JP2019020057A - Metal plate for heat exchanger, and heat exchanger - Google Patents

Abstract

To provide a metal plate for heat exchanger and a heat exchanger, capable of preventing internal leakage that heat exchange fluid leaks between two metal plates adjacent to each other, in a plate heat exchanger.SOLUTION: A metal plate 20D for heat exchanger comprises: an outer peripheral region 21; a thin region 22 formed in the outer peripheral region 21, and made thinner than the outer peripheral region 21; and a heat transfer fin 25 provided so as to project from the thin region 22 in a thickness direction of the metal plate 20D. In the thin region 22, an inlet side opening 23B into which second fluid Fflows is formed. In a region positioned around the inlet side opening 23B in the thin region 22, a reinforcement part 31 projecting in the thickness direction of the metal plate 20D is provided.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a heat exchanger metal plate and a heat exchanger.

  Generally, heat exchangers are widely used for devices that require the use of heat energy or heat removal. Among them, a plate type heat exchanger is known as a typical high performance heat exchanger. In such a plate-type heat exchanger, a plurality of metal plates that are partially thinned by pressing, half-etching, or the like are stacked, and an opposing or parallel flow of heat exchange fluid is performed between the metal plates. A path is formed. Moreover, in a plate type heat exchanger, in order to improve heat transfer efficiency between two heat exchange fluids having different temperatures, a plurality of heat transfer fins are provided in a flow path through which the heat exchange fluid passes to increase the heat transfer area. (For example, refer to Patent Document 1).

JP 2006-170549 A

  However, in the conventional plate heat exchanger, when the joining strength of two adjacent metal plates, particularly in the vicinity of the fluid inlet and outlet, is insufficient, the two heat exchange fluids are mixed inside the heat exchanger. There is a risk that. In order to prevent such an internal leak of the heat exchange fluid, it is necessary to firmly join regions in the vicinity of the fluid inlet and outlet, particularly in the metal plate.

  The present invention has been made in consideration of such points, and in a plate heat exchanger, it is possible to suppress an internal leak in which a heat exchange fluid leaks between two adjacent metal plates. Furthermore, it aims at providing the metal plate for heat exchangers, and a heat exchanger.

  The present invention is a metal plate for a heat exchanger, which is formed in an outer peripheral region, an inner side of the outer peripheral region, and is thinner than the outer peripheral region, and protrudes in the thickness direction of the metal plate from the thin region. The thin-walled region is formed with an opening through which fluid flows in or out, and the thin-walled region is located in a region located around the opening in the thickness direction of the metal plate. It is the metal plate for heat exchangers in which the reinforcement part which protrudes in is provided.

  The present invention is the metal plate for a heat exchanger, wherein the reinforcing portion is disposed away from the heat transfer fin in the main flow direction of the fluid.

  The present invention is the metal plate for a heat exchanger, wherein the reinforcing portion rectifies the fluid flowing in or out of the opening.

  The present invention is the metal plate for a heat exchanger, wherein the reinforcing portion has a larger area than the heat transfer fin in a plan view.

  The present invention is the metal plate for a heat exchanger, wherein the reinforcing portion has the same shape as the heat transfer fin in a plan view.

  In the heat exchanger according to the present invention, the reinforcing portion extends from the outer peripheral region in a direction crossing a main flow direction of the fluid, and a narrowed portion is formed between an edge of the outer peripheral region and the reinforcing portion. It is a metal plate.

  The present invention comprises a pair of fixing plates and a plurality of heat exchanger metal plates arranged in a stacked manner between the pair of fixing plates, and is used for at least one of the plurality of heat exchanger metal plates. The metal plate is a heat exchanger that is the metal plate for the heat exchanger.

  In the present invention, at least two heat exchanger metal plates among the plurality of heat exchanger metal plates are the heat exchanger metal plates, and the reinforcing portions of the two heat exchanger metal plates are mutually connected. It is a heat exchanger with different planar shapes.

  According to the present invention, it is possible to suppress an internal leak in which the heat exchange fluid leaks between two metal plates adjacent to each other.

FIG. 1 is an exploded perspective view showing a heat exchanger according to a first embodiment of the present invention. FIGS. 2A and 2B are plan views showing metal plates according to the first embodiment of the present invention, respectively. FIG. 3 is a partially enlarged plan view showing a metal plate according to the first embodiment of the present invention (an enlarged view of a portion III in FIG. 2B). FIG. 4 is a cross-sectional view showing a pair of metal plates joined to each other (a view corresponding to a cross section taken along line IV-IV in FIG. 3). FIG. 5 is a cross-sectional view showing a pair of metal plates joined to each other (a view corresponding to a cross section taken along line VV in FIG. 3). 6 (a) and 6 (b) are plan views showing a part of a metal plate according to a second embodiment of the present invention. 7 (a) and 7 (b) are plan views showing a part of a metal plate according to a third embodiment of the present invention. 8A and 8B are plan views showing a part of a metal plate according to a fourth embodiment of the present invention.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. Note that, in the following drawings, the same portions are denoted by the same reference numerals, and some detailed description may be omitted.

