JP2005308232A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compact heat exchanger into which low temperature fluid flows with less variations. <P>SOLUTION: The heat exchanger comprises a plurality of high temperature fluid passages 3 in which high temperature fluid is distributed, and a low temperature fluid passage 4 having a plurality of paths 4a in which low temperature fluid is distributed and at least one path 4b via which the paths 4a are communicated with one another. The paths 4a constructed to be stacked are communicated with one another via the path 4b so that the low temperature fluid distributed into the paths 4a is movable through the path 4b into different paths. Thus, the pressure and evaporating condition of the low temperature fluid are uniformed between the paths 4a. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a heat exchanger. In particular, the present invention relates to a heat exchanger in which at least one of a low-temperature fluid passage and a high-temperature fluid passage composed of a plurality of passages is formed in a laminated shape.

  A conventional heat exchanger is known in which a heated flow channel and a heated flow channel are provided between first and second divide plates that are spaced apart from each other. Of these, the heated channel is formed by arranging a first inner fin between a pair of first spacers, and each of the heated channels is a second inner fin between a pair of second spacers. Arranged. By appropriately distributing the brazing material for brazing each member, it is possible to ensure both brazability and prevent inconvenience due to the presence of the brazing material (for example, see Patent Document 1). .)

Alternatively, heat exchange using a metal plate in which a plurality of small-diameter heat transfer tubes having an inner diameter of 0.1 to 2 mm are fixed to each other on both surfaces by brazing with their axes parallel to each other. The vessel is known. A plurality of such plates are arranged in parallel and spaced apart from each other so that the axes of the small-diameter heat transfer tubes are perpendicular to each other. The upper end of each plate is placed on a header having a refrigerant inlet port, and the lower end Are connected to headers each having a refrigerant outlet port, and the headers are communicated with each other by a small-diameter heat transfer tube joined to each plate. A plurality of openings are formed in the plate at intervals, and the refrigerant flow path of each header and the small-diameter heat transfer tube is configured such that the refrigerant flowing through the small-diameter heat transfer tube flows back between the headers (for example, (See Patent Document 2).
JP 2002-203586 A JP 2003-269822 A

  However, in the heat exchanger described in Patent Document 1, the flow path is divided for each layer through which the fluid to be heated flows. For this reason, once the fluid to be heated in one layer evaporates over the entire surface of the layer, the pressure rises in the layer and the next liquid becomes difficult to flow in (vapor lock phenomenon). In addition, since the heated fluid that could not flow into the layer where evaporation has occurred flows into the other layer, the temperature drops in the other layer. As a result, the steam temperature at the outlet of the heat exchanger becomes unstable or liquid is mixed in the steam, and there is a problem that high-quality steam cannot be generated.

  On the other hand, in the heat exchanger described in Patent Document 2, the refrigerant and air are reversed, and the refrigerant layer is not divided by flowing air through the small-diameter heat transfer tube and flowing the refrigerant outside thereof. The vapor lock problem can be prevented. However, such a so-called shell and tube type heat exchanger generally produces sufficient high-quality steam because heat exchange performance per unit volume is inferior to a heat exchanger having a plurality of flow path layers. Therefore, it is necessary to sacrifice the size, and it cannot be applied to a fuel cell vehicle or the like that requires compactness.

  In view of the above problems, an object of the present invention is to provide a compact heat exchanger that suppresses variations in inflow of low-temperature fluid.

  The present invention includes a plurality of high-temperature fluid passages through which a high-temperature fluid flows, a plurality of first low-temperature fluid passages through which a low-temperature fluid flows, and at least one second low-temperature fluid passage communicating with each other. And a cryogenic fluid passage. Heat exchange is possible between the fluid flowing through the high-temperature fluid passage and the low-temperature fluid passage.

  By providing at least one second cryogenic fluid passage communicating with each other in the first cryogenic fluid passage, the cryogenic fluid can move between different first cryogenic fluid passages. Can be made uniform. As a result, in a relatively compact heat exchanger having a plurality of flow paths, it is possible to suppress variations in inflow of low-temperature fluid.

  A first embodiment will be described. FIG. 1 shows an outline of the fluid flow into and out of the heat exchanger 1.

  For example, a high-temperature fluid composed of high-temperature air flows into the heat exchanger 1 from A and flows out from B. Further, a low-temperature fluid made of liquid water flows in from C and flows out from D. Here, the heat exchanger 1 is an evaporator that generates water vapor as a low-temperature fluid by exchanging heat between high-temperature air and water.

The structure of the laminated body core 5 which is a core part of the heat exchanger 1 is shown in FIG.
Layer-shaped passage At least one of the high-temperature fluid passage 3 and the low-temperature fluid passage 4 is formed by stacking a plurality of layer-shaped passages. Here, the low-temperature fluid passage 4 is configured by stacking a plurality of layer-shaped passages 4a.

