JP2003262489A - Plate type heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a plate type heat exchanger having a small pressure loss and a high heat transmission efficiency by suppressing occurrence of exfoliation and deviation of fluid and a stagged area. <P>SOLUTION: This plate type heat exchanger 1 is provided with a plurality of heat transmission plates 2 stacked with one another and having clearances 4 between layers, and partition walls 3 interposed between the clearances 4, having inlets 51 and outlets 52 opened in the edge parts of the heat transmission plates 2, and partitioning and forming interlayer passages extending in the surface direction of the heat transmission plates 2. Fluid having different temperatures alternately flows in the clearances 4 adjoined in the stacking direction in the both sides of the heat transmission plates 2 so as to exchange heat via the heat transmission plates 2. At least, one of the interlayer passages is a flow control passage 5 having a flow control means 6 controlling the flow of the fluid flowing therein from the inlet 51 and flowing thereout from the outlet 52. <P>COPYRIGHT: (C)2003,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a plate heat exchanger having a structure in which a plurality of heat transfer plates are laminated and a flow path is formed between the heat transfer plate layers.

[0002]

2. Description of the Related Art Generally, in a plate heat exchanger, a large number of heat transfer plates serving as heat transfer surfaces are stacked and a flow path is formed between the heat transfer plate layers to form a flow path between the heat transfer plates. Heat exchange is performed by alternately flowing a high temperature fluid and a low temperature fluid.

This type of heat exchanger includes heat transfer plate interlayers for the purpose of ensuring the sealing property of the fluid to be heat-exchanged, maintaining the structural strength, and suppressing the bias of the fluid flowing through the flow paths. There is a partition wall. A flow path is formed between the heat transfer plate layers by the partition wall. Here, FIG. 16 shows a perspective view of a flow path structure in a conventional plate heat exchanger. As shown in FIG. 16, the plate heat exchanger 100 includes a heat transfer plate 110 and a partition wall 12.
With 0 and. A plurality of heat transfer plates 110 are stacked, and a gap 130 is provided between the layers. A plurality of partition walls 120 are interposed in the gap 130. The partition walls 120 have a prismatic shape and are arranged in parallel with each other with a space therebetween. The partition wall 120 partitions the gaps 130, and each of the gaps 130
A plurality of interlayer flow paths 140 are formed for each. The interlayer flow passage 140 has an inflow port 141 opening to one edge of the heat transfer plate 110 and an outflow port 142 opening to the other edge of the heat transfer plate 110 facing the inflow port 141. Extending in the plane direction. Heat transfer plate 110
In the gaps 130 that are adjacent to each other in the stacking direction, the partition walls 120 that are arranged differ in direction by 90 degrees. Therefore, the interlayer flow paths 140 in the gaps 130 that are adjacent to each other in the stacking direction, that is, the vertical direction, are formed to intersect each other with the heat transfer plate 110 interposed therebetween. The fluid flows in through the inflow port 141 and outflow through the outflow port 142 of the interlayer flow passages 140 formed in the gaps 130 that are vertically adjacent to each other with the heat transfer plate 110 interposed therebetween, and undergoes heat exchange.

[0004]

In the heat exchanger having the above-mentioned conventional structure, when the fluid flows into the interlayer flow passage formed between the heat transfer plate layers, the end of the partition wall forming the interlayer flow passage is formed. There was a problem that the fluid separated from the partition wall due to the contraction phenomenon in the part. That is, when the fluid that has proceeded straight to the interlayer flow path collides with the end portion of the partition wall at the inflow port, the inflow cross-sectional area decreases and the flow direction changes, so that the fluid flows away from the partition wall. This separation of the fluid increases the pressure loss when the fluid flows in. Further, a vortex is generated behind the separation point, a stagnation region is generated, and a low pressure state is created. That is, the fluid once separated from the partition wall is less likely to flow near the side portion of the partition wall downstream of the inflow port, and a so-called stagnation area where the flow is stagnant is generated near the side portion of the partition wall. When a stagnation region occurs in the interlayer flow passage, the flow passage becomes substantially narrower by that amount. Therefore, the flow path loss increases and the effective heat transfer area decreases. That is, the utilization rate of the heat transfer area is reduced. Further, when a stagnation area is generated in the interlayer flow passage, dust or the like is likely to be accumulated in the vicinity of the side portion of the partition wall, which may lead to blockage of the flow passage. On the other hand, when the interlayer flow passage is formed in a curved shape instead of a straight shape, there is a problem that the flow is biased in the interlayer flow passage.

