JPWO2018216245A1 - Plate heat exchanger and heat pump hot water supply system - Google Patents

Abstract

The plate type heat exchanger (1) includes a plate portion (39, 49) having an outflow / inlet hole for allowing a fluid to flow in and out, and extends on one surface side of the plate portion (39, 49). The first outer peripheral wall portion (31) or the second outer peripheral wall portion (31) forming a flow path for flowing a fluid between the plate portion (39, 49) adjacent to one surface side of the portion (39, 49). 41) and a first heat transfer plate (30) or a second heat transfer plate (40) including a first inner fin (38) or a second inner fin (48) attached in the flow path. Are stacked. The first inner fin (38) and the second inner fin (48) are provided on one surface of the plate portion (39, 49) in the first fluid outflow / inlet holes (32, 35) in the flow path and the second fluid outflow hole. It is placed at a position separated from the entrance holes (43, 46).

Description

  The present invention relates to a plate heat exchanger and a heat pump hot water supply system.

  Some plate heat exchangers have a configuration in which a plurality of heat transfer plates in each of which a flow path for flowing a fluid is formed are stacked.

  For example, Patent Literature 1 discloses a plate heat exchanger having a configuration in which a plurality of heat transfer plates each having a flow path and a fluid outflow / inflow hole that communicates with the flow path and flows fluid in and out are stacked. Have been.

  In the plate heat exchanger described in Patent Literature 1, the flow path is formed in a rectangular concave shape in plan view. The fluid inflow / outflow hole is adjacent to the recess of the flow path. Further, the inner fin is disposed in the entire recess of the flow path, thereby increasing the heat exchange efficiency.

International Publication No. 2008/023732

  In the plate heat exchanger described in Patent Literature 1, the fluid inflow / outflow hole is adjacent to the recess of the flow path. For this reason, the fluid easily flows to the portion of the inner fin adjacent to the fluid outflow / inflow hole. However, the fluid is less likely to flow to other portions of the inner fin away from the fluid inflow / outflow holes. As a result, the pressure loss of the fluid is large in the entire inner fin. Thereby, the heat exchange efficiency of the plate heat exchanger decreases.

  The present invention has been made to solve the above problems, and has as its object to provide a plate heat exchanger and a heat pump hot water supply system with high heat exchange efficiency.

  In order to achieve the above object, a plate heat exchanger according to the present invention includes a plate portion having an inflow / outflow hole through which a fluid flows in and out, and a plate portion extending on one surface side of the plate portion. A plurality of heat transfer plates having an outer peripheral wall portion forming a flow path for flowing a fluid between adjacent plate portions on one surface side of the heat transfer plate and inner fins mounted in the flow path are stacked. Have been. The inner fin is mounted on one surface of the plate portion at a position separated from the inflow / outflow hole in the flow path, and the entire periphery of the inflow / outflow hole is in contact with a space where the inner fin is not arranged.

  According to the configuration of the present invention, since the inner fin is placed on one surface of the plate portion at a position separated from the outflow / inflow hole in the flow path, the inner fin does not cover the outflow / inflow hole. Further, since the entire circumference of the outflow / inflow hole is in contact with the space where the inner fin is not arranged, a sufficient space for fluid flow is secured around the outflow / inflow hole. Since the fluid spreads over the entire flow path in the space where the inner fin is not arranged, the pressure loss of the fluid is small in the present invention. As a result, the heat exchange efficiency can be increased.

Exploded perspective view of a plate heat exchanger according to Embodiment 1 of the present invention. Sectional view of the II-II line shown in FIG. Sectional view of the line III-III shown in FIG. Sectional view of the line IV-IV shown in FIG. Front view of the first heat transfer plate provided in the plate heat exchanger according to Embodiment 1 of the present invention. Sectional view of the first passage hole and the second passage hole formed in the first heat transfer plate and the second heat transfer plate of the plate heat exchanger according to Embodiment 1 of the present invention. Front view of a second heat transfer plate included in the plate heat exchanger according to Embodiment 1 of the present invention. FIG. 3 is an enlarged plan view of an end of a first heat transfer plate included in the plate heat exchanger according to Embodiment 1 of the present invention. 8A is a perspective view when viewed from the front, and FIG. 8B is a perspective view when viewed from the back. Enlarged plan view of an end of a second heat transfer plate provided in the plate heat exchanger according to Embodiment 1 of the present invention. In the plate heat exchanger according to Embodiment 1 of the present invention, an enlarged plan view showing a positional relationship between a first convex portion and a second convex portion. Sectional view of a first fluid supply pipe, a first fluid outflow / inlet hole, and a second passage hole formed in the plate heat exchanger according to Embodiment 1 of the present invention. FIG. 4 is an enlarged plan view of an end of a first heat transfer plate included in a plate heat exchanger according to Embodiment 2 of the present invention. Enlarged plan view of an end of a second heat transfer plate provided in a plate heat exchanger according to Embodiment 2 of the present invention. In the plate heat exchanger according to Embodiment 2 of the present invention, an enlarged plan view showing a positional relationship between a first convex portion and a second convex portion. Conceptual sectional view of the first fluid supply pipe and the second fluid supply pipe of the plate heat exchanger according to Embodiment 2 of the present invention. Enlarged plan view of the end of the second heat transfer plate provided in the plate heat exchanger according to Embodiment 3 of the present invention. Conceptual sectional view of a first fluid supply pipe and a second fluid supply pipe of a plate heat exchanger according to Embodiment 3 of the present invention. Embodiment 4 An enlarged sectional view of a laminate of a plate heat exchanger according to Embodiment 4 of the present invention. Block diagram of heat pump hot water supply system according to Embodiment 5 of the present invention An enlarged plan view of an end of a first heat transfer plate provided in a plate heat exchanger according to Embodiment 6 of the present invention. An enlarged plan view of an end of a second heat transfer plate provided in a plate heat exchanger according to Embodiment 6 of the present invention. In the plate heat exchanger according to Embodiment 6 of the present invention, an enlarged plan view illustrating a positional relationship between a first convex portion and a second convex portion. Sectional drawing which shows the modification of the flange of the 1st tubular wall and the 2nd tubular wall of the plate-type heat exchanger which concerns on Embodiment 1 of this invention. Sectional drawing which shows the modification of the 1st fluid supply pipe, 1st fluid inflow / outlet hole, and 1st passage hole of the plate-type heat exchanger which concerns on Embodiment 1 of invention. Perspective view (A) of a first inner fin disposed on a first heat transfer plate and a second inner fin disposed on a second heat transfer plate provided in the plate heat exchanger according to Embodiment 1 of the present invention. Perspective view of offset fins, (B) perspective view of flat fins, (C) perspective view of corrugated fins, (D) perspective view of louver fins, (E) perspective view of corrugated fins, (F) Perspective view of pin type fin 8A is a rear view when the first convex portion is formed in a circular shape, FIG. 8B is a rear view when the first convex portion is formed in a wedge shape, and FIG. A rear view when one convex portion is formed in an elliptical shape, (D) a rear view when the first convex portion is formed in a triangular shape, and (E) a rear view in a case where the first convex portion is formed in a rectangular shape. (F) Rear view when the first convex portion is formed in an arc shape FIG. 4 is an enlarged plan view showing a modification of the first convex portion of the plate heat exchanger according to Embodiment 1 of the present invention. FIG. 4 is an enlarged plan view showing another modification of the first convex portion of the plate heat exchanger according to Embodiment 1 of the present invention.

  Hereinafter, a plate heat exchanger and a heat pump hot water supply system according to an embodiment of the present invention will be described in detail with reference to the drawings. In the drawings, the same or equivalent parts are denoted by the same reference numerals. In the orthogonal coordinate system XYZ shown in the figure, the horizontal direction of the plate heat exchanger is the X axis, the vertical direction is the Z axis, and the direction orthogonal to the X axis and the Z axis is the Y axis. Hereinafter, description will be made with reference to this coordinate system as appropriate.

(Embodiment 1)
The plate heat exchanger according to Embodiment 1 exchanges heat between two fluids, so that the first heat transfer plate in which a flow path for flowing one fluid is formed, and the other fluid And a second heat transfer plate in which a flow path for flowing is formed. In this plate heat exchanger, a space is provided around the fluid outflow / inlet hole formed in the flow path to facilitate the flow of the fluid into the flow path of the first heat transfer plate and the second heat transfer plate. I have. Further, in this plate heat exchanger, the pressure loss is small because the fluid flows through the space to the inner fin provided in the flow path. The configuration of the plate heat exchanger will be described with reference to FIGS. In the following description, the two fluids will be referred to as a first fluid and a second fluid.