Configuration of the heat exchanger first, the FIG. 1, will be outlined in the heat exchanger according to the present embodiment. FIG. 1 is an exploded perspective view showing a heat exchanger according to the present embodiment.

  As shown in FIG. 1, a heat exchanger (plate type heat exchanger) 10 according to the present embodiment includes one fixing plate 11 and the other fixing plate 12 provided apart from one fixing plate 11. And a plurality (four in FIG. 1) of heat exchanger metal plates (thin metal plate plates) 20A to 20D arranged to be stacked between one fixing plate 11 and the other fixing plate 12. Yes.

Among these, the plurality of metal plates 20A to 20D are composed of metal plates 20A and 20B for the _first fluid F1 and metal plates 20C and 20D for the _second fluid F2. Each metal plate 20A, 20B, 20C, 20D is bonded to the adjacent metal plate 20A, 20B, 20C, 20D at a temperature close to the melting point, thereby diffusing the metal atoms constituting the plate to each other at the contact surface. Are bonded to each other (diffusion bonding). Alternatively, the metal plates 20A, 20B, 20C, and 20D may be joined to each other by a brazing material. One fixing plate 11 and the other fixing plate 12 are connected to each other by a connecting means (not shown), whereby the one fixing plate 11 and the metal plate 20A are in close contact with each other, and the other fixing plate 12 and the metal plate are in close contact with each other. 20D is in close contact with each other.

  One fixed plate 11 and the other fixed plate 12 each have a substantially rectangular plane shape. One of the fixed plates 11 is connected to inflow pipes 13A and 13B and outflow pipes 14A and 14B. On the other hand, the other fixing plate 12 has a flat shape without an opening or the like.

The inflow pipe 13A and the outflow pipe 14A are used for inflow and outflow of the _first fluid F1, respectively. First fluid F ₁ is the compressor or pump (not shown), flows from the inlet pipe 13A to the heat exchanger 10, the metal plate 20A, while circulating within 20B performs heat exchange, so as to flow out from the outflow pipe 14A It has become. Further, the inlet pipe 13B and outlet pipe 14B is one in which the second fluid _{F 2,} each of which inflow and outflow. The second fluid F ₂ flows into the heat exchanger 10 from the inflow pipe 13B by a compressor or pump (not shown), exchanges heat while circulating in the metal plates 20C and 20D, and flows out from the outflow pipe 14B. It has become.

The first fluid F ₁ and the second fluid F ₂ have different temperatures at least when they flow into the inflow pipes 13A and 13B. The first fluid F ₁ and the second fluid F ₂ may be a gas such as carbon dioxide or air, or may be a liquid such as water. As the first fluid F ₁ and the second fluid F ₂ , the same type of fluid may be used, or different types of fluid may be used. In the present embodiment, high-temperature high-pressure refrigerant (R744 (carbon dioxide) and the like) is used as the first fluid F _1, the case where low-temperature low-pressure fluid (water) is used as the second fluid F ₂ Let's take an example.

Thus, in the heat exchanger 10, the metal plate 20A, the first fluid _{F 1} passing between 20B, metal plates 20C, with the second fluid _{F 2} passing between 20D, Heat exchange is performed. Note that the number of the metal plates 20A to 20D is four in FIG. 1 for convenience, but is not limited thereto, and may be, for example, about 20 or more and 200 or less. Further, a part of the plurality of metal plates may be configured differently from the metal plates 20A to 20D according to the present embodiment.

  Such a heat exchanger 10 can be used for, for example, a heat pump unit of a water heater, air conditioning equipment, refrigeration equipment, refrigeration equipment, in-vehicle EGR (Exhaust Gas Recirculation) cooler, chemical plant, and the like.

Configuration of Metal Plate Next, the configuration of the metal plate according to the present embodiment will be described with reference to FIGS. In the following, the pair of metal plates 20C and 20D for the _second fluid F ₂ (low temperature and low pressure fluid) will be described.

  As shown in FIGS. 2A and 2B, each of the pair of metal plates 20C and 20D has a substantially rectangular shape in plan, and has a longitudinal direction and a lateral direction. 2A and 2B, the longitudinal direction is parallel to the Y direction, and the short side direction is parallel to the X direction orthogonal to the Y direction.

  Each of the metal plates 20 </ b> C and 20 </ b> D has an outer peripheral region 21 and a thin region (half-etched region) 22 formed inside the outer peripheral region 21. Among these, the outer peripheral area | region 21 is formed in cyclic | annular form along the outer periphery whole region of each metal plate 20C, 20D. The outer peripheral region 21 is not half-etched and has the same thickness as the entire thickness of the metal plates 20C and 20D.

  Moreover, the thin area | region 22 is thinner than the outer peripheral area | region 21, and is formed only in the one surface side of the metal plates 20C and 20D. In this case, the thin region 22 is formed by performing, for example, half etching processing from the one surface side. “Half etching” means that the material to be etched is etched halfway in the thickness direction. The depth of the thin region 22 may be, for example, 40% to 70% of the thickness of the outer peripheral region 21. Thus, since the thin region 22 of the metal plates 20A to 20D is formed by (half) etching, the heat exchanger 10 can be made compact and highly efficient compared to the case where the fluid flow path is formed by pressing. can do. Thereby, energy efficiency can be improved including reduction of the amount of refrigerant.