The present invention has been made in view of the above circumstances, and by controlling the flow in the interlayer flow passage,
It is an object of the present invention to provide a plate heat exchanger that suppresses fluid separation and unevenness, and the occurrence of a stagnation region in an interlayer flow path, has a small pressure loss, and has high heat transfer efficiency.

[0006]

(1) A plate heat exchanger according to the present invention includes a plurality of heat transfer plates that are stacked and have a gap between layers, and an edge of the heat transfer plate that is interposed in the gap. A partition wall having an inflow opening and an outflow opening that open in the surface of the heat transfer plate to extend in the surface direction of the heat transfer plate, and fluids of different temperatures are sandwiched in the stacking direction. A plate-type heat exchanger in which heat is exchanged through the heat transfer plate by alternately flowing through the gaps adjacent to each other, wherein at least one of the interlayer flow paths flows from the inflow port. A flow control flow path having a flow control means for controlling the flow of the fluid flowing out from the outlet.

That is, in the plate heat exchanger of the present invention, a gap is formed between the heat transfer plate layers, and an interlayer flow path is formed in the gap. Then, at least one of the interlayer flow paths is a flow control flow path having a flow control means for controlling the flow of the fluid. By controlling the flow of the fluid in the interlayer flow passage by the flow control means, in the flow control passage, the above-mentioned fluid separation, uneven flow,
Generation of stagnation area is suppressed. As a result, in the flow control channel, a flow with a uniform flow rate distribution can be realized. For example, if the separation of the fluid at the inflow port of the flow control channel is suppressed, the pressure loss at the time of inflow of the fluid is reduced, and the occurrence of a stagnation region downstream of the inflow port is also suppressed. When the generation of the stagnation area is suppressed, the flow passage is widened and the flow passage loss is reduced. As described above, the plate heat exchanger of the present invention has a small pressure loss, a small flow path loss, and can effectively utilize the heat transfer area, so that the heat exchanger has a high heat transfer efficiency.

(2) The plate heat exchanger according to the present invention is implemented in such a manner that the inflow port and the outflow port of the flow control channel are respectively arranged at opposite edges of the heat transfer plate. can do. In other words, in this aspect, the inflow port is arranged at one edge portion of the heat transfer plate, and the outflow port is arranged at the edge portion facing the one edge portion. According to this aspect, the fluid flows more smoothly. In particular, by arranging the inflow port and the outflow port to face each other, the flow control channel can be formed linearly. In this case, since the fluid flows linearly, the pressure loss in the flow control flow path is reduced, and a heat exchanger having more excellent heat transfer performance can be configured.

(3) In the plate heat exchanger of the present invention, the inflow port and the outflow port of the flow control passage are:
It can be implemented in a mode in which they are arranged at the same edge of the heat transfer plate. That is, in this aspect, the flow control channel is formed by bending the flow control channel by arranging the flow inlet and the flow outlet on the same side. According to this aspect, it is possible to easily form a manifold that supplies and discharges two fluids having different temperatures.

(4) In the above aspect (2) or (3), the partition wall is arranged so that the fluids flowing in from the inflow port are once branched, then merged again and flowed out from the outflow port. Is desirable. That is, in this aspect, the flow control flow path is further partitioned by the partition wall to form a branch path in the flow control flow path. For example, in the curved flow control channel, the fluid easily flows in the inner part,
On the contrary, the fluid may not flow easily in the outer portion. That is, there is a possibility that the flow is unbalanced in the flow control channel. In this aspect, by providing the branch passage in the flow control passage, the flow in the flow control passage is less likely to be biased and the flow rate distribution becomes uniform. Moreover, when many partition walls are arranged to branch the flow, the number of partition walls interposed between the heat transfer plate layers increases. That is, since the number of points supporting the heat transfer plates to be laminated increases, the strength of the heat exchanger itself improves as a result.