FIG. 1 is an exploded perspective view of a plate heat exchanger 1 according to Embodiment 1 of the present invention. FIG. 2 is a sectional view taken along line II-II shown in FIG. FIG. 3 is a sectional view taken along line III-III shown in FIG. FIG. 4 is a sectional view taken along line IV-IV shown in FIG. 2 to 4, a part of the first heat transfer plate 30 and the second heat transfer plate 40 among the plurality of first heat transfer plates 30 and the second heat transfer plates 40 is omitted.
As shown in FIGS. 1 to 4, the plate heat exchanger 1 according to the first embodiment includes a first heat transfer plate 30 in which a flow path for flowing a first fluid is formed; A second heat transfer plate 40 in which a flow path for flowing a second fluid to be exchanged is formed, and a plurality of stacked bodies 100 are alternately stacked. The laminate 100 is sandwiched and reinforced by the first reinforcing plate 10 and the second reinforcing plate 20.

  Hereinafter, among the configurations of the plate heat exchanger 1, first, the configurations of the first reinforcing plate 10 and the second reinforcing plate 20 will be described. Subsequently, the configuration of the first heat transfer plate 30 and the second heat transfer plate 40 will be described.

  The first reinforcing plate 10 is a plate that reinforces the multilayer body 100 and is connected to a connection pipe for supplying and discharging the first fluid and the second fluid flowing through the multilayer body 100. As shown in FIG. 1, the first reinforcing plate 10 is formed in a rectangular shape with rounded corners. The first reinforcing plate 10 is arranged in parallel with the XZ plane and at the most + Y side in the plate heat exchanger 1. The first reinforcing plate 10 is provided with a first reinforcing outer peripheral wall portion 11 surrounding the outer periphery of the first reinforcing plate 10. As shown in FIGS. 2 and 3, the first reinforcing outer peripheral wall portion 11 is joined to a second outer peripheral wall portion 41 (described later) of the second heat transfer plate 40 located closest to the + Y side in the laminate 100. are doing. Further, the first reinforcing outer peripheral wall portion 11 is formed in a shape that is inclined outward from the first reinforcing plate 10 as going from the periphery of the first reinforcing plate 10 in the + Y direction.

  As shown in FIG. 1, a first fluid supply pipe 12 for supplying a first fluid and a second fluid to the laminate 100 and a second fluid supply pipe 13 are provided at the + X end of the first reinforcing plate 10. And are provided. The first fluid supply pipe 12 and the second fluid supply pipe 13 are arranged side by side in the Z direction, and extend in the + Y direction, respectively. Here, the first fluid supply pipe 12 and the second fluid supply pipe 13 are respectively connected to connection pipes (not shown) for supplying the first fluid and the second fluid. The first fluid and the second fluid are respectively supplied to the first fluid supply pipe 12 and the second fluid supply pipe 13 via the connection pipes. In the first fluid supply pipe 12, the first fluid flows in the direction indicated by the arrow F, and in the second fluid supply pipe 13, the second fluid flows in the direction indicated by the arrow S.

  On the other hand, at the −X end of the first reinforcing plate 10, a first fluid discharge pipe 14 for discharging the first fluid and the second fluid from the laminate 100 and a second fluid discharge pipe 15 are provided. I have. The first fluid discharge pipe 14 and the second fluid discharge pipe 15 are formed in the same shape as the first fluid supply pipe 12 and the second fluid supply pipe 13 described above. The first fluid discharge pipe 14 and the second fluid discharge pipe 15 are arranged in the Z direction. Then, they extend in the + Y direction. The first fluid discharge pipe 14 and the second fluid discharge pipe 15 are respectively connected to connection pipes (not shown) for discharging the first fluid and the second fluid. In the first fluid discharge pipe 14 and the second fluid discharge pipe 15, the first fluid and the second fluid are discharged to the connection pipes.

  On the other hand, the second reinforcing plate 20 is a plate for reinforcing the laminated body 100 without a portion connected to the connection pipe of the first fluid and the second fluid. The second reinforcing plate 20 is formed in a rectangular shape having the same outer shape as the first reinforcing plate 10. The second reinforcing plate 20 is arranged parallel to the first reinforcing plate 10. The second reinforcing plate 20 is disposed closest to the −Y side in the plate heat exchanger 1, and sandwiches the laminate 100 between the second reinforcing plate 20 and the first reinforcing plate 10. In the second reinforcing plate 20, in order to join with the first outer peripheral wall portion 31 of the first heat transfer plate 30 located on the most -Y side of the sandwiched laminated body 100, the outer peripheral surface is surrounded by the second reinforcing plate 20 and the outer peripheral portion thereof. A second reinforcing outer peripheral wall portion 21 inclined to is provided. The shape of the second reinforcing outer peripheral wall 21 is the same as that of the first reinforcing outer peripheral wall 11.

  Next, the first heat transfer plate 30 and the second heat transfer plate 40 of the above-described laminate 100 will be described with reference to FIGS.

FIG. 5 is a front view of the first heat transfer plate 30. FIG. 6 is a cross-sectional view of the first passage holes 33 and 36 and the second passage holes 42 and 45 formed in the first heat transfer plate 30 and the second heat transfer plate 40. FIG. 7 is a front view of the second heat transfer plate 40.
The first heat transfer plate 30 is a member for flowing a first fluid in the plate heat exchanger 1. As shown in FIG. 5, the first heat transfer plate 30 has a plate portion 39 and a first outer peripheral wall portion 31 surrounding the outer periphery of the plate portion 39.

  The plate portion 39 is formed in a rectangular shape with rounded corners. The shape and size of the plate portion 39 are the same as those of the first reinforcing plate 10 and the second reinforcing plate 20 described above.

  The first outer peripheral wall portion 31 extends from the outer periphery of the plate portion 39 to the + Y side, as shown in FIGS. The first outer peripheral wall portion 31 is inclined toward the outside of the plate portion 39 as extending toward the + Y side. The + Y end of the first outer peripheral wall portion 31 is in contact with a later-described second outer peripheral wall portion 41 of the second heat transfer plate 40 located on the + Y side with respect to the plate portion 39. Thereby, the + Y side of the space formed by the first outer peripheral wall portion 31 surrounding the plate portion 39 is closed. The laminate 100 has a plurality of spaces surrounded by the first outer peripheral wall 31.

  As shown in FIG. 5, the first fluid is provided on the + X end side and the −X end side of the plate portion 39 to allow the first fluid to flow between the space surrounded by the first outer peripheral wall portion 31 described above. First fluid inflow / outflow holes 32 and 35 for letting out / in are formed. As described later, a space in which the second outer peripheral wall portion 41 surrounds the plate portion 49 is also formed in the second heat transfer plate 40. To allow the second fluid to flow through the space formed in the second heat transfer plate 40, the first passage holes 33 and 36 through which the second fluid flows in and out are provided at the + X end side and the -X end side of the plate portion 39. Is formed.

  The first fluid inflow / outflow holes 32 and 35 are circular holes penetrating the first heat transfer plate 30 in the Y direction. The first fluid inflow and outflow holes 32 and 35 have the same inner diameter. The first fluid inflow and outflow holes 32 and 35 are formed at positions overlapping the first fluid supply pipe 12 and the first fluid discharge pipe 14 of the first reinforcing plate 10 in the stacked body 100 shown in FIG. ing.

  The first passage holes 33 and 36 are circular holes penetrating the first heat transfer plate 30 in the Y direction, and have the same inner diameter as the first fluid outflow / inlet holes 32 and 35. The first passage holes 33, 36 are arranged on the −Z side with respect to the first fluid outflow / inflow holes 32, 35. As shown in FIG. 3, the first passage holes 33 and 36 are formed at positions overlapping the second fluid supply pipe 13 and the second fluid discharge pipe 15 of the first reinforcing plate 10 when viewed in the Y direction. . In addition, the first passage holes 33 and 36 communicate with a later-described second fluid outflow / intake hole 46 of the second heat transfer plate 40, so that the first tubular wall continuous with the inner peripheral wall of the first passage holes 33 and 36. 34 and 37 are provided. As shown in FIG. 6, the + Y ends of the first tubular walls 34, 37 extend radially from the outer walls of the first tubular walls 34, 37 to join with the plate portion 49 of the second heat transfer plate 40. Flange 300 is provided. Note that FIGS. 1 and 2 to 5 show the first tubular walls 34 and 37 from which the flange 300 is omitted for easy understanding.

  On the other hand, the second heat transfer plate 40 is a member for flowing the second fluid in the plate heat exchanger 1. Similar to the first heat transfer plate 30, the second heat transfer plate 40 has a plate portion 49 shown in FIG. 7 and a second outer peripheral wall portion 41 surrounding the outer periphery of the plate portion 49.