  A stacked body core 5 is formed by stacking a plurality of plates 2. A high-temperature fluid passage 3 that is a flow passage of the high-temperature fluid in the heat exchanger 1 is configured by a through hole 3a that penetrates each plate 2 in the thickness direction. Each plate 2 is provided with a through hole 3a at a position overlapping in the stacking direction, and the high-temperature fluid passage 3 is configured to penetrate the stacked core 5 in the stacking direction. Here, a plurality of through-holes 3a are provided substantially uniformly in the plane of the plate 2.

  On the other hand, the low-temperature fluid passage 4 that is the flow passage of the low-temperature fluid in the heat exchanger 1 is configured to divide the plurality of plates 2. The passage 4a is configured such that fluid flows from one side of the rectangular plate 2 to the other side. The passages 4a are configured to be parallel to each other. By laminating the plurality of plates 2, the passage 4 a forms a channel also in the laminating direction of the laminated core 5, and the low-temperature fluid can flow in the laminating direction of the laminated core 5 and the direction perpendicular to the laminating direction. . At this time, the passage 4a formed when the plates 2 are laminated has a shape that forms a layer of one passage along the laminating direction. Therefore, such a passage has a layer shape along the lamination cross section. This is called a passage.

  Further, the passage 4b communicating with the passages 4a is configured to divide the plurality of plates 2. The passage 4 b also constitutes a layer-shaped flow path along the laminated section of the laminated core 5. Although the number of the passages 4b is one here, it may be constituted by a plurality of flow paths. The low temperature fluid flows freely between the passages 4a by flowing through the passages 4b. Further, by laminating the plurality of plates 2, the low temperature fluid can also flow through the passage 4 b in the laminating direction. In addition, although it comprised so that the channel | path 4a and the channel | path 4b might orthogonally cross here, it is not this limitation.

  As described above, the laminate core 5 is divided into a plurality of layer-shaped cryogenic fluid passages 4 configured along the lamination cross section. However, the present invention is not limited to this, and a part of the laminate core 5 is not divided. You may comprise and comprise. In this case, the parts to be connected are shifted for each plate 2 to avoid the cryogenic fluid passage 4 being composed of a plurality of independent passages 4a and 4b.

  Etching is used for shape processing corresponding to the low temperature fluid passage 3 and the high temperature fluid passage 4, and diffusion bonding is used for joining the component members. Thereby, a complicated structure can be realized and the number of processing steps can be reduced.

  In FIG. 2, the number of through holes 3 a constituting the high-temperature fluid passage 3 is relatively small for convenience of drawing, but it is preferable that the number of through holes 3 a is large. The shape of the through hole 3a is not limited to a circular shape, and may be a rectangular shape. The through hole 3a can be easily configured by etching or punching out by a mold.

  Next, an overall view of the heat exchanger 1 having the laminate core 5 as described above is shown in FIG.

  Plates (not shown) having through holes at positions overlapping the high temperature fluid passage 3 and positions not overlapping holes at the positions overlapping the low temperature fluid passage 4 are formed at the uppermost and lowermost portions of the laminate core 5 in which the plates 2 are laminated. Laminate. Furthermore, a high-temperature fluid manifold 3 and a low-temperature fluid manifold 7 that distribute the high-temperature fluid and the low-temperature fluid to the high-temperature fluid passage 3 and the low-temperature fluid passage 4 of the laminate core 5 are provided. The high-temperature fluid manifold 6 is configured by a high-temperature fluid inlet manifold 6 i and a high-temperature fluid outlet manifold 6 o that are communicated with the end of the high-temperature fluid passage 3 and are configured along the stacking surface at the stack direction end of the stacked body core 5. On the other hand, the cryogenic fluid manifold 7 is composed of a cryogenic fluid inlet manifold 7 i and a cryogenic fluid outlet manifold 7 o that communicate with the end of the passage 4 a and are configured along the side surface of the laminated core 5. The high temperature fluid manifolds 6i, 6o and the low temperature fluid manifolds 7i, 7o are provided with fluid inlets / outlets 8i, 8o, 9i, 9o, respectively.

  The hot fluid is introduced from the hot fluid inlet 8i into the hot fluid inlet manifold 6i and distributed to the hot fluid passage 3 constituted by the respective through holes 3a. Heat exchange is performed when circulating in the high-temperature fluid passage 3, a relatively low temperature state is obtained, and the heat is recovered by the high-temperature fluid outlet manifold 6 o and discharged from the high-temperature fluid outlet 8 o.