(5) Further, the above (4) in which the fluid is branched.
When the above aspect is adopted, it is preferable that the flow control means has a flow rate distribution adjusting member that is disposed between the inflow port and the outflow port and that adjusts the flow rate distribution of the branched flow. As described above, in the curved flow control channel, the flow is likely to be biased. Therefore, there is a possibility that the inflow amount may be different for each branch passage divided by the partition wall. In this aspect, a flow rate distribution adjusting member that adjusts the flow rate distribution that flows into the branch passage is arranged as the flow control means. As a result, it is possible to correct the imbalance of the flow rate for each branch in the flow control channel. That is, the flow rate distribution in the flow control channel can be made more uniform.

(6) In the above aspect (5), it is preferable that the flow rate distribution adjusting member is arranged apart from one of the two heat transfer plates sandwiching the flow rate distribution adjusting member. That is, in this aspect, the flow rate distribution adjusting member is arranged on one surface of the two heat transfer plates, and
In this mode, there is a gap between the flow rate distribution adjusting member and the back surface of the other heat transfer plate. That is, the flow rate distribution adjusting member does not have to have a function of completely partitioning the gap like the partition wall. Therefore, unlike the partition wall, the range of selection of the material and shape of the flow rate distribution adjusting member is wide. Further, the partition wall, in addition to forming the interlayer flow path,
It also plays the role of supporting the heat transfer plate. Therefore, when the height of the flow rate distribution adjusting member and the height of the partition wall are the same, the dimensional accuracy of the flow rate distribution adjusting member is required. According to this aspect, since the flow rate distribution adjusting member can be made lower than the height of the partition wall, dimensional accuracy is not so required, and as a result, the heat exchanger can be easily manufactured.

(7) In the plate heat exchanger of the present invention, it is desirable that the flow control means has a separation suppressing member that suppresses separation of the fluid generated at the end of the partition wall. By suppressing the separation of the fluid by the separation suppressing member, the pressure loss at the time of inflow can be reduced. Further, the generation of a stagnation area in the flow control channel can be suppressed. According to this aspect, the heat exchanger has low pressure loss and flow path loss and high heat transfer efficiency. This aspect is more effective when combined with the aspects (2) to (6).

(8) In the aspect of (7) above, it is desirable that the separation suppressing member is disposed near the inflow port. By disposing the separation suppressing member near the inflow port, separation from the partition wall when the fluid flows into the flow control channel is effectively suppressed. As a result, the pressure loss at the time of inflow can be reduced. Furthermore, it is possible to suppress the occurrence of a stagnation area that occurs in the vicinity of the side of the partition wall downstream from the inflow port.

(9) Further, in the above aspect (8),
It is preferable that the separation suppressing member is a narrow width portion that is arranged at an end portion of the partition wall and has a width that narrows toward an upstream side of the fluid flow. By disposing the separation suppressing member at the end portion of the partition wall, separation from the partition wall when the fluid flows into the flow control channel is suppressed. The narrow portion has a shape in which the width becomes narrower toward the upstream side of the fluid flow. Therefore, the resistance of the fluid colliding with the end of the partition wall is reduced,
Fluid tends to flow along the sides of the partition wall. That is, separation of the fluid from the partition wall is suppressed. Furthermore, since the cross-sectional area of the end portion of the partition wall is reduced, the cross-sectional area of the branch inlet, that is, the cross-sectional area of the opening is increased, and the pressure loss at the time of fluid inflow is also reduced.