  The plate portion 49 is formed in the same shape and size as the plate portion 39 of the first heat transfer plate 30. The second outer peripheral wall 41 is formed in the same shape and size as the first outer peripheral wall 31 of the first heat transfer plate 30. The + Y end of the second outer peripheral wall portion 41 is, as shown in FIG. 2 to FIG. 4, the first reinforcing outer peripheral wall portion 11 or the first reinforcing outer wall portion of the first reinforcing plate 10 located on the + Y side with respect to the plate portion 49. One heat transfer plate 30 is in contact with the first outer peripheral wall portion 31. As a result, the + Y side of the space formed by the second outer peripheral wall portion 41 surrounding the outer periphery of the plate portion 49 is closed by the first reinforcing plate 10 or the first heat transfer plate 30. A plurality of spaces surrounded by the second outer peripheral wall 41 are formed in the laminate 100.

  As shown in FIG. 7, the second fluid is provided on the + X end side and the −X end side of the plate portion 49 to allow the second fluid to flow between the space surrounded by the second outer peripheral wall portion 41 described above. The second fluid inflow and outflow holes 43 and 46 for letting inflow and outflow are formed. Further, on the + X end side and the −X end side of the plate portion 49, the first fluid flows through the above-described space formed by surrounding the first outer peripheral wall portion 31 of the first heat transfer plate 30, Second passage holes 42 and 45 through which the first fluid flows in and out are formed.

  The second fluid inflow / outflow holes 43 and 46 are circular holes penetrating the plate portion 49. The second fluid inflow / outflow holes 43, 46 have the same inner diameter as the first passage holes 33, 36. As shown in FIG. 3, the second fluid inflow / outflow holes 43 and 46 are formed at positions overlapping the second fluid supply pipe 13 and the second fluid discharge pipe 15 of the first reinforcing plate 10 in the Y direction. I have. Thereby, in the second fluid inflow / outflow hole 43, when the second fluid is supplied from the second fluid supply pipe 13 into the stacked body 100, the second fluid passes through the first passage hole 33 overlapping in the Y direction. Circulates smoothly in the Y direction. In the second fluid inflow / outflow hole 46, the second fluid flows through the first passage hole 36 in the Y direction, that is, to the second fluid discharge pipe 15.

  The second passage holes 42 and 45 are circular holes penetrating the plate portion 49. The second passage holes 42, 45 have the same inner diameter as the first fluid outflow / inflow holes 32, 35. As shown in FIG. 2, the second passage holes 42 and 45 are formed at positions overlapping the first fluid supply pipe 12 and the first fluid discharge pipe 14 of the first reinforcing plate 10 when viewed in the Y direction. In addition, since the second passage holes 42 and 45 communicate with the first fluid supply pipe 12, the first fluid discharge pipe 14, or the first fluid outflow / inlet holes 32 and 35, inner peripheral walls of the second passage holes 42 and 45 are provided. And second tubular walls 44 and 47 extending in the + Y direction are provided. Thus, in the second passage hole 42, when the first fluid is supplied from the first fluid supply pipe 12, the first fluid flows to the first fluid outflow / inlet hole 32 in the Y direction. In the second passage hole 45, the first fluid flows through the first fluid inflow / outflow hole 35 and the first fluid discharge pipe 14 that overlap in the Y direction. As shown in FIG. 6, the second tubular walls 44 and 47 are provided with a flange 300 having the same shape as the first tubular walls 34 and 37 for joining with the plate portion 39 of the first heat transfer plate 30. . 1 to 4 and 7 show the second tubular walls 44 and 47 from which the flange 300 is omitted for easy understanding.

  As shown in FIGS. 5 and 7, in order to increase the heat exchange efficiency between the supplied first fluid and the second fluid, an intermediate portion in the X direction between the first heat transfer plate 30 and the second heat transfer plate 40 is provided. The first inner fin 38 and the second inner fin 48 are arranged, respectively. Although not shown in FIGS. 5 and 7, the first heat transfer plate 30 and the second heat transfer plate 40 have a first heat transfer plate 30 and a second heat transfer plate 40, in order to prevent the stacked body 100 from being deformed by the supplied first fluid and second fluid. The one convex part 50 and the second convex part 60 are provided, respectively. Next, the first inner fin 38, the second inner fin 48, the first protrusion 50, and the second protrusion 60 will be described.

FIG. 8 is an enlarged plan view of an end of the first heat transfer plate 30. FIG. 9 is a perspective view of the IX region shown in FIG. FIG. 10 is an enlarged plan view of an end portion of the second heat transfer plate 40. FIG. 11 is an enlarged plan view showing the positions of the first convex portion 50 and the second convex portion 60.
Note that FIG. 9A is a perspective view of the first protrusion 50 when viewed from the front, and FIG. 9B is a perspective view of the first protrusion 50 when viewed from the back.
As shown in FIGS. 8 and 10, the first inner fin 38 and the second inner fin 48 have corrugated fin portions that are uneven in the Z direction and extend in the X direction. Thereby, in the first inner fin 38 and the second inner fin 48, when the first fluid and the second fluid flow in the X direction, the first fluid and the second fluid flow along the fin portions. Heat of the first fluid and the second fluid is transmitted to the fin portions of the first inner fin 38 and the second inner fin 48, and as a result, the first fluid and the second fluid exchange heat.

  The above-described wavy fin portion is fixed to a rectangular substrate portion (not shown) of the first inner fin 38 and the second inner fin 48 as viewed in the XZ plane. Here, in the first inner fin 38, the length of the substrate portion in the short direction is equal to the first outer peripheral wall portion 31 at the + Z end of the first heat transfer plate 30 and the −Z end of the first heat transfer plate 30. It is the same as the distance from a certain first outer peripheral wall 31. The length in the longitudinal direction of the substrate portion is smaller than the distance between the first fluid outflow / inlet hole 32 and the first fluid outflow / inlet hole 35 in the X direction. In the second inner fin 48, the length of the substrate in the short direction is at the second outer peripheral wall 41 at the + Z end of the second heat transfer plate 40 and at the −Z end of the second heat transfer plate 40. The distance from the second outer peripheral wall portion 41 is the same. The length of the substrate portion in the longitudinal direction is smaller than the distance between the second fluid outflow / inflow hole 43 and the second fluid outflow / inflow hole 46 in the X direction. In the first inner fin 38 and the second inner fin 48, the short direction of the substrate portion is directed in the Z direction, and the long direction of the substrate portion is directed in the X direction.

  As shown in FIGS. 1 to 3, 5, 7, 8, and 10, the first inner fin 38 and the second inner fin 48 are formed by + Y of the first heat transfer plate 30 and the second heat transfer plate 40. On the surface. The + X ends of the first inner fin 38 and the second inner fin 48 are separated from the first fluid inflow / outflow hole 32 and the second fluid outflow / inflow hole 43 to facilitate the inflow and outflow of the first fluid and the second fluid. I have. Thereby, the first fluid and the second fluid spread in the Z direction when going from the first fluid outflow / inflow hole 32 and the second fluid outflow / inflow hole 43 to the first inner fin 38 and the second inner fin 48 side. Cheap. As a result, the first fluid and the second fluid easily flow uniformly in the entire Z direction of the first inner fin 38 and the second inner fin 48. In addition, since there is a space in which the first inner fin 38 and the second inner fin 48 are not arranged over the entire circumference of the first fluid outflow / inflow hole 32 and the second fluid outflow / inflow hole 43, the first fluid, The second fluid tends to spread around the first fluid outflow / inflow holes 32 and the second fluid outflow / inflow holes 43.

The −X ends of the first inner fin 38 and the second inner fin 48 are separated from the first fluid outflow / inlet 35 and the second fluid outflow / inlet 46. Therefore, the first fluid outflow / inlet hole 35 and the second fluid outflow / inlet hole 46 also have a space in which the first inner fin 38 and the second inner fin 48 are not arranged over the entire circumference. Thereby, the first fluid and the second fluid easily flow from the first inner fin 38 and the second inner fin 48 into the first fluid outflow / inlet 35 and the second fluid outflow / inlet 46.
The distance between the first inner fin 38 and the first fluid outflow / inflow hole 35 and the distance between the second inner fin 48 and the second fluid outflow / inflow hole 46 are determined by the flow of the first fluid and the second fluid. In order to facilitate the diameter, it is desirable that the diameter is 1/20 to 1/4 with respect to the diameter of the first fluid outflow / inlet 35 and the second fluid outflow / inlet 46. More preferably, these distances are 1/16 to 1/8 of the diameter of the first fluid outflow / inlet 35 and the second fluid outflow / inlet 46. Further, these distances may be larger than the pitch in the X direction of the waves of the wavy fins of the first inner fin 38 and the second inner fin 48 or the pitch of the fins adjacent in the Z direction. More preferably, the pitch is 1.5 to 2.0 times these pitches. The same applies to the distance between the first inner fin 38 and the first fluid outflow / inflow hole 32 and the distance between the second inner fin 48 and the second fluid outflow / inflow hole 43.

