation pump 62. By such water circulation operation, hot water is stored in the hot water storage tank 61.

  The water use circuit 70 is a circuit for using the water in the hot water storage tank 61. The water use circuit 70 is provided with a temperature adjustment valve 71 and various devices that use the water in the hot water storage tank 61.

  FIG. 2 is a perspective view schematically showing the hot water supply heat exchanger 10. In FIG. 2, a part of the hot water supply heat exchanger 10 is cut away. As shown in FIG. 2, the hot water supply heat exchanger 10 includes a thin rectangular parallelepiped box 20. The box 20 includes a flat upper plate 21 and a dish-shaped lower plate 22. Note that the front, rear, top, bottom, left and right directions in the present embodiment are directions for convenience of explanation, and do not necessarily indicate the respective directions of the installed state of the hot water supply heat exchanger 10. The upper plate 21 is formed by cutting a copper plate into a rectangular shape. The lower plate 22 is formed by drawing a copper plate into a shallow container shape. The box 20 is formed by joining the peripheral portions 21a and 22a of the upper plate 21 and the lower plate 22 to each other by brazing or the like. If the vertical direction of the box 20 is the Z direction, the front-rear direction (longitudinal direction of the box 20) is the Y direction, and the left-right direction orthogonal to the Z direction and the Y direction is the X direction, the left front portion of the peripheral portion 22a of the lower plate 22 Is formed with a water inlet 27. Further, a water outlet 28 is formed in the left rear portion of the peripheral portion 21a of the upper plate 21. However, the positions of the inlet 27 and the outlet 28 are not limited at all.

  In the box 20, a plurality of first partition plates 23 and 24 that divide the internal space of the box 20 back and forth are arranged. The first partition plates 23 and 24 extend in the left-right direction, and are arranged in parallel to each other in the front-rear direction. By the first partition plates 23 and 24, a plurality of regions 33 extending in the left-right direction are formed inside the box body 20. Adjacent regions 33 communicate with each other at one end side or the other end side in the left-right direction of each region 33. As a result, the plurality of regions 33 form a meandering flow path 30 from the inlet 27 to the outlet 28.

  A second partition plate 34 extending in the left-right direction is joined to the middle portion of the first partition plates 23, 24 in the vertical direction. Each region 33 is partitioned into an upper flow path 31 and a lower flow path 32 by the second partition plate 34. The left end side or the right end side of the second partition plate 34 is separated from the inner surface of the box 20. Thereby, the upper flow path 31 and the lower flow path 32 are communicated vertically on the left end side or the right end side. As a result, in each region 33, a two-stage round trip path (upper flow path 31 and lower flow path 32) is formed. The flow direction of the upper flow path 31 and the flow direction of the lower flow path 32 are opposed to each other.

  Next, the detailed structure of the 1st partition plates 23 and 24 and the 2nd partition plate 34 is demonstrated. FIG. 3A is a perspective view showing the first partition plate 23 and the second partition plate 34, and FIG. 3B is a perspective view showing the first partition plate 24 and the second partition plate 34. FIG.

  As shown in FIG. 3A, the first partition plate 23 includes a vertical portion 23a formed in a thin plate shape that is long in the left-right direction, and an upper bent portion 23e that is bent rearward from the upper end of the vertical portion 23a. The lower bent portion 23f is bent backward from the lower end of the vertical portion 23a. A slit hole 23g extending in the left-right direction is formed at an intermediate position in the vertical direction of the vertical portion 23a. The right end of the slit hole 23g is located on the left side of the right end of the vertical portion 23a. A cutout 23h is formed at the left end of the vertical portion 23a and above the intermediate position in the vertical direction.

  The second partition plate 34 is fitted in the slit hole 23 g of the first partition plate 23. The second partition plate 34 includes a horizontal portion 23b formed in a thin plate shape that is long in the left-right direction, a rear bent portion 23c that is bent downward from the rear end of the horizontal portion 23b, and a lower portion from the front end of the horizontal portion 23b. And the front bent portion 23d bent toward the front.

  The front side surface of the rear bent portion 23c of the second partition plate 34 and the rear side surface of the vertical portion 23a of the first partition plate 23 are joined by brazing or the like. Thereby, the 2nd partition plate 34 and the 1st partition plate 23 are integrated.