(10) The plate heat exchanger of the present invention comprises:
It is preferable that the flow control means is provided between the inflow port and the outflow port, and has a stagnation suppressing member that changes a flow direction of the fluid and suppresses stagnation of the fluid. By suppressing the occurrence of the stagnation area in the flow control flow path by the stagnation suppression member, the flow path loss can be reduced. Therefore, according to this aspect, the heat exchanger has a small flow path loss and a large utilization rate of the heat transfer area. In addition,
When this aspect is combined with the aspects (2) to (9),
It is even more effective.

(11) In the above aspect (10), the stagnation suppressing member is preferably a protrusion arranged on the surface of the heat transfer plate. When the fluid collides with the protrusion in the flow control channel, a vortex is generated in the vicinity of the protrusion to stir the flow. Due to the stirring action of the vortex, even if the flow is separated at the inlet, the flow is brought closer to the side of the partition wall thereafter. Therefore, the generation of the stagnation area near the side portion of the partition wall is suppressed.

(12) Further, in the aspect of the above (10), it is preferable that the stagnation suppressing member is an uneven portion arranged on a side portion of the partition wall. When the fluid collides with the uneven portion, a vortex is generated near the uneven portion. As the flow is agitated by this vortex, the flow is brought closer to the side of the partition wall. That is, the generation of the stagnation area near the side portion of the partition wall is suppressed.

(13) The plate heat exchanger of the present invention comprises:
It is desirable to be used for a hydrogen reformer for supplying hydrogen as fuel for a fuel cell. Generally, a hydrogen reformer includes a reformer that produces hydrogen from a hydrocarbon-based fuel and steam by a reforming reaction, and a CO shifter that reduces the concentration of carbon monoxide in the reformed gas as necessary. And a CO remover for removing carbon monoxide in the reformed gas. The reforming reaction in the reformer is performed at a relatively high temperature. on the other hand,
The reaction of reducing the concentration of carbon monoxide or removing carbon monoxide is carried out at a low temperature. Therefore, the reformed gas discharged from the reformer is cooled to a certain extent by the heat exchanger, and C
It is supplied to the O converter or the CO remover. By incorporating and using the plate heat exchanger of the present invention in such a hydrogen reformer, the reformed gas can be efficiently heat-exchanged.

[0020]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the plate heat exchanger of the present invention will be described in detail below. In the embodiment described below, the plate heat exchanger of the present invention is used by incorporating it into a hydrogen reformer for supplying hydrogen as fuel for a fuel cell.

(1) First Embodiment First, the structure of the plate heat exchanger of this embodiment will be described. FIG. 1 shows a perspective view of a flow channel structure in the plate heat exchanger of this embodiment. In FIG. 1, only a part of the flow channel structure is shown in an enlarged manner. That is, in the plate heat exchanger of this embodiment, the flow path structure shown in FIG. 1 is repeatedly developed in the plane direction and the vertical direction of the heat transfer plate.

As shown in FIG. 1, a plate heat exchanger 1
Includes a heat transfer plate 2 and a partition wall 3. The heat transfer plate 2 serving as a heat transfer surface is made of SUS and has a thin plate shape. The size of the heat transfer plate 2 is 150 mm long ×
The width is 150 mm and the thickness is 500 μm. Heat transfer plate 2
Are stacked in the vertical direction. A gap 4 is formed between the layers of the heat transfer plate 2.

A plurality of partition walls 3 are provided in the gap 4. The partition wall 3 is made of SUS and has a width of 500 μm and a height of 5
It has a prismatic shape of 00 μm. The partition walls 3 are spaced apart from each other and arranged in parallel. The separation width of the partition wall 3 is 5 m
m. The partition walls 3 partition the gaps 4, and three flow control channels 5 are formed in each of the gaps 4.

The flow control channel 5 includes an inlet 51 and an outlet 5.
2 and the flow control means 6. The inflow port 51 is open at the edge of the heat transfer plate 2. The outflow port 52 is open at the edge of the heat transfer plate 2 facing the inflow port 51. The inflow port 51 and the outflow port 52 are arranged to face each other, and the flow control channel 5 extends linearly in the surface direction of the heat transfer plate 2. The flow control means 6 includes a narrow portion 61 and fins 62. The flow control means 6 will be described in detail later.