  No structure is provided between the first inner fin 38 and the first fluid outflow / inlet 35 and between the second inner fin 48 and the second fluid outflow / inlet 46. Further, no structure is provided between the first inner fin 38 and the first fluid outflow / inlet hole 32 and also between the second inner fin 48 and the second fluid outflow / inlet hole 43. For this reason, the strength of the laminated body 100 is partially weak and easily deformed. Therefore, between the inner fins and the outflow / inflow holes, in order to maintain the shape of the laminated body 100 and to maintain a state in which the first fluid and the second fluid flow smoothly, The second convex part 60 is arranged.

  In addition, the first convex portion 50 disposed between the first inner fin 38 and the first fluid outflow / inlet 35 is the first convex portion 50 disposed between the first inner fin 38 and the first fluid outflow / inlet 32. The same configuration as the one convex portion 50 is provided. In addition, the second convex portion 60 disposed between the second inner fin 48 and the second fluid outflow / inlet hole 46 has a second convex portion 60 disposed between the second inner fin 48 and the second fluid outflow / inlet hole 43. It has the same configuration as the biconvex portion 60. Therefore, hereinafter, the first convex portion 50 disposed between the first inner fin 38 and the first fluid outflow / inlet hole 32 and the second convex portion 50 disposed between the second inner fin 48 and the second fluid outflow / inlet hole 43 will be described. A description will be given by taking the arranged second convex portion 60 as an example.

  As shown in FIG. 8, a plurality of first protrusions 50 are arranged in a region of the first inner fin 38 on the side of the first fluid outflow / inlet hole 32, that is, in a region on the first heat transfer plate 30 on the + X side. ing. The arrangement of each of the first protrusions 50 is random in order to diffuse the flow of the first fluid. Each of the first convex portions 50 protrudes from the + Y surface of the plate portion 39 of the first heat transfer plate 30 to the + Y side.

  As shown in FIG. 9, each of the first convex portions 50 is formed in a cylindrical shape whose front end, that is, the + Y end is closed. The diameter of the first convex portion 50 is 1/14 to 1/15 of the diameter of the first fluid inflow / outflow hole 32. The diameter of the first convex portion 50 is larger than the distance between the first inner fin 38 and the first fluid outflow / inlet hole 35 and the distance between the second inner fin 48 and the second fluid outflow / inlet hole 46. Preferably, it is small, in particular 2/3 to 1/3 of these distances. The first convex portion 50 is in a state where the first heat transfer plate 30 and the second heat transfer plate 40 form the laminated body 100 (hereinafter, referred to as a state in which the laminated body 100 is formed), and the + Y end is the second The heat transfer plate 40 is formed at a height in contact with the −Y surface. Thereby, the first convex portion 50 serves as a support between the second heat transfer plate 40 and the first heat transfer plate 30 in a state where the stacked body 100 is formed, and has a shape of a flow path through which the first fluid flows. Have maintained.

  Further, as shown in FIG. 10, a plurality of second convex portions 60 are provided in the region of the second inner fin 48 on the side of the second fluid outflow / inlet hole 43, that is, in the + X side region on the second heat transfer plate 40. Are located. Although not shown, the + Y end of the second convex portion 60 abuts on the −Y surface of the first heat transfer plate 30 in a state where the first heat transfer plate 30 and the second heat transfer plate 40 form the stacked body 100. It is formed at the height. Thereby, the second convex portion 60 serves as a support between the first heat transfer plate 30 and the second heat transfer plate 40 in a state where the laminate 100 is formed, and has a shape of a flow path through which the second fluid flows. Have maintained. Then, as shown in FIG. 11, the second convex portion 60 is shifted from the first convex portion 50 in a position where the second convex portion 60 does not overlap with the first convex portion 50 when viewed in the Y direction, that is, shifted from the first convex portion 50 in a state where the laminate 100 is formed. It is randomly arranged in the position.

  Next, the flow of the first fluid and the second fluid in the plate heat exchanger 1 will be described with reference to FIG. In the following description, the first fluid and the second fluid are connected to the plate heat exchanger 1 so that the first fluid and the second fluid are connected to the first fluid supply pipe. 12, it is supplied to the second fluid supply pipe 13. Further, by connecting the connection pipes for discharging the first fluid and the second fluid to the plate heat exchanger 1, the first fluid and the second fluid after the heat exchange can be connected to the first fluid discharge pipe 14 and the second fluid. It shall be discharged from the two-fluid discharge pipe 15. In the following description, FIG. 1 will be referred to as needed.

FIG. 12 is a cross-sectional view of the first fluid supply pipe 12, the first fluid inflow / outflow hole 32, and the second passage hole.
First, the flow of the first fluid will be described. The first fluid is supplied from outside to the laminate 100 via the first fluid supply pipe 12. The supplied first fluid passes through the second passage hole 42 of the second heat transfer plate 40 and the first fluid outflow / inlet hole 32 of the first heat transfer plate 30, as shown in FIG. It flows in the Y direction. Here, a second tubular wall 44 is formed in the second passage hole 42. On the other hand, the first fluid outflow / inflow hole 32 has no tubular wall surrounding the outer periphery. Therefore, the first fluid not only flows in the −Y direction, but also flows in the direction from the first fluid inflow / outflow hole 32 to the first inner fin 38 side (that is, the direction of arrow F1). Thereby, the first fluid flows along the + Y plane of the first heat transfer plate 30. On the + Y surface of the first heat transfer plate 30, a space is provided between the first fluid outflow / inflow hole 32 and the first inner fin 38, where only the first protrusion 50 exists. Therefore, the first fluid spreads from the first fluid inflow / outflow holes 32 in the Z direction to the entire first heat transfer plate 30 in this space, and flows into the first inner fins 38 with a uniform distribution.

  The first fluid flowing into the first inner fin 38 exchanges heat with the first inner fin 38. After the heat exchange, the first fluid flows to the first fluid outlet / inlet 35 side of the first heat transfer plate 30 (not shown). In the vicinity of the first fluid inflow / outflow hole 35, there is provided a space between the first inner fin 38 and only the first protrusion 50. Therefore, in this space, the pressure loss of the first fluid is small. As a result, the first fluid smoothly flows to the first fluid outflow / inlet 35 side. On the first fluid outlet / inlet 35 side, the −X end of the first heat transfer plate 30 is closed by the first outer peripheral wall 31. On the other hand, a part of the plate surface of the first heat transfer plate 30 is opened by the first fluid inflow / outflow hole 35. Therefore, the first fluid flows through the first fluid outflow / inlet 35 toward the first fluid discharge pipe 14. That is, the first fluid flows to the second passage hole 45 of the second heat transfer plate 40 located on the + Y side. Then, the first fluid flows into the first fluid discharge pipe 14 through the second passage hole 45 and is discharged to the outside.

  Next, the flow of the second fluid will be described. The second fluid is supplied to the multilayer body 100 from the outside via the second fluid supply pipe 13 as shown by an arrow S in FIG. The supplied second fluid flows in the −Y direction through the second fluid outflow / inlet hole 43 of the second heat transfer plate 40 and the first passage hole 33 of the first heat transfer plate 30. Here, a first tubular wall 34 is formed in the first passage hole 33. On the other hand, the second fluid inflow / outflow hole 43 does not have a tubular wall surrounding the outer periphery. Therefore, the second fluid not only flows in the −Y direction, but also flows from the second fluid inflow / outflow hole 43 to the second inner fin 48 side. Then, the second fluid flows along the + Y plane of the second heat transfer plate 40 and flows into the second inner fin 48.

  The second fluid flowing into the second inner fin 48 exchanges heat with the second inner fin 48. Thereafter, the second fluid flows from the second inner fin 48 to the second fluid inflow / outflow port 46 side. A space is provided between the second inner fin 48 and the second fluid inflow / outflow hole 46, in which only the second convex portion 60 is present. It flows to the hole 46 side. On the second fluid inflow / outflow hole 46 side, the + Y end of the second heat transfer plate 40 is closed by the second outer peripheral wall portion 41. On the other hand, a part of the plate surface of the second heat transfer plate 40 is opened by the second fluid inflow / outflow hole 46. Therefore, the second fluid flows toward the second fluid discharge pipe 15 via the second fluid inflow / outflow hole 46. That is, the second fluid flows to the first passage hole 36 of the first heat transfer plate 30 on the + Y side or the second fluid discharge pipe 15 on the + Y side. Then, the second fluid is discharged to the outside through the second fluid discharge pipe 15.

  The heat transmitted to the first inner fin 38 and the second inner fin 48 is transmitted to the first heat transfer plate 30 and the second heat transfer plate 40. Since the first heat transfer plate 30 and the second heat transfer plate 40 are alternately stacked, the heat transferred to the first heat transfer plate 30 and the second heat transfer plate 40 is Heat exchange is performed between the two heat transfer plates 40. As a result, heat exchange between the first fluid and the second fluid is performed in the plate heat exchanger 1.