In the thin region 22, an inlet side opening 23 </ b> B and an outlet side opening 24 </ b> B are formed in the vicinity of a pair of corners on the diagonal lines of the metal plates 20 </ b> C and 20 </ b> D. The inlet side opening 23 </ b> B and the outlet side opening 24 </ b> B are in communication with the thin region 22 while the second fluid F ₂ passes therethrough.

Further, in the outer peripheral region 21, an inlet side opening 23A and an outlet side opening 24A are formed in the vicinity of another pair of corners on the diagonal lines of the metal plates 20C and 20D, respectively. The inlet side opening 23A and the outlet side opening 24A allow the _first fluid F1 to pass through. Therefore, the inlet-side opening 23A and the outlet-side opening 24A are arranged away from the thin region 22 without communicating with the thin region 22 of the metal plates 20C and 20D. On the other hand, the inlet side opening 23A and the outlet side opening 24A communicate with the thin region 22 of the metal plates 20A and 20B (see FIG. 1).

  These inlet side openings 23A and 23B and outlet side openings 24A and 24B are formed so as to penetrate the metal plates 20C and 20D. The inlet openings 23A and 23B and the outlet openings 24A and 24B may be formed by etching from both sides simultaneously with the thin area 22 when the thin area 22 is formed by half etching from one side.

A plurality of heat transfer fins 25 are provided in the thin region 22 so as to protrude in the Z direction (thickness direction of the metal plates 20C and 20D). The thickness of the portion where each heat transfer fin 25 is provided is the same as the thickness of the outer peripheral region 21. On the other hand, each heat transfer fin 25 is arranged separately from the outer peripheral region 21 and the other heat transfer fins 25 in the planar direction (X direction and Y direction). For this reason, each heat transfer fin 25 is independently arranged in an island shape, and a flow path 26 through which the second fluid F ₂ passes is formed around each heat transfer fin 25. In FIG. 1 and FIGS. 2A and 2B, only a part of the heat transfer fins 25 is shown for the sake of convenience, but actually, the heat transfer fins 25 extend over most of the thin region 22. Is arranged.

As shown in FIG. 3, each heat transfer fin 25 has a substantially plane S shape. The heat transfer fins 25 are arranged in large numbers at regular intervals along the second fluid F ₂ in the main flow direction D (Y-direction). Further, the heat transfer fins 25 are disposed in parallel to each other at a predetermined interval in a direction (X direction) perpendicular to the second fluid F ₂ in the main flow direction D (Y-direction). The heat transfer fins 25 are each formed in a streamline shape such that turbulence such as vortex or swirl does not occur at both ends in the longitudinal direction, and is configured to reduce fluid resistance. Note that the shape of each heat transfer fin 25 may be a planar circular shape, a planar oval shape, or a planar polygonal shape.

  In the present embodiment, the plurality of heat transfer fins 25 are configured by combining a plurality of two types of heat transfer fins 25a and 25b having a shape symmetrical with each other. Of these, the heat transfer fin 25a has a substantially S-shape extending from the X direction minus side and the Y direction minus side toward the X direction plus side and the Y direction plus side. On the other hand, the heat transfer fin 25b has a substantially S shape extending from the X direction plus side and the Y direction minus side toward the X direction minus side and the Y direction plus side. The heat transfer fins 25a and 25b are each arranged in a line along the X direction, and the lines of the heat transfer fins 25a and the lines of the heat transfer fins 25b are alternately arranged along the Y direction. The plurality of heat transfer fins 25 are arranged so that a large number of these heat transfer fins 25a and 25b are shifted by a predetermined amount in the X direction and the Y direction, and so-called staggered arrangement (delta arrangement). It has become. In the present specification, these two types of heat transfer fins 25a and 25b are collectively referred to as heat transfer fins 25. The width of the heat transfer fin 25 may be appropriately changed depending on the thickness of the material of the metal plates 20C and 20D and the fluid. Specifically, it is good also as 0.3 mm or more and 1.0 mm or less in the widest location among each heat-transfer fin 25, for example.

The second fluid F ₂ passes through the flow path 26 between the pair of heat transfer fins 25 adjacent to each other in the X direction, and then upstream of the other heat transfer fins 25 located on the further downstream side (minus side in the Y direction). It branches at the end of the side (Y direction plus side) and passes through the flow path 26 between this heat transfer fin 25 and a pair of heat transfer fins 25 adjacent to each other in the X direction. Thereafter, the second fluid F ₂ flowing along the heat transfer fins 25 joins at the end portion on the downstream side (minus side in the Y direction) of the heat transfer fins 25. As a result, pressure loss due to vortex formation and swirling flow due to a sharp bend in the flow path 26 can be minimized, and changes in the flow path area, that is, expansion and contraction of the flow path 26 can be suppressed. And pressure loss due to contraction flow can be kept small. The width of the flow path 26 may be appropriately changed depending on the thickness of the material of the metal plates 20C and 20D and the fluid, and may be, for example, 0.2 mm or more and 3.0 mm or less.