In the gaps 4 which are vertically adjacent to each other with the heat transfer plate 2 interposed therebetween, the partition walls 3 to be arranged are different in direction by 90 degrees. Therefore, the flow control flow paths 5 in the gaps 4 that are vertically adjacent to each other are formed so as to intersect each other with the heat transfer plate 2 interposed therebetween.

Next, the mechanism of heat exchange in the plate heat exchanger of this embodiment will be described. Fluid is the gap 4
Flows in from the inflow port 51 of each flow control channel formed in
It flows out from the outlet 52. Two fluids having different temperatures, that is, a high-temperature reformed gas supplied from a reformer and a low-temperature reformed gas or a reforming fuel gas are respectively provided in vertically adjacent gaps 4 with a heat transfer plate 2 interposed therebetween. By alternately flowing, heat exchange is performed via the heat transfer plate 2.

Next, the flow control flow path will be described in detail by taking one heat transfer plate surface in the flow path structure shown in FIG. 1 as an example. FIG. 2 shows a top view of the heat transfer plate in the plate heat exchanger shown in FIG. As described above, the partition walls 3 are arranged on the surface of the heat transfer plate 2 so as to be spaced apart from each other. The partition wall 3 forms three flow control channels 5. The flow control flow path 5 has a flow control means 6 including a narrow portion 61 and fins 62.

The narrow portion 61 is arranged at the end of the partition wall 3 and has a shape that is pointed toward the edge of the heat transfer plate 2. The narrow portion 61 is formed integrally with the partition wall 3.
The fins 62 are made of SUS, and three fins 62 are arranged near each of the inflow port 51 and the outflow port 52. The fin 62 corresponds to a peeling suppressing member.

The fluid flows into the flow control passage 5 from the inflow port 51. The fluid collides with the narrow portion 61 when flowing in. However, the narrow portion 61 is sharpened with respect to the inflow port 51, that is, toward the upstream. Therefore, the fluid is
Smoothly flows along 1. Therefore, the pressure loss at the time of inflow is small. The narrow width portion 61 is arranged at the end of the partition wall 3. Therefore, as compared with the case where the partition wall 3 has a prismatic shape, the cross-sectional area of the inflow port 51 is increased.
That is, by arranging the narrow width portion 61 at the end portion of the partition wall 3, the change in the opening cross-sectional area becomes gentle, and the inflow loss at the time of inflow of the fluid is further reduced. Further, even if the fluid collides with the narrow width portion 61, the fluid flows smoothly along the narrow width portion 61, so that the direction of the flow does not change much as indicated by the arrow in FIG. Therefore, the fluid is flow control channel 5
Even after flowing into, it flows along the partition wall 3. That is, the separation of the fluid from the partition wall 3 is suppressed.

Further, the fluid also collides with the fins 62 when flowing in. The flow direction changes due to the flow control effect caused by the collision with the fins 62, and the flow direction becomes parallel to the narrow width portion 61. Then, the fluid flowing to the center of the flow control flow path 5 due to separation or the like is pushed toward the partition wall 3. That is, the fluid is brought close to the partition wall 3. Therefore, the separation from the partition wall 3 is suppressed, and the fluid flows along the partition wall 3. Since the fluid flows along the partition wall 3, a stagnation area near the side of the partition wall 3 is less likely to occur. In addition, since the fins 62 are provided in the gaps 4 between the heat transfer plates 2,
Compared to the case where only the partition wall 3 is provided, the number of points that support the heat transfer plates 2 to be stacked increases. Therefore, the joint between the heat transfer plates 2 becomes strong, the fluid sealing property is improved, and the strength of the heat exchanger itself is also improved.

As described above, by disposing the flow control means in the interlayer flow passage, the pressure loss at the time of inflow of the fluid becomes small, and the occurrence of separation and stagnation area is suppressed. That is, in the flow control channel, a flow having a uniform flow rate distribution can be realized.
As a result, the plate heat exchanger of this embodiment is a heat exchanger with high heat transfer efficiency.