  As described above, in the plate heat exchanger 1 according to Embodiment 1 of the present invention, the first inner fin 38 is separated from the first fluid outflow / inflow holes 32, 35. Further, the second inner fin 48 is separated from the second fluid inflow / outflow holes 43 and 46. The entire circumference of the first fluid outflow / inlet holes 32 and 35 and the second fluid outflow / inlet holes 43 and 46 is in contact with a space where the first inner fin 38 and the second inner fin 48 are not provided. For this reason, in the space between the first inner fin 38 and the first fluid inflow / outflow holes 32 and 35, the first fluid spreads over the entire first inner fin 38, and the first fluid flows in the first inner fin 38. There is no one-sided flow. In the space between the second inner fin 48 and the second fluid inflow / outflow holes 43 and 46, the second fluid spreads over the entire second inner fin 48, and the second fluid flows through the second inner fin 48. There is no one-sided flow. As a result, in the plate heat exchanger 1, the pressure loss of the first fluid and the second fluid is small.

  A first convex portion 50 is provided between the first inner fin 38 and the first fluid outflow / inlet holes 32 and 35. Further, between the second inner fin 48 and the second fluid inflow / outflow holes 43 and 46, a second projection 60 is provided at a position shifted from the first projection 50 in the Y direction. For this reason, in the plate heat exchanger 1, the stacked body 100 is less likely to be deformed by the pressure of the first fluid and the second fluid. As a result, it is possible to prevent the laminate 100 from deforming and increasing the pressure loss. Further, the first convex portion 50 and the second convex portion 60 are provided at positions shifted from each other when viewed in the Y direction. For this reason, the first heat transfer plate 30 and the second heat transfer plate 40 are reinforced by the first protrusion 50 and the second protrusion 60 at portions different from each other when viewed in the Y direction. As a result, the strength of the plate heat exchanger 1 can be further increased as compared with the case where the same number of the first convex portions 50 and the second convex portions 60 are provided at the same position in the Y direction. More specifically, the first convex portion 50 and the second convex portion 60 are viewed in the Y direction as compared with the case where the first convex portion 50 and the second convex portion 60 are arranged at the same position in the Y direction or at the overlapping position. In the case of displacing them with each other, it is possible to secure a necessary pressure resistance according to the pressure of the flowing fluid. In addition, since the pressure resistance can be ensured with a small number of the first protrusions 50 and the second protrusions 60, the pressure loss of the fluid due to the first protrusions 50 and the second protrusions 60 can be suppressed. It is possible.

  Flanges 300 are provided on the first tubular walls 34 and 37 and the second tubular walls 44 and 47. For this reason, by joining the flange 300 to the plate surfaces of the first heat transfer plate 30 and the second heat transfer plate 40, the bonding strength between the first tubular walls 34 and 37 and the second heat transfer plate 40, and The joint strength between the two tubular walls 44 and 47 and the first heat transfer plate 30 can be increased. As a result, it is possible to prevent the first fluid from leaking from the joint and entering the second flow path and the second fluid from leaking from the joint and entering the first flow path.

  Further, by brazing the first outer peripheral wall portion 31 of the first heat transfer plate 30 and the second outer peripheral wall portion 41 of the second heat transfer plate 40, the first fluid and the second fluid leak to the outside. Is prevented. Further, the strength of the laminate 100 is increased.

(Embodiment 2)
In the plate heat exchanger 1 according to Embodiment 1, the first protrusion 51 is provided near the first fluid outflow / inflow hole 32 and the first passage hole 33. Further, a second convex portion 61 is provided near the second fluid inflow / outflow hole 43 and the second passage hole 42. On the other hand, in the plate heat exchanger 2 according to the second embodiment, the first convex portion 51 is provided only near the first fluid outflow / inflow hole 32. Further, the second convex portion 61 is provided only near the second fluid outflow / inlet hole 43. Hereinafter, the plate heat exchanger 2 according to the second embodiment will be described with reference to FIGS. 13 to 16. In the second embodiment, a configuration different from the first embodiment will be described.

FIG. 13 is an enlarged plan view of an end of the first heat transfer plate 30 included in the plate heat exchanger 2 according to Embodiment 2 of the present invention. FIG. 14 is an enlarged plan view of an end of the second heat transfer plate 40 provided in the plate heat exchanger 2 according to Embodiment 2 of the present invention. FIG. 15 is an enlarged plan view illustrating a positional relationship between the first convex portion 51 and the second convex portion 61 in the plate heat exchanger 2 according to Embodiment 2 of the present invention.
As shown in FIG. 13, the first protrusion 51 is formed only on the + X side and + Z side of the first heat transfer plate 30 where the first fluid outflow / inlet holes 32 are formed. A plurality of first convex portions 51 are randomly arranged in the area. The shape and size of each of the first protrusions 51 are the same as those of the first protrusion 50 of the first embodiment.

  On the other hand, as shown in FIG. 14, the second convex portion 61 is formed only in the + X side and the −Z side region of the second heat transfer plate 40 where the second fluid outflow / inlet hole 43 is formed. . A plurality of second convex portions 61 are also arranged in the area. The shape and size of each of the second protrusions 61 are the same as those of the second protrusion 60 of the first embodiment. The arrangement of each of the second convex portions 61 is random. However, in the state where the stacked body 100 is formed, the second convex portion 61 is arranged at a position that does not overlap with the first convex portion 51 as viewed in the Y direction, as shown in FIG.

  Although not shown, the first convex portions 51 are also randomly arranged in a region of the first heat transfer plate 30 on the −X side and the + Z side where the first fluid outflow / inlet holes 35 are formed. The second convex portions 61 are also randomly arranged in a region of the second heat transfer plate 40 on the −X side and the −Z side where the second fluid outflow / inlet holes 46 are formed. And the 2nd convex part 61 is arrange | positioned at the position which does not overlap with the 1st convex part 51 in the Y direction view in the state which the laminated body 100 was formed.

  Next, the operation of the first convex portion 51 and the second convex portion 61 in the plate heat exchanger 2 will be described with reference to FIG. FIG. 16 is a conceptual cross-sectional view of the first fluid supply pipe 12 and the second fluid supply pipe 13 of the plate heat exchanger 2 according to Embodiment 2 of the present invention. In the following description, as in the first embodiment, the first fluid supply pipe 12 and the second fluid supply pipe 13 have connection pipes for supplying the first fluid and the second fluid to be heat-exchanged. It is assumed that they are connected.

  As shown in FIG. 16, when the first fluid is supplied from the first fluid supply pipe 12 and the first fluid flows as shown by the arrow F, the first fluid is formed on the first heat transfer plate 30 by the flow of the first fluid. Pressure is applied in the first flow path. On the other hand, when the second fluid is supplied from the second fluid supply pipe 13 and the second fluid flows as shown by the arrow S, pressure is applied to the second flow path formed in the second heat transfer plate 40.

  At this time, the pressure resistance of the first flow path is high near the first fluid outflow / inflow hole 32 because the first convex portion 51 is provided near the first fluid outflow / inflow hole 32, and as a result, the deformation Hard to do. On the other hand, the first convex portion 51 is not provided in the vicinity of the first passage hole 33 in the first flow passage, but the vicinity of the second fluid inflow / outflow hole 43 in the second flow passage adjacent to the first flow passage in the Y direction. Is provided with a second convex portion 61. Since it is supported by the second convex portion 61, the vicinity of the first passage hole 33 in the first flow passage is not easily deformed. Thereby, the first fluid flows through the first fluid outflow / inflow holes 32 smoothly without being hindered by the deformation of the first heat transfer plate 30. Further, since the first convex portion 51 is not provided near the first passage hole 33, the first fluid flows from the first fluid outflow / inlet hole 32 to the first passage hole in comparison with the case of the first embodiment. It is easier to flow near 33. Thereby, the first fluid easily spreads to the −Z side in the first heat transfer plate 30. The first fluid flows with the flow rate of the first heat transfer plate 30 in the Z direction being more uniform.