As shown in FIG. 3, a longitudinal edge 27 and a lateral edge 28 are formed on the thin region 22 side in the outer peripheral region 21. Among longitudinal edge 27 extends linearly along the second fluid F ₂ in the main flow direction D (Y-direction). The longitudinal edge 27 may have a wave shape or a zigzag shape along the shape of the heat transfer fin 25. Further, the lateral edge 28 is bent along the direction (X direction) perpendicular to the main flow direction D in the outer peripheral region 21. The lateral edge 28 has an opening adjacent edge 28a, an S-shaped intermediate edge 28b connected to the opening adjacent edge 28a, and an inclined edge 28c connected to the S-shaped intermediate edge 28b. Yes. Among these, the opening adjacent edge portion 28a extends in the direction (X direction) orthogonal to the main flow direction D from the peripheral edge of the inlet side opening 23B. Also, S-shaped intermediate edge 28b extends from the opening adjacent the edge 28a towards the second downstream of the fluid F ₂ (Y-direction negative side) are curved in a substantially S-shape in plan view. The inclined edge portion 28c extends from the S-shaped intermediate edge portion 28b so as to incline toward the X direction plus side and the Y direction minus side.

In the present embodiment, a plurality of reinforcing portions 31 are provided in a region located around the inlet side opening 23 </ b> B in the thin region 22. The reinforcing portion 31 along the direction (X direction) perpendicular to the second main flow direction D of the fluid F _2, (4 one in this case) more at regular intervals are arranged. That is, the centers of the plurality of reinforcing portions 31 are arranged on a straight line parallel to the X direction. Each reinforcing portion 31 protrudes from the thin region 22 in the thickness direction (Z direction) of the metal plate 20D. That is, the thickness of the portion where each reinforcing portion 31 is provided is the same as the thickness of the outer peripheral region 21. On the other hand, each reinforcement part 31 is arrange | positioned away from the outer peripheral area | region 21 and the other reinforcement part 31, respectively in the plane direction (X direction). Therefore, each of the reinforcing portions 31 are arranged independently in an island shape, a second fluid F ₂ from the inlet side opening 23B is adapted to pass around the respective reinforcing portions 31. Thus, the reinforcing part 31 plays a role of rectifying the _second fluid F2 flowing out from the inlet side opening 23B. Accordingly, the second fluid F ₂ can flow uniformly in the thin region 22, it is possible to enhance the heat exchange efficiency between the first fluid F ₁ and the second fluid F _2.

As shown in FIG. 3, the plurality of reinforcing portions 31 have the same planar shape. Moreover, each reinforcement part 31 has a planar shape different from the heat-transfer fin 25, and specifically has a parallelogram shape. In this case, a pair of opposing sides of the parallelogram constituting each reinforcing portion 31, and extends parallel to the second fluid F ₂ in the main flow direction D (Y-direction). On the other hand, the other pair of opposite sides of the parallelogram forming each reinforcing portion 31 is arranged so as to be inclined in the X direction and the Y direction. Thus, by arranging the plurality of reinforcing portions 31 uniformly in the plane, the flow of the second fluid F ₂ can be uniformly dispersed around the reinforcing portion 31.

The reinforcing portion 31 is spaced apart from the heat transfer fins 25 in the second main flow direction D of the fluid F _2. That is, between the portion closest to the heat transfer fin 25 in the reinforcing portion 31 (the portion on the minus side in the Y direction) and the portion closest to the reinforcing portion 31 in the heat transfer fin 25 (the portion on the plus side in the Y direction). A space 22a is formed. In the space 22a, the second fluid F ₂ temporarily stays, so that heat exchange between the first fluid F ₁ and the second fluid F ₂ can be promoted. The distance D1 (the length in the Y direction) of the space 22a may be, for example, not less than 0.5 mm and not more than 50 mm. Further, the length L1 (the length in the Y direction) of the reinforcing portion 31 may be, for example, 0.5 mm or more and 10 mm or less, and the width W1 (the length in the X direction) of the reinforcing portion 31 is, for example, 0.5 mm or more and 10 mm. The following may be used.

In addition, as shown to Fig.2 (a), the reinforcement part 31 is the thin area | region 22 of 20 C of metal plates, Comprising: It forms also in the circumference | surroundings of the entrance-side opening 23B. In this case, the reinforcing portion 31 around the inlet side opening 23B of the metal plate 20C and the reinforcing portion 31 around the inlet side opening 23B of the metal plate 20D are joined together in the Z direction. Thus, the some reinforcement part 31 is provided in the area | region located in the circumference | surroundings of the entrance-side opening 23B of metal plate 20C, 20D, and these reinforcement parts 31 which oppose are mutually joined. In this case, the reinforcement part 31 plays the role of the support | pillar part which joins the metal plates 20C and 20D. Thus, the metal plate 20C around the inlet-side opening 23B, is 20D each other firmly bonded to suppress the internal leakage of the metal plate 20C, the first fluid _{F 1} or the second fluid _{F 2} between the 20D leaks be able to.