Next, a method of manufacturing the plate heat exchanger of this embodiment will be described. The plate heat exchanger of this embodiment can be manufactured by a method including the following three steps.
First, as a first step, a partition wall and a flow control means are formed on the surface of a substrate that is a heat transfer surface by half etching or machining. Then, as a second step, a plurality of substrates on which the partition wall and the flow control means are formed are laminated, and high pressure,
Bonded by a diffusion bonding method at a high temperature to form a laminated body. Further, as a third step, the end portion of the obtained laminated body is cut to obtain the intended laminated body of the heat transfer plate.

In the above method, the partition wall, the flow control means and the substrate, that is, the heat transfer plate are integrally formed. This makes it possible to easily manufacture a heat exchanger having a small flow control flow path. However, the method of forming the partition wall and the flow control means is not limited to the above method. The partition wall and the flow control means may be formed separately from the substrate, and they may be arranged on the surface of the substrate. Further, the method of joining the laminated substrates is not limited to the above method, and various methods such as brazing can be used. In the above method, after laminating a plurality of substrates to form a laminated body, the end portions thereof are cut to obtain a laminated body of heat transfer plates. However, a partition wall and a flow control means may be formed on the heat transfer plate itself, and a plurality of the partition walls and the flow control means may be stacked to form a heat transfer plate laminate. In this case, the substrate in the above method becomes the heat transfer plate, and the third step is omitted. That is, the method for manufacturing a plate heat exchanger of the present invention comprises a first step of forming a partition wall and a flow control means on the surface of a substrate which is a heat transfer surface, and a substrate on which the partition wall and the flow control means are formed. A second step of laminating and joining a plurality of layers may be included.

(2) Second Embodiment The difference between this embodiment and the first embodiment is that a prism is arranged instead of the narrow width portion and the fins as the separation suppressing member. Since the other configurations are the same as those of the first embodiment, only the differences will be described here.

FIG. 3 shows a top view of the heat transfer plate in the plate heat exchanger of this embodiment. The members corresponding to those in FIG. 2 are indicated by the same symbols. As shown in FIG. 3, partition walls 3 are arranged on the surface of the heat transfer plate 2 so as to be separated from each other. The partition wall 3 forms three flow control channels 5. The flow control flow path 5 has a flow control means 6. The flow control means 6 comprises a prism 63. The prism 63 corresponds to a peeling suppressing member. The prism 63 is made of SUS and has an outlet 51.
And one is arranged near each of the inflow ports 52. The distance from the prism 63 to the end of the partition wall 3 arranged on the left side thereof is substantially equal to the distance from the prism 63 to the end of the partition wall 3 arranged on the right side. Also,
The distance from the prism 63 to the end of the partition wall 3 arranged on the left side thereof is substantially equal to the separation width of the partition wall 3. That is, when the prism 63 and the ends of the partition walls 3 arranged on both sides of the prism 63 are connected, a substantially equilateral triangle is formed. In the present embodiment, as in the first embodiment, the partition walls 3 arranged in the gaps 4 vertically adjacent to each other with the heat transfer plate 2 sandwiched therebetween are different in direction by 90 degrees. In addition, the plurality of heat transfer plates 2 are formed by prisms 6
The center of gravity 631 of a triangle that connects 3 and the ends of the partition walls 3 arranged on both sides of the partition wall 3 is positioned above the partition walls 3 (shown by broken lines in the figure) interposed in the adjacent gaps 4. It is stacked.

The fluid flows into the flow control passage 5 from the inflow port 51. The fluid collides with the prism 63 when flowing in.
When the fluid collides with the prism 63, a vortex is generated behind the prism 63. The fluid is agitated by this vortex, and as a result, the separation point generated in the vicinity of the partition wall 3 becomes unstable, and the main flow of the flow approaches the side portion of the partition wall 3. That is, the partition wall 3
From peeling is suppressed. As a result, the fluid easily flows along the partition wall 3, and the occurrence of the stagnation area near the side portion of the partition wall 3 is eliminated.