  On the other hand, the cryogenic fluid is introduced from the cryogenic fluid inlet 9i into the cryogenic fluid inlet manifold 7i and distributed to the respective passages 4a. Since the low-temperature fluid flowing through the passage 4a can freely go back and forth between the passages 4a at the communication portion with the passage 4b, the pressure and the evaporation state between the passages 4a are made uniform. Thereafter, the refrigerant is again collected through the passage 4a to the cryogenic fluid outlet manifold 7o and discharged from the cryogenic fluid outlet 9o. At this time, the low temperature fluid evaporates by heat exchange with the high temperature fluid, and is discharged in the state of water vapor.

  As described above, the low-temperature fluid distributed to each passage 4a is configured to be movable between the passages 4a via the passage 4b. By connecting the plurality of passages 4a through the passages 4b, the respective pressures in the passages 4a can be made uniform. Further, in the stacked heat exchanger 1, the bonding stacking direction E (stacking direction of the plates 2) at the time of manufacture and the direction F (planar direction of the plates 2) in which the passages 4a are arranged are orthogonal to each other. That is, as shown in FIG. 2, the low-temperature fluid is configured to flow perpendicularly to the stacking direction of the plates 2, which is the flow direction of the high-temperature fluid.

  Next, the effect of this embodiment will be described.

  A low-temperature fluid passage 4 having a plurality of high-temperature fluid passages 3 that circulate a high-temperature fluid, a plurality of passages 4 a that circulate a low-temperature fluid, and at least one passage 4 b that communicates the passages 4 a with each other. Heat exchange is possible between the fluid flowing through the high-temperature fluid passage 3 and the low-temperature fluid passage 4. Thereby, since the low temperature fluid distributed to each passage 4a can move between passages 4a in passage 4b, the pressure state and heat exchange state of the low temperature fluid in heat exchanger 1 are made uniform in a plurality of passages 4a. can do. Further, when an evaporator is used as the heat exchanger 1, the state of the steam discharged from the plurality of passages 4a can be made uniform. As a result, in the relatively compact heat exchanger 1 having a plurality of fluid passages 3 and 4, variation in inflow of low-temperature fluid can be suppressed.

  A laminated body core 5 formed by laminating a plurality of plate-like plates 2 is provided, and a high-temperature fluid passage 3 is provided with a passage penetrating the laminated body core 5 in the laminating direction. In addition, the passage 4 a includes a plurality of layers formed along the laminated section of the laminated core 5. Further, as the passage 4b, the passage 4a is communicated and provided with at least one layer formed along the laminated cross section of the laminated body core 5, thereby performing efficient heat exchange and between the plurality of passages 4a. The fluid pressure and vapor state can be made uniform.

  Etching is used for processing the fluid passages 3 and 4, and brazing or diffusion bonding is used for joining the plates 2. Thereby, it is possible to secure the degree of freedom of processing, reduce the number of processing steps, and reduce the cost.

  Next, a second embodiment will be described. The configuration of the heat exchanger 1 is shown in FIG. Hereinafter, a description will be given centering on differences from the first embodiment.

  FIG. 4 shows the configuration of the plate 12. As the plate 12, the laminated core 15 is configured by laminating a high temperature fluid plate 12 h constituting the high temperature fluid passage 13 and a low temperature fluid plate 12 c constituting the low temperature fluid passage 4.

  As shown in FIG. 4A, the layered high-temperature fluid passage 13 is configured so that the high-temperature fluid flows in substantially one direction along one plane of the high-temperature fluid plate 12h. A pair of plate edge portions 121h configured along the flow direction side surface of the high-temperature fluid is configured to protrude in the thickness direction with respect to the plane of the plate 12h, thereby forming a channel side wall. The other opposing plate edge 122 h is an entrance / exit part of the high-temperature fluid passage 13.

  A cylindrical protrusion 124h having a through-hole 123h penetrating through the high-temperature fluid plate 12h in the thickness direction is provided at the center of the plane that forms the high-temperature fluid passage 13 of the high-temperature fluid plate 12h. The hollow-shaped protrusion 124h is configured at a position overlapping with a protrusion 124c provided on the low-temperature fluid plate 12c described later in the stacking direction. The height of the protrusion 124h is substantially the same as the plate edge 121h that constitutes the flow path side wall. The plate edge 121h and the protrusion 124h serve as a joint with the adjacent plate 12 during lamination.

  Further, as shown in FIG. 4B, the low-temperature fluid passage 14 is constituted by a passage 14a formed along one surface of the low-temperature fluid plate 12c, a projection 124h described above, and a projection 124c described later. The passage 14b is formed by combining the through holes 123h and 123c and the through holes 125c provided on the side surfaces of the protrusions 124c.

  The passage 14a is configured so that the cryogenic fluid flows in a layered manner in substantially one direction along one plane of the cryogenic fluid plate 12c. A pair of plate edge portions 122c configured along the flow direction side surface of the low-temperature fluid in the passage 14a is configured to protrude in the thickness direction with respect to the plate plane, thereby forming a channel side wall. The other opposing plate edge 121c is an entrance / exit part of the passage 4a.