  As described above, the right end of the slit hole 23 g is located on the left side of the right end of the first partition plate 23. Therefore, the right end of the second partition plate 34 is also located on the left side of the right end of the first partition plate 23. Thus, a vertical U-turn channel 35 that connects the upper channel 31 and the lower channel 32 is formed on the right side of the second partition plate 34. As described above, the upper left portion of the first partition plate 23 is provided with the notch 23h. Thus, a front-rear U-turn channel 36 that connects the front upper channel 31 and the rear upper channel 31 of the first partition plate 23 is formed.

  As shown in FIG. 3B, the first partition plate 24 has substantially the same configuration as the first partition plate 23. The difference between the first partition plate 23 and the first partition plate 24 is that the first partition plate 23 has a notch 23h formed in the upper left part, whereas the first partition plate 24 has a notch 23h. The notch 24h is formed in the lower left part. In the first partition plate 24, a front-rear U-turn channel 37 that connects the second channel portion 32 on the front side and the second channel portion 32 on the rear side of the first partition plate 24 is formed by the notch 24 h. Is formed. In FIG. 3, the flow direction of the fluid (water) in the upper flow path 31, the lower flow path 32, and the U-turn flow paths 35, 36, and 37 is indicated by arrows.

  As shown in FIG. 2 (in FIG. 2, the upper bent portion 23e and the lower bent portion 23f of the first divider plate 23 and the first divider plate 24, the front bent portion 23d of the second divider plate 34, etc.) The first partition plate 23 and the first partition plate 24 are alternately arranged in the front-rear direction. As a result, a meandering flow path 30 composed of a plurality of regions 33 is formed inside the box 20, and a two-stage upper and lower reciprocating path composed of an upper flow path 31 and a lower flow path 32 is formed in each area 33. .

  Although not shown, the upper bent portion 23e of the first partition plate 23 and the first partition plate 24 is joined to the inner surface of the upper plate 21 by brazing or the like. The lower bent portion 23f of the first partition plate 23 and the first partition plate 24 is joined to the inner surface of the lower plate 22 by brazing or the like. The front surface of the front bent portion 23d of the second partition plate 34 is joined to the back surface of the adjacent first partition plate 23 or the first partition plate 24 by brazing or the like. However, these junctions are not necessarily required, and can be omitted as appropriate as long as a predetermined heat exchange capability is obtained.

  A heat transfer tube 40 is wound around the outside of the box 20. In the present embodiment, the heat transfer tube 40 is not branched and forms one flow path as a whole. The heat transfer tubes 40 are arranged along the longitudinal direction (left and right direction in the drawing) of each region 33 of the box 20. Of the heat transfer tubes 40, the straight portions 40a arranged in the left-right direction along the upper and lower surfaces of the box 20 are joined to the box 20 by brazing or the like. On the other hand, among the heat transfer tubes 40, the curved portion 40 b disposed along the front-rear direction of the box body 20 and the curved portion 40 c disposed along the vertical direction of the box body 20 are joined to the box body 20. It has not been. In the present embodiment, the straight portion 40a is formed by a single tube, and the curved portions 40b and 40c are formed by a U-bend that connects the single tubes. By adopting such a configuration, the manufacturing process is simplified and the manufacturing becomes easy. In the present embodiment, the box 20, the partition members 23 and 24, and the heat transfer tube 40 are all made of copper. However, the present invention is not limited to this, and various materials can be used as long as the members have good thermal conductivity. can do.

  FIG. 4 is an explanation for explaining the flow direction of the fluid (water) in the upper flow path 31 and the lower flow path 32 in the meandering flow path 30 shown in FIG. 2 and the flow direction of the refrigerant in the heat transfer tube 40. FIG. In FIG. 4, the upper flow path 31 and the lower flow path 32 are shown as plan views as viewed from above. In FIG. 4, the flow direction of the water flowing in the upper flow path 31 and the lower flow path 32 is indicated by a thin line, and the flow direction of the refrigerant flowing in the heat transfer tube 40 is indicated by a thick line. In addition, among the thick lines indicating the flow direction of the refrigerant in the heat transfer tube 40, the broken line indicates that the heat transfer tube 40 is disposed below the box 20 (see FIG. 2). .