In addition, the pressure resistance of the second flow path is high near the second fluid outflow / inlet hole 43 because the second convex portion 61 is provided in the vicinity of the second fluid outflow / inlet hole 43. Hard to do. On the other hand, although the second convex portion 61 is not provided near the second passage hole 42 in the second flow passage, the first fluid outflow / inflow hole 32 in the first flow passage adjacent to the second flow passage in the Y direction is provided. A first convex portion 51 is provided in the vicinity. Since it is supported by the first convex portion 51, the vicinity of the second passage hole 42 in the second flow passage is also hardly deformed. Thereby, the second fluid flows through the second fluid inflow / outflow hole 43 smoothly without being hindered by the deformation of the second heat transfer plate 40. Since the second convex portion 61 is not provided in the vicinity of the second passage hole 42, the second fluid flows from the second fluid outflow / inlet hole 43 to the vicinity of the second passage hole 42 as compared with the first embodiment. , It is easy to flow, and easily spreads to the −Z side in the second heat transfer plate 40. The second fluid flows in a state where the flow rate of the second heat transfer plate 40 in the Z direction is more uniform.
Note that a first convex portion 51 is also provided near the first fluid outflow / inlet hole 35 of the first heat transfer plate 30 (not shown). The second convex portion 61 is also provided near the second fluid outflow / inlet hole 46 of the second heat transfer plate 40. Therefore, the stacked body 100 is similarly unlikely to be deformed near the first fluid outflow / inlet 35 and the second fluid outflow / inlet 46, and the first fluid and the second fluid flow smoothly.

  As described above, in the plate heat exchanger 2 according to Embodiment 2 of the present invention, the first protrusion 51 is not provided near the first passage hole 33. However, since the second convex portion 61 is provided near the adjacent second fluid inflow / outflow hole 43, the deformation of the stacked body 100 can be prevented by the small number of first convex portions 51. Further, the second convex portion 61 is not provided in the vicinity of the second passage hole 42, but the first convex portion 51 is provided in the vicinity of the adjacent first fluid outflow / inlet hole 32, so that a small number of second convex portions 61 are provided. The protrusions 61 can prevent the laminate 100 from being deformed. As a result, it is possible to prevent the flow of the first fluid and the second fluid from being hindered by the deformation of the laminate 100.

(Embodiment 3)
In the plate heat exchanger 1 according to Embodiment 1, the first heat transfer plate 30 is provided with the first protrusion 50. Further, the second heat transfer plate 40 is provided with a second convex portion 60. On the other hand, in the plate heat exchanger 3 according to the third embodiment, the first convex portion 52 and the second convex portion 62 are provided on the second heat transfer plate 40. Hereinafter, the plate heat exchanger 3 according to the third embodiment will be described with reference to FIGS. In the third embodiment, a configuration different from the first and second embodiments will be described.

FIG. 17 is an enlarged plan view of an end portion of the second heat transfer plate 40. FIG. 18 is a conceptual sectional view of the first fluid supply pipe 12 and the second fluid supply pipe 13. In FIG. 17, the depression is hatched to indicate that the first projection 52 is a depression.
As shown in FIG. 17, the second heat transfer plate 40 includes a plurality of second protrusions 62 protruding in the + Y direction and a plurality of first protrusions protruding in the −Y direction by the same height as the first flow path. 52. Then, each of the second convex portion 62 and the first convex portion 52 is arranged at a position that does not overlap in the Y direction. Further, the second convex portion 62 and the first convex portion 52 are arranged in a region on the + X side of the second inner fin 48 in the second heat transfer plate 40. Specifically, the second convex portion 62 and the first convex portion 52 are arranged near the second passage hole 42 and near the second fluid outflow / inlet hole 43.

  As shown in FIG. 18, the + Y end of the second convex portion 62 is located on the + Y side with respect to the second heat transfer plate 40 having the second convex portion 62 in a state where the laminate 100 is formed. It is in contact with one reinforcing plate 10. Alternatively, the + Y end of the second convex portion 62 is in contact with the first heat transfer plate 30 located on the + Y side with respect to the second heat transfer plate 40 having the second convex portion 62. Thereby, the second convex portion 62 functions as a support between the second heat transfer plate 40 and the first reinforcing plate 10 or between the second heat transfer plate 40 and the first heat transfer plate 30. .

  On the other hand, the −Y end of the first convex portion 52 is in contact with the first heat transfer plate 30 located on the −Y side with respect to the second heat transfer plate 40 having the first convex portion 52. Thereby, the first convex portion 52 functions as a support between the second heat transfer plate 40 and the first heat transfer plate 30.

  Although not shown, the second heat transfer plate 40 is also provided in a region on the −X side of the second inner fin 48, that is, in the second heat transfer plate 40, the second passage hole 45 and the second fluid inflow / outflow. The region on the hole 46 side also has a second convex portion 62 and a first convex portion 52 that function as columns.

  As described above, in the plate heat exchanger 3 according to Embodiment 3 of the present invention, the second heat transfer plate 40 has the second convex portion 62 protruding in the + Y direction and the first convex portion 62 protruding in the −Y direction. The projection 52 is provided. Since the second convex portion 62 and the first convex portion 52 function as columns, the strength of the laminate 100 is high. As a result, it is possible to prevent the laminate 100 from being deformed and the first fluid and the second fluid from being difficult to flow. With the configuration of the third embodiment, neither the first protrusion 52 nor the second protrusion 62 is provided on the first heat transfer plate 30, so that the processing cost of the first heat transfer plate is reduced. It is possible. As a result, the cost of the plate heat exchanger 3 can be reduced.

(Embodiment 4)
In the plate heat exchanger 4 according to the fourth embodiment, the first heat transfer plate 30 includes a first convex portion 52 and a second convex portion having the same shape as the second heat transfer plate 40 described in the third embodiment. A part 62 is provided. Hereinafter, the plate heat exchanger 4 according to the fourth embodiment will be described with reference to FIG. In the fourth embodiment, a configuration different from the first to third embodiments will be described.

FIG. 19 is an enlarged cross-sectional view of the laminate 100.
As shown in FIG. 19, the first heat transfer plate 30 includes a second protrusion 62 protruding from the plate surface in the + Y direction and a first protrusion 52 protruding from the plate surface in the -Y direction. . The second convex portion 62 and the first convex portion 52 protrude from the plate surface by the same distance. Further, the second heat transfer plate 40 also includes a second convex portion 62 and a first convex portion 52 having the same shape. And the 2nd convex part 62 which the 1st heat transfer plate 30 has, and the 1st convex part 52 which the 2nd heat transfer plate 40 has are formed in the position which overlaps in the Y direction. The + Y end of the second convex portion 62 of the first heat transfer plate 30 and the first convex portion 52-Y end of the second heat transfer plate 40 are in contact with each other and are brazed. Thereby, the second convex portion 62 of the first heat transfer plate 30 and the first convex portion 52 of the second heat transfer plate 40 function as a support of the stacked body 100.

  Although not shown, also in the fourth embodiment, similarly to the third embodiment, the first convex portion 52 and the second convex portion 62 are located on the + X side of the first heat transfer plate 30 with respect to the first inner fin 38. It is arranged in a certain area and an area on the −X side of the first inner fin 38. Further, the first convex portion 52 and the second convex portion 62 are located in a region of the second heat transfer plate 40 on the + X side with respect to the second inner fin 48 and a region on the −X side with respect to the second inner fin 48. Are located.

  As described above, in the plate heat exchanger 4 according to Embodiment 4 of the present invention, the second convex portion 62 of the first heat transfer plate 30 and the first convex portion 52 of the second heat transfer plate 40 are formed. It functions as a support for the laminate 100. For this reason, the second protrusion 62 and the first protrusion 52 can prevent the laminate 100 from being deformed. As a result, the flow of the first fluid and the second fluid is maintained in the plate heat exchanger 4.

  Further, the first convex portion 52 and the second convex portion 62 provided in the plate heat exchanger 4 are more convex portions than the convex portions provided in the plate heat exchanger 1-3 according to Embodiment 1-3. Can be halved in height. For this reason, the forming of the first convex portion 52 and the second convex portion 62 is easy, and the thickness of the first heat transfer plate 30 and the second heat transfer plate 40 can be reduced.

(Embodiment 5)
Embodiment 5 is a heat pump hot water supply system 5 using the plate heat exchanger 1 according to Embodiment 1. Referring to FIG. 20, a heat pump hot water supply system 5 according to Embodiment 5 will be described.

FIG. 20 is a block diagram of the heat pump hot water supply system 5.
As shown in FIG. 20, the heat pump hot water supply system 5 includes a refrigerant circuit 80 and a water circuit 90 that performs heat exchange with the refrigerant circuit 80.

  The refrigerant circuit 80 includes a compressor 81 for compressing the refrigerant, a plate heat exchanger 1 for exchanging the refrigerant with water in the water circuit 90, an expansion valve 82, and a refrigerant expanded by the expansion valve 82, which is heated by the outside air. And a heat exchanger 83 to be exchanged. In the refrigerant circuit 80, the compressor 81, the plate heat exchanger 1, the expansion valve 82, and the heat exchanger 83 are connected in this order.

  On the other hand, the water circuit 90 includes a pump 91 for circulating water and a heating / hot-water supply water utilization device 92. The water circuit 90 is connected to the plate heat exchanger 1. In detail, the water circuit 90 includes a heating / hot water supply water utilization device 92, a pump 91, and the plate heat exchanger 1. The heating / hot-water supply water use device 92, the pump 91, and the plate heat exchanger 1 are connected in this order to form a closed circuit.