Further, as shown in FIGS. 2 (a) and 2 (b), the reinforcing portion 31 is a thin region 22 of the metal plate 20C around the outlet side opening 24B and a thin region 22 of the metal plate 20D at the outlet side. It is also formed around the opening 24B. In this case, the reinforcing portion 31 around the outlet side opening 24B of the metal plate 20C and the reinforcing portion 31 around the outlet side opening 24B of the metal plate 20D are joined together in the Z direction. Thus, the metal plate 20C around the outlet opening 24B, 20D to each other are firmly joined, suppress internal leakage metal plate 20C, the first fluid _{F 1} or the second fluid _{F 2} between the 20D leaks can do. In addition, the reinforcement part 31 may be provided only in any one of the circumference | surroundings of the entrance side opening 23B, and the circumference | surroundings of the exit side opening 24B.

  Further, each reinforcing portion 31 has a planar shape having a larger area than each heat transfer fin 25 in plan view. Thereby, metal plate 20C, 20D can be joined more firmly by the reinforcement part 31, and the internal leak mentioned above can be suppressed more effectively.

  Next, the bonded metal plates 20C and 20D will be described with reference to FIGS. 4 and 5 are cross-sectional views showing a state in which the metal plates 20C and 20D are joined to each other.

As shown in FIG. 4, the metal plates 20 </ b> C and 20 </ b> D are arranged so that the surfaces on which the thin regions 22 are formed face each other. Further, the thin region 22 and the plurality of heat transfer fins 25 of the pair of metal plates 20C and 20D are formed so as to be mirror-symmetric with each other. For this reason, when the metal plates 20C and 20D are joined together, the thin regions 22 are joined together, and the corresponding heat transfer fins 25 are joined together. The metal plate 20C, the flow path 26 where the second fluid _{F 2} flows through the thin region 22 between the 20D is formed.

  The height h (distance in the Z direction) of the flow path 26 is preferably set to 0.1 mm or more and 1.0 mm or less, for example. Thus, by suppressing the height h of the flow path 26, the heat exchanger 10 can be made compact and the efficiency of heat exchange can be increased.

  Further, as shown in FIG. 5, the plurality of reinforcing portions 31 formed on the pair of metal plates 20C and 20D are formed so as to be mirror-symmetric with each other. For this reason, when the metal plates 20C and 20D are joined to each other, the corresponding reinforcing portions 31 are joined to each other in plan view.

  In the present embodiment, the metal plates 20C and 20D are preferably made of a metal having good thermal conductivity, such as stainless steel, iron, copper, copper alloy, aluminum, aluminum alloy, titanium, and the like. Further, the thicknesses of the metal plates 20C and 20D may be set to 0.1 mm or more and 2.0 mm or less, respectively.

The configuration of the pair of metal plates 20A and 20B for the _first fluid F1 may be substantially the same as the configuration of the pair of metal plates 20C and 20D for the _second fluid F2. Alternatively, the shape and / or arrangement of the heat transfer fins 25 of the metal plates 20A and 20B may be different from the shape and / or arrangement of the heat transfer fins 25 of the metal plates 20C and 20D. For example, when a high-temperature and high-pressure fluid is used as the first fluid F _{1 and a} low-temperature and low-pressure fluid is used as the second fluid F ₂ , the interval between the heat transfer fins 25 of the metal plates 20A and 20B is set to the metal plate 20C. The distance between the 20D heat transfer fins 25 may be narrower. In this case, the high temperature and high pressure first fluid F ₁ is less likely to flow than the low temperature and low pressure second fluid F _2, so that the flow rates of the first fluid F ₁ and the second fluid F ₂ can be made closer. it can promote first fluid F ₁ and the heat exchange between the second fluid F _2. In the present embodiment, the metal plates 20A and 20B are provided with reinforcing portions 31 similar to the metal plates 20C and 20D. However, the present invention is not limited to this, and reinforcing portions 31 having shapes and / or arrangements different from those of the metal plates 20C and 20D may be provided on the metal plates 20A and 20B. Or the reinforcement part 31 does not need to be provided in either metal plate 20A, 20B or metal plate 20C, 20D.

Operation of the present embodiment Next, the operation of the heat exchanger having such a configuration will be described.

First, in the heat exchanger 10 shown in FIG. 1, along with introducing the first fluid _{F 1} to the inlet pipe 13A, introducing a second fluid _{F 2} to the inlet pipe 13B. In this case, the temperature of the _first fluid F _{1 and} the temperature of the second fluid F ₂ are different from each other.

Next, the first fluid F ₁ passes through the flow path 26 formed in the thin region 22 between the metal plates 20A and 20B, and flows out from the outflow pipe 14A of the heat exchanger 10. Similarly, the second fluid _{F 2} is a metal plate 20C, the flow path 26 formed in the thin region 22 between 20D passes, flows out from the outflow pipe 14B of the heat exchanger 10. At the time of flowing out from the outflow pipe 14A, 14B, relatively cool second is a fluid temperature of the fluid F ₂ is increased than when the inflow of relatively high temperature first is a fluid of the fluid F ₁ The temperature is lower than at the inflow. In this case, since the metal plate 20B and the metal plate 20C are bonded to each other, the metal plate 20B, through 20C, the heat exchange efficiency between the first fluid F ₁ and the second fluid F ₂ Done.