  As shown in FIG. 4, the heat transfer tube 40 is disposed along the meandering flow path 30. In the meandering flow path 30, the flow direction of the fluid in the upper flow path 31 and the lower flow path 32 extending in the left-right direction of the box 20 is opposite to the flow direction of the fluid in the straight portion 40 a of the heat transfer tube 40. . Therefore, the fluid in the upper flow path 31 and the lower flow path 32 of the meandering flow path 30 and the fluid in the straight portion 40a of the heat transfer tube 40 are all in counterflow.

  Further, in the meandering flow path 30, the flow direction of the fluid in the U-turn flow path 36 and the U-turn flow path 37 extending in the front-rear direction of the box 20 is the flow direction of the fluid in the curved portion 40 b of the heat transfer tube 40. The reverse direction.

  Further, although not shown in FIG. 4, the flow direction of the fluid in the U-turn flow path 35 (see FIG. 3) extending in the vertical direction of the box 20 in the meandering flow path 30 is the curve of the heat transfer tube 40. It is the direction opposite to the flow direction of the fluid in the part 40c (refer FIG. 2). That is, the hot water supply heat exchanger 10 according to the embodiment is opposed to the heat transfer tube 40 with respect to the entire meandering flow path 30 from the inlet 27 to the outlet 28.

  The fluid (water) flowing through the meandering flow path 30 first enters the lower flow path 32 from the introduction port 27. Then, after traveling in the right direction in the lower flow path 32, the U-turn flow path 35 (see FIG. 3) is advanced upward from the right end of the lower flow path 32, and then in the left direction in the upper flow path 31. Proceed to When the left end of the upper flow path 31 is reached, the U-turn flow path 36 is then moved rearward, and then proceeds to the right from the left end in the upper flow path 31. When the right end of the upper flow path 31 is reached, the U-turn flow path 35 (see FIG. 3) is moved downward to reach the right end of the lower flow path 32. When it reaches the right end of the lower flow path 32, it proceeds in the left direction in the lower flow path 32, then proceeds through the U-turn flow path 37, and reaches the left end of the lower flow path 32. Thereafter, similarly, the lower channel 32, the U-turn channel 35, the upper channel 31, the U-turn channel 36, the upper channel 31, the U-turn channel 35, the lower channel 32, and the U-turn channel. The process proceeds repeatedly in the order of 37 and reaches the outlet 28 at the left end of the upper channel 31.

  On the other hand, the refrigerant flowing through the heat transfer tube 40 first proceeds in the right direction along the upper flow path 31 from the portion where the outlet 28 is formed. Then, after proceeding downward from the right end portion of the upper flow path 31 along the U-turn flow path 35, the process proceeds leftward along the lower flow path 32. When it reaches the left end of the lower flow path 32, it proceeds forward along the U-turn flow path 37 and then proceeds rightward along the lower flow path 32. When it reaches the right end of the lower flow path 32, it proceeds upward along the U-turn flow path 35, and then proceeds leftward along the upper flow path 31. Then, it advances ahead along the U-turn flow path 36 and reaches the left end of the upper flow path 31. Thereafter, similarly, the upper flow path 31, the U-turn flow path 35, the lower flow path 32, the U-turn flow path 37, the lower flow path 32, the U-turn flow path 35, the upper flow path 31, and the U-turn flow path. It progresses repeatedly in the order of 36, and reaches the part where the inlet 27 at the left end of the lower flow path 32 is formed.

  As described above, in the hot water supply heat exchanger 10 according to the embodiment, the meandering flow is performed in the entire joining portion of the meandering flow path 30 with the heat transfer tube 40, that is, in the entire upper flow path 31 and the lower flow path 32. The water flowing through the passage 30 and the refrigerant flowing through the heat transfer tube 40 are counterflows. Therefore, heat exchange performance can be improved.

  Moreover, in this embodiment, the heat exchanger tube 40 is not branched, but forms one flow path as a whole. Therefore, it is not necessary to split the refrigerant when the counterflow is performed. Therefore, it is possible to improve the heat exchange performance while preventing the pressure loss from varying due to the diversion.

  In this embodiment, counterflow is realized in the entire meandering channel 30, but as long as heat exchange performance can be improved, part of the meandering channel 30 is parallelized or cross-flowed. It may be made. For example, the refrigerant in the heat transfer tube 40 and the water in the meandering channel 30 may be counterflowed over most of the portion of the heat transfer tube 40 that is in contact with the box 20 (for example, 55% or more).