  When the high temperature fluid plate 12h and the low temperature fluid plate 12c are stacked, the plate edge portion 121h and the plate edge portion 121c are configured so that the plate edge portion 122h and the plate edge portion 122c overlap in the stacking direction. That is, the flow direction of the high-temperature fluid in the high-temperature fluid passage 13 and the low-temperature fluid in the passage 14a are configured to be substantially orthogonal.

  Further, a cylindrical protrusion 124c having a through-hole 123c penetrating through the low-temperature fluid plate 12c in the thickness direction is provided at the center on the plane constituting the passage 14a of the low-temperature fluid plate 12c. The plurality of hollow projections 124c are configured substantially evenly on a plane. The height in the thickness direction of the protruding portion 124c is set to the same height as the plate edge portion 122c constituting the flow path side wall. The plate edge 122c and the protrusion 124c serve as a joint with the adjacent plate 12 when stacked.

  When the high temperature fluid plate 12h and the low temperature fluid plate 12c are stacked, the protrusion 124c and the protrusion 124h are configured to overlap each other. Thereby, the through-holes 123c and 123h provided in the center of the cylindrical shape are continuous, and the passage 14b penetrating the stacked body core 15 in the stacking direction is configured. A through hole 125c communicating with the through hole 123c is provided on the side surface of the protrusion 124c. That is, the passage 14b and the passage 14a communicating in the stacking direction are configured to communicate with each other.

  By laminating such high temperature fluid plates 12h and low temperature fluid plates 12c alternately, a laminated body core 15 as shown in FIG. 5B is configured. The passage 14a of the high-temperature fluid passage 13 and the low-temperature fluid passage 14 is isolated by a plate plane.

  Further, as shown in FIG. 5A, high temperature fluid manifolds 16 i and 16 o and low temperature fluid manifolds 17 i and 17 o are provided along the side surface of the laminated body core 15. The high-temperature fluid manifolds 16i and 16o are configured to communicate with the high-temperature fluid passage 13 through the plate edge portion 122h, which is an opening, and not to communicate with the low-temperature fluid passage 14. Further, the low-temperature fluid manifolds 17i and 17o are configured to communicate with the passage 14a via the plate edge portion 121c that is an opening, and are not communicated with the high-temperature fluid passage 13. Similarly to the first embodiment, the manifolds 16i, 16o, 17i, and 17o are provided with fluid inlets and outlets 18i, 18o, 19i, and 19o, respectively.

  In such a heat exchanger 1, the high-temperature fluid introduced from the high-temperature fluid inlet 18i to the high-temperature fluid inlet manifold 16i is distributed to the high-temperature fluid passages 13 of the respective layers and flows in substantially one direction along the lamination surface. At this time, heat exchange with the low-temperature fluid flowing through the adjacent layers is performed, a relatively low temperature state is obtained, and the heat is recovered by the high-temperature fluid outlet manifold 16o and discharged from the high-temperature fluid outlet 18o. That is, the high-temperature fluid flows through the laminated core 15 independently for each layer.

  On the other hand, the cryogenic fluid introduced from the cryogenic fluid inlet 19i into the cryogenic fluid inlet manifold 17i is distributed to the passage 14a. A part of the low-temperature fluid flowing through the passage 14a flows into the passage 14b and flows in the stacking direction. For this reason, the low-temperature fluid can freely move between the layer-shaped passages 4a through the passages 14b, and the temperature state and the evaporation state can be made uniform.

  In other words, the laminated heat exchanger 1 is configured by providing the laminated core 15 with a hollow communication structure passage 14b having a through hole 125c that penetrates in the lamination direction and communicates only with the passage 14a. In other words, the laminated core 15 may be constituted by a pipe-shaped member as shown in FIG. 5C, and the passage 14b having the through hole 125c on the side surface may be inserted.

  Further, by providing the protrusions 124h and 124c in the high-temperature fluid passage 13 and the passage 14a, turbulent flows are generated in the flows of the high-temperature fluid and the low-temperature fluid, and heat transfer is promoted. Furthermore, since the protrusions 124h and 124c are configured to overlap each other in the stacking direction, an effect of improving rigidity can be obtained.

  Etching and diffusion bonding are used for the processing and bonding of the passage shape as in the first embodiment.

  Next, the effect of this embodiment will be described. Only the effects different from those of the first embodiment will be described below.