In this way, during use of the heat exchanger 10, the first fluid F ₁ of high temperature and pressure flows continuously to the inlet pipe 13A. Fluid _{F 1} of the first is to sequentially pass through the inlet-side opening 23A of each metal plate 20A to 20D, flows into the flow paths 26 formed metal plate 20A, the thin region 22 of 20B. By thus first fluid F ₁ of the high-temperature high-pressure flows, metal plates 20C, a high load on the inlet-side opening 23A between the 20D applied. If the joining of the metal plates 20C and 20D near the inlet opening 23A is insufficient, the metal plates 20C and 20D may be separated from each other. In this case, there is a possibility that the metal plate 20C, the fluid F ₁ gap from a first of the vicinity of the inlet-side opening 23A formed between the 20D will invade. Assuming that the metal plate 20C, a first fluid _{F 1} during 20D invades, first fluid _{F 1} that has entered is reached the flow path 26 formed by a metal plate 20C, 20D thin region 22 between the And mixed with the second fluid F ₂ in the flow path 26.

Similarly, the second fluid F ₂ flows continuously to the inlet pipe 13B. Fluid _{F 2} of the second is to sequentially pass through the inlet-side opening 23B of the metal plates 20A to 20D, flows into the flow paths 26 formed metal plate 20C, the thin region 22 of 20D. At this time, if the metal plates 20A and 20B are not sufficiently joined in the vicinity of the inlet opening 23B, the metal plates 20A and 20B may be peeled off. In this case, the metal plate 20A, the gap in the vicinity of the inlet-side opening 23B formed between 20B, there is a possibility that the second fluid F ₂ will invade. If the second fluid F ₂ enters between the metal plates 20A and 20B, the invading second fluid F ₂ reaches the flow path 26 formed by the thin regions 22 of the metal plates 20A and 20B. And mixed with the first fluid F ₁ in the flow path 26.

On the other hand, according to the present embodiment, the reinforcing portion 31 is formed around the inlet side opening 23B and the outlet side opening 24B in the thin region 22 of the metal plates 20C, 20D. Thereby, especially the joint strength between the metal plates 20C and 20D around the inlet side opening 23B and the outlet side opening 24B can be increased, and a problem that peeling occurs between the metal plates 20C and 20D can be suppressed. Thus, it is possible to first fluid F ₁ or the second fluid F ₂ suppresses the internal leakage of leaking, to improve the durability and the heat exchange performance of the heat exchanger 10. The metal plates 20C, by having an increased bonding strength between 20D, it is possible to use a high-pressure fluid from a fluid F ₂ of the first fluid F ₁ or the second.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIGS. 6 (a) and 6 (b) are diagrams showing a second embodiment of the present invention. Specifically, FIG. 6A is a plan view showing a part of the metal plate 20B for the _first fluid F1, and FIG. 6B is a metal plate for the _second fluid F2. It is a top view which shows a part of 20D. The second embodiment shown in FIGS. 6A and 6B is different in the configuration of the reinforcing portion, and the other configurations are substantially the same as those of the first embodiment described above. 6A and 6B, the same parts as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIGS. 6A and 6B, each of the metal plates 20B and 20D has a reinforcing portion 32. That is, as shown in FIG. 6A, the reinforcing portion 32 is formed in a region located around the entrance-side opening 23A in the thin region 22 of the metal plate 20B. Moreover, as shown in FIG.6 (b), the reinforcement part 32 is formed in the area | region located around the exit side opening 24B among the thin area | regions 22 of metal plate 20D. The reinforcing portions 32 of the metal plates 20B and 20D protrude from the thin region 22 in the thickness direction (Z direction) of the metal plates 20B and 20D, respectively. That is, the thickness of the portion where each reinforcing portion 32 is provided is the same as the thickness of the outer peripheral region 21.

In this case, the metal plate 20B, 20D reinforcing portion 32 of the extend toward each direction transverse to the first fluid _{F 1} or the second main flow direction D of the fluid _{F 2} from the outer peripheral region 21 (X direction). Each reinforcing portion 32 serves to rectify the first fluid _{F 1} or the second fluid _{F 2,} respectively. Moreover, each reinforcement part 32 has a planar substantially triangular shape, and the width | variety becomes narrow gradually as it leaves | separates from the outer peripheral area | region 21 toward the X direction, respectively.

A narrowed portion 33 is formed between each reinforcing portion 32 and the lateral edge 28 (S-shaped intermediate edge 28b, inclined edge 28c) of the outer peripheral region 21. In the narrowed portion 33, the first fluid F ₁ (FIG. 6A) flowing into the thin wall region 22 from the inlet side opening 23A, or the second fluid F ₂ flowing out from the thin wall region 22 into the outlet side opening 24B ( The flow in FIG. 6B is limited. To serve as thus narrowed portion 33 is the flow resistance, the first fluid F ₁ or the second speed of flow of the fluid F ₂ is lowered, the first fluid F ₁ or the second fluid F ₂ Tends to stay in the thin region 22. Thus, it is possible to further promote the first fluid F ₁ and the heat exchange between the second fluid F _2.