  As described above, the heat pump hot water supply system 5 according to Embodiment 5 includes the plate heat exchanger 1. Therefore, the pressure loss of the refrigerant and water is small, and the heat exchange efficiency is high.

(Embodiment 6)
Embodiment 6 A plate heat exchanger 6 according to Embodiment 6 will be described with reference to FIGS. In the sixth embodiment, a configuration different from the first to fifth embodiments will be described.

  First, returning to FIG. 20, the flow in the plate heat exchanger 6 will be described in detail. In the present embodiment, it is assumed that the first fluid is a refrigerant and the second fluid is water. When heating with the heat pump hot water supply system 5, the first fluid flows from the compressor 81 into the inlet of the plate heat exchanger 6 in a single-phase state of high-temperature and high-pressure gas, and the first inner fins 38 (both fin portions). ) To form a two-phase state in which a gas phase and a liquid phase coexist. After the first fluid is completely liquefied, the first fluid flows out of the outlet hole (also referred to as a header) of the plate heat exchanger 6 in a high-pressure liquid single-phase state, and returns to the compressor 81 again to circulate. On the other hand, the second fluid is always in a liquid state, absorbs heat from the refrigerant as the first fluid, becomes hot water, is sent into the room, and heats the room. In the case of cooling with the heat pump hot water supply system 5, the flow in the refrigerant circuit 80 is reversed by a four-way valve, not shown. The first fluid flows from the expansion valve 82 into the outlet of the plate heat exchanger 6 in a low-pressure two-phase state, and is evaporated and absorbed by the first inner fins 38 to be in a two-phase state in which the ratio of the gas phase is increased. . After the first fluid is completely gasified, the first fluid flows out of the inlet of the plate heat exchanger 6 in a gas single-phase state. On the other hand, the second fluid is always in a liquid state, and after exchanging heat with the first fluid, water is sent into the room to cool the room. In this way, on the second fluid side, both the header portion and the fin portion are always in a liquid single-phase state, whereas on the first fluid side, when heating, the inlet / outlet header portion is in a gas and liquid single-phase state, and is cooled. In some cases, the inlet (outlet for cooling flow) header is in a single-phase gas state, and the outlet (inlet) header is in a two-phase state with a large liquid volume ratio. In general, the pressure loss in the gas and liquid single-phase state (including the two-phase state with a large liquid ratio) is smaller than the two-phase state even if the flow path shape is the same. The pressure loss at the header is relatively small. For this reason, when newly adding a flow path resistance to the entrance / exit header portion, the influence on the pressure loss increase of the entire plate type heat exchanger 6 is smaller on the first fluid side than on the second fluid side.

Subsequently, the configuration of the plate heat exchanger 6 will be described with reference to FIGS.
FIG. 21 is an enlarged plan view of an end of the first heat transfer plate 30 provided in the plate heat exchanger 6 according to Embodiment 6 of the present invention. FIG. 22 is an enlarged plan view of an end of the second heat transfer plate 40 provided in the plate heat exchanger 6 according to Embodiment 6 of the present invention. FIG. 23 is an enlarged plan view showing a positional relationship between the first convex portion 53 and the second convex portion 63 in the plate heat exchanger 6 according to Embodiment 6 of the present invention.
As shown in FIG. 21, a first convex portion 53 is provided near the first fluid inflow / outflow hole 32 and the first passage hole 33 at the + X end of the first heat transfer plate 30. Although not shown, the same number of first protrusions 53 are provided near the first fluid inflow / outflow hole 35 and the first passage hole 36 at the −X end of the first heat transfer plate 30.

  On the other hand, as shown in FIG. 22, near the second fluid inflow / outflow hole 43 and the second passage hole 42 at the + X end of the second heat transfer plate 40, the pressure loss increase due to the above-described flow passage resistance. In order to reduce the influence of the first convex portion 53, a smaller number of second convex portions 63 than the first convex portion 53 are provided. As shown in FIG. 23, the second convex portion 63 is disposed at a position shifted from the first convex portion 53 in the Y direction when the laminated body 100 is formed. Although not shown, the same number of second protrusions 63 are provided near the second passage hole 45 and the second fluid outflow / inflow hole 46 at the −X end of the second heat transfer plate 40.

  As described above, in the plate heat exchanger 6 according to Embodiment 6, dimples are concentrated on the first fluid side (a dimple generally means a depression, but a dimple shape here means (Referred to as the first convex portion 53 formed by the -Y surface of the heat transfer plate 30 being recessed to the + Y side), so that the influence of the deterioration of the performance of the entire heat pump hot water supply system 5 can be further reduced. Is possible. Further, in the case of the cooling operation, the first fluid flows into the outflow hole on the first fluid side (corresponding to the inflow hole at the time of the cooling operation) in a two-phase state of gas and liquid. As a result, the first fluid can be brought closer from the two-phase state to the single-layer state. For this reason, it is possible to suppress the gas-liquid fluid in the plate-type heat exchanger 6 from having an uneven distribution and to flow the gas-liquid fluid with a uniform distribution. As a result, the average heat transfer coefficient on the refrigerant side can be further improved as compared with the first embodiment.

  As described above, the embodiments of the present invention have been described, but the present invention is not limited to the above embodiments. For example, the tip of the flange 300 extends from the first tubular walls 34, 37 in the radial direction. However, the shape of the flange 300 is arbitrary as long as it can be joined to the first heat transfer plate 30 and the second heat transfer plate 40.

FIG. 24 is a cross-sectional view showing a modified example of the flanges of the first tubular walls 34 and 37. FIG. 25 is a cross-sectional view showing a modification of the first fluid supply pipe 12, the first fluid inflow / outflow hole 32, and the second passage hole.
As shown in FIGS. 24 and 25, the flange 301 may extend from the + Y end of the first tubular wall 34, 37 to the inside of the first passage hole 33, 36. Although not shown, the flange 301 may also be provided on the second tubular walls 44, 47. In this case, the flange 301 provided on the second tubular walls 44, 47 may extend from the + Y end of the second tubular walls 44, 47 to the inside of the second passage holes 42, 45. Note that the flanges 300 and 301 provided on the first heat transfer plate 30 may be referred to as a first flange, and the one provided on the second heat transfer plate 40 may be referred to as a second flange.

  In Embodiment 1-5, the first inner fin 38 and the second inner fin 48 are formed in a shape having irregularities in the Z direction and having wavy fin portions extending in the X direction. However, in the present invention, the first inner fin 38 and the second inner fin 48 are not limited to this. The shape of the fin portion is arbitrary.

  FIG. 26 shows the first inner fins 38 arranged on the first heat transfer plate 30 included in the plate heat exchanger 1 according to Embodiment 1 of the present invention, and the second inner fins 38 arranged on the second heat transfer plate 40. FIG. 4 is a perspective view of an inner fin 48. FIGS. 26A to 26F show offset fins, flat fins, corrugated fins, louver fins, corrugated fins, and pin fins, respectively.

  As shown in FIG. 26, the fin portions of the first inner fin 38 and the second inner fin 48 may be offset fins in which the inner walls of the groove shown in FIG. Further, the fin portion may be a flat fin in which a plurality of flat plates shown in FIG. 26B are arranged in parallel. The fin portion may be a corrugated fin having a wave shape in plan view, a louver-type fin, or a corrugated fin having a cross-sectional shape as shown in FIGS. A so-called pin-type fin in which pins are arranged in a grid pattern as shown in FIG.

  In Embodiment 1-5, the first convex portions 50-53 and the second convex portions 60-63 are cylindrical. However, in the present invention, if the first convex portions 50-53 and the second convex portions 60-63 are formed in convex shapes protruding from the plate surfaces of the first heat transfer plate 30 and the second heat transfer plate 40, respectively. The shapes of the first projections 50-53 and the second projections 60-63 are arbitrary.

  FIG. 27 is a rear view of the X region shown in FIG. FIG. 27A is a perspective view of the first protrusion 50 described in Embodiment 1 when viewed from the back. FIGS. 27B to 27F respectively show wedge-shaped, elliptical, triangular, quadrangular, and arc-shaped first convex portions 50 as viewed in the Y direction.

  As shown in FIGS. 27B to 27F, the first convex portion 50 may be formed in a wedge shape, an elliptical shape, a triangular shape, a rectangular shape, or an arc shape when viewed in the Y direction. Although not shown, the first convex portions 51-53 and the second convex portions 60-63 may also be formed in a wedge shape, an elliptical shape, a triangular shape, a rectangular shape, and an arc shape when viewed in the Y direction. When the first protrusions 50-53 and the second protrusions 60-63 are wedge-shaped as shown in FIG. 27B, the tips of the wedges may be directed in the direction in which the first fluid and the second fluid flow. In this case, the pressure loss of the first fluid and the second fluid can be further reduced.