  A high temperature fluid plate 12h provided with the high temperature fluid passage 13 and a low temperature fluid plate 12c provided with the passage 4a are laminated. Furthermore, as the passage 4b, a hollow-shaped protrusion 124 having a through-hole 123 that penetrates the laminated core 15 in the stacking direction and having a communication hole 125 that communicates between the through-hole 123 and the passage 4a on the side surface. Prepare. Here, the passages 14b penetrating in the stacking direction are formed by combining the protrusions 124h and 124c. Thereby, the movement of the low-temperature fluid between the different passages 14a becomes possible, and the pressure and the evaporation state of the low-temperature fluid can be made uniform.

  Further, the protrusion 124 is formed in a cylindrical shape. Such protrusions 124 are configured to be distributed on the plane of the plate 12. Here, the protrusion 124 is constituted by a protrusion provided on at least the high-temperature fluid plate 12h of the high-temperature fluid plate 12h and the low-temperature fluid plate 12c and having a height substantially equal to the maximum plate thickness. Thereby, it can join to the adjacent plate 12, can maintain durability, and can suppress the low-temperature fluid leakage to the high-temperature fluid channel | path 3. FIG.

  Next, a third embodiment will be described. The structure of the laminated body core 5 of the heat exchanger 1 is shown in FIG. Hereinafter, a description will be given centering on differences from the second embodiment.

  The high-temperature fluid plate 22h is provided with a cylindrical protrusion 224h having a through-hole 223h penetrating in the plate thickness direction. On the other hand, the low temperature fluid plate 22c is not provided with a protrusion, and only the through-hole 223c penetrating the plate in the thickness direction is provided.

  Thereby, the low-temperature fluid flowing through the passages 24a provided along the plane of each low-temperature fluid plate 22c passes through the protrusions 224h of the high-temperature fluid plate 22h adjacent in the stacking direction and is further adjacent to the low-temperature fluid plate. It is configured to be movable in the passage 24a of 22c. That is, the low-temperature fluid passage 24 is constituted by the passage 24a configured along the plane of the low-temperature fluid plate 22c, the through hole 223h of the protrusion 224h, and the through hole 223c, and passes through the high-temperature fluid plate 22h, thereby passing the passage 24a The passage 24b communicates with each other. Thereby, the low temperature fluid in the laminated body core 25 can go back and forth between the passages 24a provided in the adjacent low temperature fluid plate 22c via the high temperature fluid plate 22h, and the pressure and the evaporation state can be made uniform. .

  In FIG. 6, for convenience, the high-temperature fluid plate 22h and the low-temperature fluid plate 22c are shown as box-shaped configurations, but the configurations shown in FIGS. 4 and 5 may be used. Etching and diffusion bonding are used for the processing and bonding of the passage shape as in the first embodiment.

  Next, the effect of this embodiment will be described. Hereinafter, only effects different from those of the second embodiment will be described.

    A high temperature fluid plate 22h provided with a high temperature fluid passage 3 comprising a second laminate formed by laminating a second plate provided with the high temperature fluid passage and a third plate provided with the first low temperature fluid passage; The laminate core 25 is formed by laminating a low-temperature fluid plate 22c provided with 24a. Furthermore, as the passage 24b, a hollow-shaped protrusion 224h that communicates between the passages 24a of the low-temperature fluid plates 22c adjacent in the stacking direction via the high-temperature fluid plate 22h is provided. As described above, even when the low temperature fluid plate 22c is not provided with the protrusion and is provided only on the high temperature fluid plate 22h, the low temperature fluid can be moved between the adjacent low temperature fluid plates 22c via the high temperature fluid plate 22h. can do.

  Next, a fourth embodiment will be described. Hereinafter, a description will be given centering on differences from the first embodiment.

  FIG. 7A shows a plan view of the cryogenic fluid plate 32c. The low-temperature fluid passage 34 includes a passage 34a configured along the plate plane and a passage 34b penetrating in the stacking direction.

  The passage 34a is formed in a folded shape. At this time, the flow path cross section is configured to be larger in the upstream region than the folded portion of the passage 34a than in the downstream region. The upstream end of the passage 34a communicates with the cryogenic fluid inlet manifold 37i, and the downstream end thereof communicates with the cryogenic fluid outlet manifold 37o. The cryogenic fluid manifolds 37i and 37o are formed on the same outer edge portion 321c on the plate plane.

  Further, a part of the passage 34a is configured to communicate with the passage 34b penetrating in the stacking direction. The passage 34b is configured by a combination of a through hole 323c provided in the low-temperature fluid plate 32c and penetrating the plate in the thickness direction, and a through hole 323h of a flow path wall 324h configured in a hollow shape as will be described later. Here, it is configured such that a part of the upstream region and a part of the downstream region of the passage 34a having a relatively large cross-sectional area communicate with the passage 34b. As shown in FIG. 7A, a communication hole 323c is formed by a hole that is continuous in a direction crossing the passage 34a at the approximate center of the plate plane.