In the present embodiment, the reinforcing portion 32 of the metal plate 20B for the _first fluid F1 and the reinforcing portion 32 of the metal plate 20D for the _second fluid F2 have different planar shapes. Yes. Specifically, the width W2 (FIG. 6A) of the narrowed portion 33 of the metal plate 20B is narrower than the width W3 (FIG. 6B) of the narrowed portion 33 of the metal plate 20D (W2 <W3). In this case, the high-temperature and high-pressure first fluid F ₁ is less likely to flow than the low-temperature and low-pressure second fluid F _2, so that the flow rates of the first fluid F ₁ and the second fluid F ₂ are relatively close to each other. And can facilitate heat exchange between the first fluid F ₁ and the second fluid F ₂ .

  The width W2 (width along the mainstream direction D) of the narrowed portion 33 of the metal plate 20B may be, for example, 0.5 mm to 2 mm, and the width W3 (width along the mainstream direction D) of the narrowed portion 33 of the metal plate 20D is For example, it is good also as 1 mm or more and 5 mm or less. Further, the length (length along the X direction) L2 (FIG. 6A) of the reinforcing portion 32 of the metal plate 20B is, for example, 30% or more of the width (length along the X direction) W4 of the thin region 22 70. % Of the reinforcing portion 32 of the metal plate 20D (length along the X direction) L3 (FIG. 6B) is, for example, 30 of the width (length along the X direction) W4 of the thin region 22 % To 70%.

  Although not shown, reinforcing portions 32 similar to the above are also formed on the outlet side opening 24A side of the metal plate 20B and the inlet side opening 23B side of the metal plate 20D. Further, the metal plate 20A has a planar shape that is mirror-symmetrical with the metal plate 20B (FIG. 6A), and the metal plate 20C is a planar shape that is mirror-symmetrical with the metal plate 20D (FIG. 6B). have.

Thus, according to the present embodiment, the reinforcing portions 32 are formed around the inlet side opening 23A of the metal plate 20B and around the outlet side opening 24A of the metal plate 20D, respectively. Thereby, the joining strength between metal plate 20A-20D can be raised, and the malfunction which peeling arises between metal plates 20A-20D can be suppressed. Further, according to the present embodiment, since the narrowed portion 33 is formed between the lateral edge 28 of the outer peripheral region 21 of the metal plates 20B and 20D and the reinforcing portion 32, the first fluid F ₁ is formed. or the second fluid F ₂ is likely to remain in the thin region 22, it is possible to improve the heat exchange efficiency between the first fluid F ₁ and the second fluid F _2.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIGS. 7 (a) and 7 (b) are diagrams showing a third embodiment of the present invention. Specifically, FIG. 7A is a plan view showing a part of the metal plate 20B for the _first fluid F1, and FIG. 7B is a metal plate for the _second fluid F2. It is a top view which shows a part of 20D. The third embodiment shown in FIGS. 7A and 7B is different in the configuration of the reinforcing portion, and the other configurations are substantially the same as those of the first embodiment described above. 7A and 7B, the same parts as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIGS. 7A and 7B, the metal plates 20 </ b> B and 20 </ b> D each have a plurality of reinforcing portions 34. That is, as shown in FIG. 7A, a plurality of reinforcing portions 34 are formed in a region located around the inlet side opening 23A in the thin region 22 of the metal plate 20B. Moreover, as shown in FIG.7 (b), the some reinforcement part 34 is formed in the area | region located around the exit side opening 24B among the thin area | regions 22 of metal plate 20D. The reinforcing portions 34 of the metal plates 20B and 20D protrude from the thin region 22 in the thickness direction (Z direction) of the metal plates 20B and 20D, respectively. That is, the thickness of the portion where each reinforcing portion 34 is provided is the same as the thickness of the outer peripheral region 21.

In this case, each reinforcement part 34 has the same planar shape as each heat-transfer fin 25, specifically, has a planar substantially S-shape. Each reinforcing portion 34 serves to rectify the first fluid _{F 1} or the second fluid _{F 2,} respectively. Further, in each of the metal plates 20B and 20D, the plurality of reinforcing portions 34 are arranged at a certain interval in a direction (X direction) perpendicular to the main flow direction D. The reinforcing portion 34 is configured to reduce fluid resistance so that turbulence such as vortex or swirling flow does not occur at both ends in the longitudinal direction.

In the present embodiment, the reinforcing portions 34 of the metal plate 20B for the _first fluid F1 and the reinforcing portions 34 of the metal plate 20D for the _second fluid F2 are arranged in different numbers. Specifically, the number (seven) of the reinforcing portions 34 of the metal plate 20B is larger than the number (four) of the reinforcing portions 34 of the metal plate 20D. Further, the interval between the reinforcing portions 34 of the metal plate 20B is narrower than the interval between the reinforcing portions 34 of the metal plate 20D. In this case, the high-temperature and high-pressure first fluid F ₁ is less likely to flow than the low-temperature and low-pressure second fluid F _2, so that the flow rates of the first fluid F ₁ and the second fluid F ₂ are relatively close to each other. And can facilitate heat exchange between the first fluid F ₁ and the second fluid F ₂ .