  Further, in the present embodiment, only the straight portion 40 a of the heat transfer tube 40 arranged in the left-right direction of the upper surface and the lower surface of the box body 20 is joined to the box body 20. However, the curved portion 40b disposed along the front-rear direction of the box 20 and the curved portion 40c disposed along the vertical direction of the box 20 may also be joined to the box 20. Of course. In this case, the heat exchange rate can be further improved.

Second Embodiment
FIG. 5A is a perspective view showing the first partition plate 23 and the second partition plate 34 according to the second embodiment, and FIG. 5B is the first partition according to the second embodiment. It is a perspective view which shows the board 24 and the 2nd partition plate 34. FIG.

  As shown in FIGS. 5A and 5B, in the second embodiment, thin plate-like inner fins 45 are joined to the vertical portions 23a, 24a of the first partition plates 23, 24 by brazing or the like. ing. Two inner fins 45 are provided in parallel with the second partition plate 34, two above and below the second partition plate 34. The inner fin 45 is made of copper. However, the material of the inner fin 45 is not limited to this, and other members may be used.

  Thus, in the second embodiment, the inner fin 45 is provided in the meandering flow path 30. Therefore, the heat transfer area can be increased, and the heat exchange performance of the hot water supply heat exchanger 10 can be further improved.

<Third Embodiment>
FIG. 6A is a perspective view showing the first partition plate 23 and the second partition plate 34 according to the third embodiment, and FIG. 6B is the first partition according to the third embodiment. It is a perspective view which shows the board 24 and the 2nd partition plate 34. FIG.

  As shown in FIGS. 6A and 6B, in the third embodiment, as in the second embodiment (see FIG. 5), the inner fins 45 are fixed to the vertical portions 23a and 24a. However, in the present embodiment, the inner fin 45 is formed with a plurality of holes 45a arranged at predetermined intervals in the left-right direction. The hole 45a corresponds to the turbulent flow promoting portion referred to in the present invention. By forming the hole 45a, the flow of the fluid in the meandering flow path 30 can be stirred, and the heat exchange performance of the hot water supply heat exchanger 10 can be improved. Moreover, since it is the structure which stirs the flow of the fluid by the hole 45a formed in the inner fin 45, a turbulent flow promotion part can be formed by simple operation.

  However, the turbulent flow promoting portion in the inner fin 45 is not limited to the hole 45a. For example, the turbulent flow promoting portion may be formed by providing a turbulent flow promoting body such as a protrusion on the inner fin 45.

<Fourth embodiment>
By the way, when the fluid flowing through the meandering flow path 30 is water, precipitation of calcium contained in the water becomes a problem. In particular, precipitation at a portion where water heated to a high temperature flows, that is, in the vicinity of the outlet 28 of the meandering channel 30 poses a problem. Therefore, in the present embodiment, the flow passage cross-sectional area on the outlet port 28 side is made larger than the flow passage cross-sectional area on the introduction port 27 side. In this case, it is desirable that the flow path cross-sectional area be increased stepwise from the inlet 27 side toward the outlet 28 side.

  There is no particular limitation on the method of making the flow path cross-sectional area on the outlet 28 side larger than the flow path cross-sectional area on the inlet 27 side. As an example, as shown in FIGS. 7A and 7B, the number of inner fins 45 provided on the outlet 28 side may be smaller than the number provided on the inlet 27 side. FIG. 7A shows the first partition plate 23 (or the first partition plate 24) provided on the introduction port 27 side. In the first partition plate 23, two inner fins 45 are respectively provided above and below the second partition plate 34. On the other hand, FIG. 7B shows the first partition plate 23 (or 24) provided on the outlet 28 side. In the first partition plate 23, one inner fin 45 is provided above and below the second partition plate 34. In this method, the flow passage cross-sectional area of the outlet 28 can be increased with a simple configuration.