  On the other hand, as shown in FIG. 7B, the high-temperature fluid passage 33 is configured so that the high-temperature fluid flows in substantially one direction along the plane of the high-temperature fluid plate 32h. The flow direction of the high temperature fluid and the low temperature fluid is configured to be substantially orthogonal. The high-temperature fluid passage 33 is composed of two passages, and a flow passage wall 324h having a hollow shape is provided between the passages. The inside of the flow path wall 324h has a through hole 323h that penetrates the high temperature fluid plate 32h. The through hole 323h is provided at a position overlapping the through hole 323c provided in the low-temperature fluid plate 32c described above in the stacking direction, and penetrates the stacked body core 25 in the stacking direction by combining the through holes 323c and 323h. A passage 34b is formed.

  Here, the number of flow path walls 324h is one, but this is not restrictive, and a plurality of flow path walls 324h may be provided. Further, the processing and joining of the passage shape use etching and diffusion joining as in the first embodiment.

  Such a low-temperature fluid plate 32c and a high-temperature fluid plate 32h are alternately laminated to constitute a laminated body core 35, thereby constituting a heat exchanger 1 as shown in FIG.

  Cryogenic fluid is introduced from a cryogenic fluid inlet 39i and distributed to the cryogenic fluid passages 34a of each layer in a cryogenic fluid inlet manifold 37i. When flowing through the low-temperature fluid passage 34a, the low-temperature fluid can freely go back and forth between the passages 34a formed in different layers via the passage 34b. On the other hand, the high-temperature fluid flows along the high-temperature fluid passage 33 formed in each layer, as in the first embodiment.

  Next, the effect of this embodiment will be described. Only the effects different from those of the first embodiment will be described below.

  The communication portion is configured in a rectangular shape substantially orthogonal to the flow direction of the passage 34a. Here, it is rectangular, and is constituted by a flow path wall 324h having a through hole 323h therein. The rectangular channel wall 324h is configured to cross the channel cross section of the passage 34a. As a result, the entire low-temperature fluid flow can be moved, so that the pressure and evaporation state of the low-temperature fluid can be made uniform.

  Next, a fifth embodiment will be described. Hereinafter, a description will be given centering on differences from the fourth embodiment.

  As shown in FIG. 9A, the cryogenic fluid passage 44a is formed in a three-stage meandering shape along the surface of the cryogenic fluid plate 42c. At this time, the two folded portions 441 are configured by the manifold 423. The manifold 423 may be configured in the plate plane, or may be provided on the side surface of the laminate core 45 as shown in FIG. The manifold 423 is configured to allow the movement of the layer pipe of the low-temperature fluid flowing through the passage 44a provided in each layer. That is, the manifold 423 is used as the passage 44b that enables the movement of the low-temperature fluid between the passages 43a. Further, cryogenic fluid manifolds 47i and 47o are provided at both ends of the passage 44a. At this time, the manifold 423 and the cryogenic fluid manifolds 47i and 47o are configured in a pair of opposed plate edge portions 421c.

  Moreover, as shown in FIG.9 (b), the high temperature fluid channel | path 43 which distribute | circulates a high temperature fluid to one direction is provided in the high temperature fluid plate 42h plane. Further, when the low-temperature fluid plate 42c and the high-temperature fluid plate 42h are stacked, the above-described manifold 423 is disposed on the plate edge 421h that is an area overlapping the plate edge 421c. As in the fourth embodiment, the manifold 423 may be configured by providing a flow path wall of the high-temperature fluid plate 42h. Note that the processing and bonding of the passage shape uses etching and diffusion bonding as in the first embodiment.

  By laminating such a high temperature fluid plate 42h and a low temperature fluid plate 42c, a laminate core 45 as shown in FIG. 10 is formed. As a result, the low-temperature fluid dispersed in each layer can freely travel to and from the passage 44a formed in a different layer through the passage 44b in the folded portion 441 of the passage 44a.

  Next, the effect of this embodiment will be described. Only the effects different from those of the fourth embodiment will be described below.

  The passage 44a is provided with a flow path having at least one folded portion 441 at a flat end provided in the cryogenic fluid plate 42c. In addition, a manifold 423 is provided as a communication portion, which is connected to the folded portion 441, which is not connected to the high-temperature fluid passage 3 and is connected to the passage 44a. Thereby, since the low temperature fluid can move between the passages 44a configured in different layers, the pressure and the vapor state of the low temperature fluid can be made uniform.

  Next, a sixth embodiment will be described. The structure of the laminated body core 55 used for the heat exchanger 1 is shown in FIG. Hereinafter, a description will be given centering on differences from the first embodiment.