  In the first embodiment, the diameter of the first protrusion 50 and the second protrusion 60 is 1/14 to 1/15 of the diameter of the first fluid outflow / inflow hole 32. However, the present invention is not limited to this, and the size of the first protrusion 50 and the second protrusion 60 is arbitrary. Further, the sizes of the first convex portions 51-53 and the second convex portions 61-63 are also arbitrary.

FIG. 28 is a plan view showing a modification of the first convex portion 50 included in the plate heat exchanger 1 according to Embodiment 1 of the present invention. FIG. 29 is an enlarged plan view showing another modified example of the first convex portion 50 included in the plate heat exchanger 1 according to Embodiment 1 of the present invention.
As shown in FIG. 28, the diameter of the first convex portion 50 may be larger than that in the first embodiment. In this case, the number of the first convex portions 50 may be smaller than that in the first embodiment. Conversely, as shown in FIG. 29, the diameter of the first protrusion 50 may be smaller than in the first embodiment. In this case, the number of the first protrusions 50 may be larger than in the first embodiment. In this manner, the size of the first protrusions 50 in the Y direction, that is, the area in the Y direction, may be changed depending on the number thereof. The number and area of the first protrusions 50 may be determined according to the required pressure resistance of the laminate 100. This is the same for the first convex portions 51-53 and the second convex portions 60-63.

  In the fifth embodiment, the plate heat exchanger 1 is used for the heat pump hot water supply system 5. However, the present invention is not limited to this. The plate heat exchanger 1-4 can be applied to a cooling chiller. In addition, the plate heat exchanger 1-4 can be used for industrial and household equipment such as a power generator and a food heat sterilization apparatus. By using the plate heat exchanger 1-4 for such a device, the heat exchange efficiency can be increased.

  The present invention is capable of various embodiments and modifications without departing from the broad spirit and scope of the invention. Further, the above-described embodiments are for describing the present invention, and do not limit the scope of the present invention. That is, the scope of the present invention is shown not by the embodiment but by the claims. Various modifications made within the scope of the claims and the equivalents of the invention are considered to be within the scope of the present invention.

  This application is based on Japanese Patent Application No. 2017-101390 filed on May 23, 2017. The specification, claims, and drawings of Japanese Patent Application No. 2017-101390 are incorporated herein by reference.

  1-4, 6-plate heat exchanger, 5 heat pump hot water supply system, 10 first reinforcing plate, 11 first reinforcing outer peripheral wall, 12 first fluid supply pipe, 13 second fluid supply pipe, 14 first fluid discharge Pipe, 15 second fluid discharge pipe, 20 second reinforcing plate, 21 second reinforcing outer peripheral wall, 30 first heat transfer plate, 31 first outer peripheral wall, 32 first fluid outflow / inlet hole, 33 first passage hole , 34 first tubular wall, 35 first fluid outflow / inlet hole, 36 first passage hole, 37 first tubular wall, 38 first inner fin, 39 plate portion, 40 second heat transfer plate, 41 second outer peripheral wall portion , 42 second passage hole, 43 second fluid inflow / outflow hole, 44 second tubular wall, 45 second passage hole, 46 second fluid inflow / outflow hole, 47 second tubular wall, 48 second inner fin, 49 plate portion , 50-53 first convex portion, 0-63 second convex portion, 80 refrigerant circuit, 81 compressor, 82 expansion valve, 83 heat exchanger, 90 water circuit, 91 pump, 92 heating and hot water supply water utilization device, 100 laminate, 300, 301 flange, F, F1, S arrow.

In order to achieve the above object, the plate heat exchanger according to the present invention has a first plate portion in which a first outflow / inflow hole for inflow / outflow of the first fluid is formed, on one surface side of the first plate portion. the first outer peripheral wall portion forming a first flow path for passing the first fluid surrounding the outer periphery of the first plate and, on one surface of the first plate, the first outlet in hole in the first flow path second plate portion first inner fins placed at a position spaced a first heat transfer plate having a, a second inflow and outflow hole for and out flow of the second fluid is formed from the second plate portion A second outer peripheral wall portion surrounding the outer periphery of the second plate portion on one surface side to form a second flow passage for flowing the second fluid, and a second flow passage on one surface of the second plate portion. a second heat transfer plate having a second inner fin, which is placed at a position spaced from the second inflow and outflow hole of the inner, but Several sheets, are alternately stacked. The second plate portion protrudes on one surface side, abuts the first plate portion of the first heat transfer plate adjacent to the one surface side, and the second flow passage has a second outflow / inflow hole. The first convex portion disposed between the inner fins, and protruding on the other surface side, abuts the first plate portion of the first heat transfer plate adjacent to the other surface side, and of the first flow path, a second projecting portion disposed between the first inflow and outflow hole to the first inner fin, that have a.

According to the configuration of the present invention, the first inner fin is placed on one surface of the first plate portion at a position separated from the first outflow / inflow hole in the first flow path . Therefore, the first fluid is spread across the first flow path between the first inflow and outflow hole to the first inner fin. As a result, the pressure loss of the first fluid is small. The second inner fin is placed on one surface of the second plate portion at a position separated from the second inflow / outflow hole in the second flow path. For this reason, the second fluid spreads over the entire second flow path from the second outflow / inflow hole to the second inner fin. As a result, the pressure loss of the second fluid is small. Thus, the heat exchange efficiency of the plate heat exchanger is not high. Further, since the first convex portion is disposed between the second outflow / inlet hole and the second inner fin, and the second convex portion is disposed between the first outflow / inlet hole and the first inner fin, a plate type is provided. High heat exchanger strength.

Claims (11)

A plate portion formed with an outflow / inflow hole for inflow / outflow of the fluid,
An outer peripheral wall portion extending to one surface side of the plate portion and forming a flow path for flowing the fluid between a plate portion adjacent to the one surface side of the plate portion;
An inner fin attached in the flow path,
A plate heat exchanger in which a plurality of heat transfer plates with
The inner fin is placed on the one surface of the plate portion at a position separated from the outflow / inflow hole in the flow path, and the entire circumference of the inflow / outflow hole is not provided with the inner fin. In contact with space,
Plate heat exchanger. The plate portion and the flow path are formed in a rectangular shape in plan view,
The inner fin is formed in a rectangular shape in a plan view, the longitudinal direction of which is shorter than the plate portion and the flow path, and a short side of the inner fin is separated from the outflow / inflow hole.
The plate heat exchanger according to claim 1. The plate portion has a protrusion projecting from the plate portion,
The projecting portion, of the stacked heat transfer plates, forms a support that is in contact with the heat transfer plate located on one surface side or the other surface side of the plate portion,
The plate heat exchanger according to claim 1. Of the stacked heat transfer plates, each of the two adjacent heat transfer plates has a protrusion projecting from the plate portion and abutting on each other,
The plate heat exchanger according to claim 1. The heat transfer plate,
A first heat transfer plate through which the first fluid flows in and out of the outflow hole as the fluid,
A second heat transfer plate through which a second fluid different from the first fluid flows in and out of the inflow / outflow hole as the fluid,
The first heat transfer plate and the second heat transfer plate are alternately stacked, and heat exchange is performed between the first fluid and the second fluid.
The plate heat exchanger according to any one of claims 1 to 4. The convex portion provided on the plate portion of the first heat transfer plate, and the convex portion provided on the plate portion of the second heat transfer plate, the first heat transfer plate and the second heat transfer plate The plates are arranged offset in the direction in which they are stacked,
A plate heat exchanger according to claim 5. A plurality of convex portions provided on the plate portion of the first heat transfer plate and a plurality of convex portions provided on the plate portion of the second heat transfer plate are provided, and the first fluid and the Of the two fluids, more convex portions are provided on the plate portion through which the higher pressure fluid flows,
The plate heat exchanger according to claim 5. Only one of the plate portion of the first heat transfer plate and the plate portion of the second heat transfer plate has the protrusion.
A plate heat exchanger according to claim 6. The first heat transfer plate is surrounded by a first tubular wall, a first passage hole through which the second fluid flows into and out of the second heat transfer plate, and provided at an end of the first tubular wall, And a first flange joined to the second heat transfer plate,
The second heat transfer plate is surrounded by a second tubular wall, a second passage hole through which the first fluid flows into and out of the first heat transfer plate, and provided at an end of the second tubular wall, And a second flange joined to the first heat transfer plate,
The plate heat exchanger according to any one of claims 5 to 8. The distance at which the inner fin is separated from the outflow / inflow hole in the flow path of the one surface of the plate portion is larger than the pitch between the fins and the fins of the inner fin,
The plate heat exchanger according to any one of claims 1 to 9. A plate heat exchanger according to any one of claims 1 to 10, wherein the plate heat exchanger performs heat exchange between refrigerant and water.
Heat pump hot water supply system.

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