  Although not shown, reinforcing portions 34 similar to the above are also formed on the outlet side opening 24A side of the metal plate 20B and the inlet side opening 23B of the metal plate 20D. The metal plate 20A has a plane shape that is mirror-symmetric with the metal plate 20B (FIG. 7A), and the metal plate 20C is a plane shape that is mirror-symmetric with the metal plate 20D (FIG. 7B). have.

Thus, according to the present embodiment, a plurality of reinforcing portions 34 are formed around the inlet side opening 23A and the outlet side opening 24B in the thin region 22 of the metal plates 20B and 20D. This allows the fluid _{F 2} of the first fluid _{F 1} or the second between the metal plate 20A~20D to suppress internal leakage leaking.

(Fourth embodiment)
Next, a fourth embodiment of the present invention will be described with reference to FIGS. 8 (a) and 8 (b) are diagrams showing a fourth embodiment of the present invention. Specifically, FIG. 8A is a plan view showing a part of the metal plate 20B for the _first fluid F1, and FIG. 8B is a metal plate for the _second fluid F2. It is a top view which shows a part of 20D. The fourth embodiment shown in FIGS. 8A and 8B is different in the configuration of the reinforcing portion, and the other configuration is substantially the same as the first embodiment described above. 8A and 8B, the same parts as those in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  8A, the metal plate 20B has the same configuration as that of the metal plate 20B shown in FIG. 6A, and a reinforcing portion 32 is formed in a region located around the entrance-side opening 23A. Yes. On the other hand, in FIG. 8B, the metal plate 20D has the same configuration as that of the metal plate 20D shown in FIG. 7B, and a plurality of reinforcing portions 34 are provided in the region located around the outlet side opening 24B. Is formed. That is, the reinforcing portion 32 of the metal plate 20B and the reinforcing portion 34 of the metal plate 20D have different planar shapes.

In this embodiment, the first fluid F ₁ for the metal plate 20B is, while having a reinforcing portion 32 extending in the direction (X direction) transverse to the main flow direction D from the outer peripheral region 21, the second fluid F ₂ The metal plate 20 </ b> D has a plurality of reinforcing portions 34 different from the reinforcing portion 32. In this case, the overall direction of flow FA (to FIG. 8 (a)) the direction FB (FIG overall flow of the second fluid _{F 2} in the metal plate 20D of the first fluid _{F 1} in the metal plate 20B 8 (b)). Thus, it is possible to further promote the first fluid F ₁ and the heat exchange between the second fluid F _2.

  Although not shown, a reinforcing portion 32 similar to the above is formed also on the outlet side opening 24A side of the metal plate 20B, and a reinforcing portion 34 similar to the above is also formed on the inlet side opening 23B of the metal plate 20D. Is formed. The metal plate 20A has a plane shape that is mirror-symmetrical with the metal plate 20B (FIG. 8A), and the metal plate 20C is a plane shape that is mirror-symmetrical with the metal plate 20D (FIG. 8B). have.

  It is also possible to appropriately combine a plurality of constituent elements disclosed in the embodiment and the modification examples as necessary. Or you may delete a some component from all the components shown by the said embodiment and modification.

10, 10A Heat exchanger 11 One fixed plate 12 Other fixed plate 20A-20D Metal plate 21 Outer peripheral region 22 Thin region 23A, 23B Inlet side opening 24A, 24B Outlet side opening 25 Heat transfer fin 26 Channel 27 Longitudinal edge Part 28 Lateral edge 31 Reinforcement part

Claims (8)

A metal plate for a heat exchanger,
An outer peripheral area; and
Formed on the inner side of the outer peripheral region, and a thinner region than the outer peripheral region, and
A heat transfer fin provided so as to protrude in the thickness direction of the metal plate from the thin region,
In the thin region, an opening through which fluid flows in or out is formed,
A metal plate for a heat exchanger, wherein a reinforcing portion protruding in the thickness direction of the metal plate is provided in a region located around the opening in the thin region.   The metal plate for a heat exchanger according to claim 1, wherein the reinforcing portion is disposed away from the heat transfer fin in a main flow direction of the fluid.   The metal plate for a heat exchanger according to claim 1 or 2, wherein the reinforcing portion rectifies a fluid flowing in or out of the opening.   The metal plate for a heat exchanger according to any one of claims 1 to 3, wherein the reinforcing portion has a larger area than the heat transfer fin in a plan view.   The said reinforcement part is a metal plate for heat exchangers as described in any one of Claims 1 thru | or 3 which is the same shape as the said heat-transfer fin by planar view.   The said reinforcement part is extended in the direction which crosses the mainstream direction of the said fluid from the said outer periphery area | region, The constriction part is formed between the edge part of the said outer periphery area | region, and the said reinforcement part. A metal plate for a heat exchanger according to claim 1. A plurality of metal plates for a heat exchanger disposed between the pair of fixing plates and the pair of fixing plates,
7. The heat exchanger according to claim 1, wherein at least one of the plurality of heat exchanger metal plates is a heat exchanger metal plate according to claim 1.   7. The heat exchanger metal plate according to claim 1, wherein at least two of the plurality of heat exchanger metal plates are the heat exchanger metal plates according to claim 1. The heat exchanger according to claim 7, wherein the reinforcing portions of the plate have different planar shapes.

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