  The laminated core 55 is configured by laminating a plurality of plates 52. The laminated core 55 includes a high-temperature fluid passage 53 that penetrates the laminated core 55 in the laminating direction by through holes 53 a provided in each plate 52. The diameter of the through-hole 53a provided in each plate 52 is configured to change in the stacking direction. That is, the flow path cross section of the high-temperature fluid passage 53 is configured to change in the stacking direction.

  For example, in FIG. 11, two plates 52x having through holes 53a having the same diameter φd and one plate 52y having through holes 53a having a half diameter φ0.5d are alternately stacked. By doing so, the laminate core 55 is configured. Thereby, turbulent flow is likely to occur in the high-temperature fluid passage 53, and the heat transfer rate can be improved. Note that the processing and bonding of the passage shape uses etching and diffusion bonding as in the first embodiment.

  Next, the effect of this embodiment will be described. Only the effects different from those of the first embodiment will be described below.

  The shape of the passage forming portion of the plate 52 constituting the high temperature fluid passage 53 and the low temperature fluid passage 54 is changed in the stacking direction. Here, the cross-sectional area of the high-temperature fluid passage 53 is changed in the stacking direction. Thereby, since a turbulent flow is generated in the flow in the high-temperature fluid passage 53, the heat transfer rate can be further improved.

  Next, a seventh embodiment will be described. The structure of the laminated body core 65 used for the heat exchanger 1 is shown in FIG. Hereinafter, a description will be given centering on differences from the first embodiment.

  The laminate core 65 is configured by laminating a plurality of plates 62. A high-temperature fluid passage 63 that penetrates the laminated body core 65 in the laminating direction is constituted by the through holes 63 a provided in each plate 62. Here, the position of the through hole 63a is configured to change in the stacking direction. That is, the flow path axis of the high-temperature fluid passage 63 is configured to be a curve or a broken line. However, the high-temperature fluid passage 63 constituted by the through holes 63a is a flow passage that is continuous in the stacking direction.

  For example, as shown in FIG. 12, each plate 62 is penetrated so that the distance from the plate edge to the center of the through hole 63a is changed to α, α + β, α + 2 × β, α + 3 × β, α + 2 × β, α + β. A hole 63a is formed.

  Note that the processing and bonding of the passage shape uses etching and diffusion bonding as in the first embodiment.

  Next, the effect of this embodiment will be described. Only the effects different from those of the first embodiment will be described below.

  The position of the passage forming portion of the plate 52 constituting the high temperature fluid passage 63 and the low temperature fluid passage 64 is changed in the stacking direction. At least one flow path axis of the high temperature fluid passage 63 or the low temperature fluid passage 64 is formed in a curved line or a broken line shape. Here, the flow path axis of the high-temperature fluid passage 63 is formed in a curve or a broken line. Thereby, since a turbulent flow is generated in the flow in the high-temperature fluid passage 63, the heat transfer rate can be improved.

  Next, an eighth embodiment will be described. The structure of the laminated body core 75 used for the heat exchanger 1 is shown in FIG. Hereinafter, a description will be given centering on differences from the first embodiment.

  Similarly to the first embodiment, the low-temperature fluid passage 74 is formed in a layer shape along the laminated section of the laminate core 75, and a plurality of layer-shaped passages 74a and a passage 74b communicating the plurality of passages 74a. It consists of. A plurality of protrusions 76 projecting inward are provided on the flow path wall surface of the low-temperature fluid passage 74. Here, a plurality of protrusions 76 are provided on both wall surfaces of the passages 74a and 74b, respectively, but only one of them may be provided. Thereby, since a heat transfer area increases, the heat exchange property of a low-temperature fluid is improved. Note that the processing and bonding of the passage shape uses etching and diffusion bonding as in the first embodiment.

  Next, the effect of this embodiment will be described. Only the effects different from those of the first embodiment will be described below.

  Protruding fins are provided on at least one flow path wall of the high temperature fluid passage 73 or the low temperature fluid passage 74. Thereby, a heat transfer area can be increased and heat exchange property can be improved.

  Next, a ninth embodiment will be described. The structure of the laminated body core 85 used for the heat exchanger 1 is shown in FIG. Hereinafter, a description will be given centering on differences from the first embodiment.

  The laminate core 85 is configured by laminating a plurality of plates 82. By providing the through holes 83a in each plate 82, a high temperature fluid passage 83 penetrating in the stacking direction is formed in the stacked body core 85. The through hole 83a is configured to connect a plurality of circular through holes in the plate plane. Here, as shown in FIG. 14, one through-hole 83 a is provided in one plate plane region divided by low-temperature fluid passages 84 a and 84 b configured in a layer shape. Thereby, absorption of the heat | fever elongation of the plate 82 becomes favorable and durability can be improved. Note that the processing and bonding of the passage shape uses etching and diffusion bonding as in the first embodiment.

  Next, the effect of this embodiment will be described. Only the effects different from those of the first embodiment will be described below.