<Fifth Embodiment>
As another method for making the flow passage cross-sectional area on the outlet port 28 side larger than the flow passage cross-sectional area on the introduction port 27 side, there is a method of changing the flow passage width. For example, as shown in FIG. 8, the interval between the adjacent first partition plates 23 and 24 on the outlet 28 side, or the interval between the first partition plate 23 or 24 and the inside of the box body 20 (exit side) Channel width) between the adjacent first partition plates 23 and 24 on the inlet 27 side, or between the first partition plate 23 or 24 and the inside of the box body 20 (inlet side channel width). ) May be wider. As shown in FIG. 8, the channel width may be increased stepwise from the inlet 27 to the outlet 28.

  As another method for making the flow passage cross-sectional area on the outlet 28 side larger than the flow passage cross-sectional area on the inlet 27 side, the distance between the upper plate 21 and the lower plate 22 on the outlet 28 side (flow path height). ) May be larger than the interval on the inlet 27 side. In this method, the flow passage cross-sectional area of the outlet port 28 can be increased by a simple method of adjusting the molding shapes of the upper plate 21 and the lower plate 22.

  In addition, the upper plate 21 and the lower plate 22 (refer FIG. 2) in this embodiment correspond to the 1st and 2nd heat exchanger plate said to this invention, respectively. The first and second heat transfer plates may have a substantially plate shape as a whole, and are not necessarily limited to a flat plate shape. For example, a curved plate shape or a bent plate shape may be used. Moreover, the lower plate 22 may be formed in a dish shape as in this embodiment, and various other shapes can be adopted as the shapes of the first and second heat transfer plates.

  In the present embodiment, the box 20 has a thin rectangular parallelepiped shape. However, in the present invention, the shape of the box is not limited to the rectangular parallelepiped shape, and various shapes can be employed. For example, like the box 320 shown in FIG. 9, the side surface 320a may be curved so as to protrude outward. Moreover, the flat cylindrical shape etc. may be sufficient. In addition, in FIG. 9, the heat exchanger tube 40 wound around the box 320 is shown.

  Further, in the first to fifth embodiments, it has been described that the heat transfer tube 40 is simply wound around the outside of the box 20 and the box 20 and the heat transfer tube 40 are joined by brazing or the like. Furthermore, in order to promote the heat exchange between the box 20 and the heat transfer tube 40, a configuration of a heat exchanger as shown in FIG. That is, in order to increase the contact area between the box 20 and the heat transfer tube 40, a depression may be formed in the box 40 in advance by a method such as pressing, and the heat transfer tube may be wound along the depression. . Also in this case, adhesion between the box 20 and the heat transfer tube 40 is brazing or the like.

  As described above, the present invention is useful for heat exchangers, refrigeration cycle apparatuses, water heaters, and the like.

The figure which shows schematic structure of the water heater based on embodiment. Perspective view showing a hot water heat exchanger (A) And (b) is a perspective view which shows a 1st partition plate and a 2nd partition plate Explanatory drawing for demonstrating the flow direction of the fluid of the upper flow path and lower flow path in a meandering flow path, and the flow direction of the refrigerant | coolant in a heat exchanger tube (A) And (b) is a perspective view which shows the 1st partition plate and 2nd partition plate which concern on 2nd Embodiment. (A) And (b) is a perspective view which shows the 1st partition plate and 2nd partition plate which concern on 3rd Embodiment. (A) And (b) is a perspective view which shows the 1st partition plate and 2nd partition plate which concern on 4th Embodiment. The top view which shows the meandering flow path which concerns on 5th Embodiment The perspective view which shows the hot water supply heat exchanger which concerns on the modification of this invention Exploded perspective view showing a heat exchanger according to the prior art Plan view of a heat exchanger according to the prior art The figure which shows the meandering flow path formed in the inside of the heat exchanger which concerns on a prior art The perspective view which shows the hot water supply heat exchanger which concerns on the modification of this invention

Explanation of symbols

10 Hot water supply heat exchanger (heat exchanger)
20 Box 21 Upper plate (first heat transfer plate)
22 Lower plate (second heat transfer plate)
23, 24 First partition plate 27 Inlet 28 Outlet 30 Meandering channel 31 Upper channel (first channel)
32 Lower channel (second channel)
33 region 34 second partition plate 35, 36, 37 U-turn flow path 40 heat transfer tube 45 inner fin 45a hole (turbulent flow promoting portion)
50 Refrigerant circuit 60 Water heating circuit 70 Water utilization circuit 100 Water heater

Claims (14)