   The cross section of at least one of the hot fluid passage 83 or the cold fluid passage 84 is configured to have a major axis along one direction of the plate plane. Thereby, when the plate 82 expands and contracts due to a temperature change, this can be absorbed and durability can be improved.

  The present invention is not limited to the best mode for carrying out the invention, and it goes without saying that various modifications can be made within the scope of the technical idea described in the claims. Absent.

  The present invention can be applied to a heat exchanger. In particular, an appropriate effect can be obtained by applying to an evaporator. Moreover, an appropriate effect can be acquired by applying to the heat exchanger used for the system in which compactization is requested | required like the case where it uses for a moving body.

It is a figure which shows the distribution | circulation state of the fluid to the heat exchanger in 1st Embodiment. It is a block diagram of the laminated body core used for the heat exchanger of 1st Embodiment. It is a block diagram of the heat exchanger and laminated body core of 1st Embodiment. It is a block diagram of the plate used for the heat exchanger of 2nd Embodiment. It is a block diagram of the heat exchanger and laminated body core of 2nd Embodiment. It is a block diagram of the laminated body core used for the heat exchanger of 3rd Embodiment. It is a top view of the plate used for the heat exchanger of 4th Embodiment. It is the structure of the heat exchanger and laminated body core of 4th Embodiment. It is a top view of the plate used for the heat exchanger of 5th Embodiment. It is a block diagram of the heat exchanger and laminated body core of 5th Embodiment. It is a block diagram of the laminated body core used for the heat exchanger of 6th Embodiment. It is a block diagram of the laminated body core used for the heat exchanger of 7th Embodiment. It is a block diagram of the laminated body core used for the heat exchanger of 8th Embodiment. It is a block diagram of the laminated body core used for the heat exchanger of 9th Embodiment.

Explanation of symbols

1 Laminated heat exchanger 2 Plate 3, 13, 23, 33, 43, 53, 63, 73 Hot fluid passage 4, 14, 24, 34, 44, 54, 64, 74 Cold fluid passage 5, 15, 25, 55, 65, 75 Laminate core

Claims (10)

A plurality of high-temperature fluid passages for circulating the high-temperature fluid;
A low-temperature fluid passage having a plurality of first low-temperature fluid passages through which a low-temperature fluid flows, and at least one second low-temperature fluid passage communicating the first low-temperature fluid passage with each other,
A heat exchanger characterized by enabling heat exchange between fluids flowing through the high-temperature fluid passage and the low-temperature fluid passage. Comprising a first laminate formed by laminating a plurality of flat plate-shaped first plates;
As the high temperature fluid passage, comprising a passage penetrating the first laminate in the lamination direction,
As the first low-temperature fluid passage, comprising a plurality of layers formed along the laminated section of the first laminate,
2. The heat exchanger according to claim 1, wherein the second low-temperature fluid passage includes at least one layer that communicates with the first low-temperature fluid passage and is formed along a laminated section of the first laminated body. A second laminate formed by laminating the second plate provided with the high-temperature fluid passage and the third plate provided with the first low-temperature fluid passage;
Furthermore, the said 2nd low temperature fluid channel | path is provided with the hollow-shaped communication part which connects between the said 1st low temperature fluid channel | paths of the 3rd plates adjacent via the said 2nd plate in the lamination direction. Heat exchanger. A second laminate formed by laminating the second plate provided with the high-temperature fluid passage and the third plate provided with the first low-temperature fluid passage;
Furthermore, as the second low-temperature fluid passage, a through-hole penetrating the second laminated body in the laminating direction is provided inside, and a communication hole communicating between the through-hole and the first low-temperature fluid passage is provided on a side surface The heat exchanger according to claim 1, comprising a hollow communication portion.   The heat exchanger according to claim 3 or 4, wherein the communication portion is configured in a cylindrical shape.   The heat exchanger according to claim 3, wherein the communication portion is configured in a rectangular shape substantially orthogonal to the flow direction of the first low-temperature fluid passage.   The communication portion is configured by a protrusion provided on at least the second plate of the second plate and the third plate and having a height substantially equal to the maximum plate thickness. The heat exchanger as described in. As the first low-temperature fluid passage, provided with a flow path having at least one folded portion at a flat end provided on the third plate,
5. The heat exchanger according to claim 3, wherein the communication portion includes a manifold that is not connected to the high-temperature fluid passage and is connected to the low-temperature fluid passage in the folded portion.   The heat exchanger according to claim 2, wherein a shape or a position of a passage forming portion of the first plate constituting the high temperature fluid passage and the low temperature fluid passage is changed in the stacking direction.   The heat exchanger according to claim 1, wherein etching is used for processing the fluid passage, and brazing or diffusion bonding is used for joining the plates.

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