A second heat transfer plate formed on the opposite side of the first heat transfer plate and the first heat transfer plate is formed with an introduction port for introducing the first fluid and an outlet port for deriving the first fluid. A hermetically sealed box having
By dividing the space between the inner surface of the first heat transfer plate and the inner surface of the second heat transfer plate inside the box body, the space extends in a predetermined direction and crosses the predetermined direction. A plurality of first partition plates having a plurality of regions arranged and forming a meandering flow path from the inlet to the outlet;
It is provided in at least one of the plurality of regions, and the region is partitioned into a first flow path portion on the first heat transfer plate side and a second flow path portion on the second heat transfer plate side. A second partition plate forming a reciprocating path composed of the first flow path part and the second flow path part in the region,
A heat transfer tube for guiding a second fluid that exchanges heat with the first fluid, the heat transfer tube being in contact with an outer surface of the first heat transfer plate in the first flow path section and along the first flow path section. A first heat transfer tube component extending; and a second heat transfer tube component contacting the outer surface of the second heat transfer plate in the second flow channel and extending along the second flow channel. And the heat transfer tube wound around the box so that the flow direction of the first heat transfer tube component and the flow direction of the second heat transfer tube component are opposed to each other,
With heat exchanger. The plurality of regions include first, second and third regions in which the first flow path part and the second flow path part are respectively formed and arranged in a direction intersecting the predetermined direction.
The first channel portion of the first region and the first channel portion of the second region communicate with each other,
2. The heat exchanger according to claim 1, wherein the second flow path part of the second region and the second flow path part of the third region communicate with each other. The heat exchanger according to claim 1, wherein the second partition plate is provided in each of the plurality of regions. The heat according to claim 1, wherein fins are provided on the inner side of the first heat transfer plate, the inner side of the second heat transfer plate, the first partition plate, or the second partition plate. Exchanger. The heat exchanger according to claim 4, wherein the fin is provided with a turbulence promoting portion that disturbs the flow of the first fluid. The heat exchanger according to claim 4, wherein holes are formed in the fins. The plurality of regions include an inlet side region facing the inlet and an outlet side region facing the outlet.
2. The heat exchanger according to claim 1, wherein a channel cross-sectional area of the outlet side region is larger than a channel cross-sectional area of the inlet side region. The plurality of first partition plates are arranged in parallel to each other,
The outlet side flow path width that is the length along the arrangement direction of the first partition plate in the outlet side region is the inlet that is the length along the arrangement direction of the first partition plate in the inlet side region. The heat exchanger according to claim 7, wherein the heat exchanger is wider than the side flow path width. The plurality of first partition plates are arranged in parallel to each other,
Each first partition plate is provided with one or more fins,
The heat exchanger according to claim 7, wherein the number of fins in the outlet side region is larger than the number of fins in the inlet side region. The heat exchanger according to claim 9, wherein the first fluid is water heated by the second fluid. The heat exchanger of claim 1, wherein the second fluid is carbon dioxide. A box body in which the first fluid flows; and a heat transfer tube that is wound around the outside of the box body and in which the second fluid flows, and heats the first fluid and the second fluid. A heat exchanger to be exchanged,
Inside the box, a meandering channel having a plurality of regions extending in a predetermined direction and arranged in a direction intersecting the predetermined direction is formed,
The heat transfer tube is arranged along the longitudinal direction of each region on both the front side and the back side of the box,
In each of the regions, a reciprocal flow composed of a front-side flow channel and a back-side flow channel so that the flow direction of the first fluid flowing in the box body and the flow direction of the second fluid flowing in the heat transfer tube are opposed to each other. A heat exchanger in which a path is formed. A heat exchanger according to claim 1;
A compressor for compressing the refrigerant;
A first pipe for guiding the refrigerant compressed by the compressor to the heat transfer pipe as the second fluid;
A second pipe for guiding the refrigerant flowing through the heat transfer pipe;
A decompression mechanism for decompressing the refrigerant flowing through the second pipe;
A third pipe for guiding the refrigerant decompressed by the decompression mechanism;
An evaporator for evaporating the refrigerant flowing through the third pipe;
A fourth pipe for guiding the refrigerant evaporated in the evaporator to the compressor;
A refrigeration cycle apparatus comprising: A refrigeration cycle apparatus according to claim 13,
The water heater in which the first fluid is water and generates hot water in the heat exchanger.

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