Since the distance from the prism 63 to the end of the partition wall 3 arranged on the left side thereof is almost equal to the separation width of the partition wall 3, the opening cross-sectional area does not change much. Similarly,
Since the distance from the prism 63 to the end of the partition wall 3 arranged on the right side of the prism 63 is also substantially equal to the separation width of the partition wall 3, the opening cross-sectional area does not change much. Therefore, the increase in pressure loss when the fluid flows in is small.

Further, since the prisms 63 are provided in the gaps 4 between the heat transfer plates 2, there are more points to support the heat transfer plates 2 to be laminated, as compared with the case where only the partition wall 3 is provided. Therefore, the joint between the heat transfer plates 2 becomes strong, the fluid sealing property is improved, and the strength of the heat exchanger itself is also improved. In addition, since the center of gravity 631 of the triangle that connects the prism 63 and the ends of the partition walls 3 arranged on both sides thereof is located on the partition walls 3 interposed in the adjacent gaps 4,
The heat transfer plate 2 can be supported more firmly.

(3) Third Embodiment The difference between this embodiment and the second embodiment is that blocks are laminated and arranged instead of the prisms as the separation suppressing member. Since the other configurations are the same as those of the second embodiment, only different points will be described.

FIG. 4 is a perspective view of the heat transfer plate in the plate heat exchanger of this embodiment. The members corresponding to those in FIG. 3 are indicated by the same symbols. As shown in FIG. 4, partition walls 3 are arranged on the surface of the heat transfer plate 2 so as to be separated from each other. The partition wall 3 forms three flow control channels 5. The flow control flow path 5 has a flow control means 6. The flow control means 6 comprises a block 64. The block 64 corresponds to a peeling suppressing member. The block 64 is made of SUS and has a flat plate shape. Block 64 is the outlet 51
And five each is arranged near the inflow port 52. The blocks 64 are stacked in two stages so that the blocks partially overlap each other. That is, the inflow port 51 and the outflow port 52 are formed in a lattice shape by stacking the blocks 64.

The fluid flows into the flow control channel 5 from the inflow port 51. By flowing in from the inflow port 51 divided into small parts by the block 64, a so-called rectifying grid effect occurs in the fluid. That is, the fluid is divided into small pieces by the blocks 64 and is laminarized by the shearing force generated on the wall surface of each block 64. Due to the flow rectifying lattice effect of the fluid, the fluid smoothly flows near the side portions of the partition wall 3. That is, peeling from the partition wall 3 is suppressed.
As a result, the fluid easily flows along the partition wall 3, and the occurrence of the stagnation area near the side portion of the partition wall 3 is eliminated.

The inflow port 51 is formed in a lattice shape by the block 64. That is, the inflow port 51 is composed of a plurality of divided openings. In the cross section of the inflow port 51, the openings are formed dispersed in the opening width direction of the inflow port 51 and in the vertical direction. The fluid flows through the dispersed openings. Since the openings are dispersed in this way, the flow rate distribution in the width direction and the vertical direction of the flow control channel 5 becomes uniform.

Further, since the block 64 is interposed in the gap 4 between the heat transfer plates 2, the number of points supporting the heat transfer plates 2 to be stacked increases as compared with the case where only the partition wall 3 is provided. Therefore, the joint between the heat transfer plates 2 becomes strong, the fluid sealing property is improved, and the strength of the heat exchanger itself is also improved. Furthermore, the blocks 64 are alternately stacked so that the blocks 64 partially overlap each other. Since the overlapping portion plays a role of a single column in the vertical direction, the heat transfer plate 2 can be more strongly supported.

(4) Fourth Embodiment The difference between the present embodiment and the first embodiment is that only the fins are arranged in place of the narrow width portion and the fins as the separation suppressing member, and further as the flow control means. It has a stagnation suppressing member. Since the other configurations are the same as those of the first embodiment, only different points will be described.

FIG. 5 shows a top view of the heat transfer plate in the plate heat exchanger of this embodiment. The members corresponding to those in FIG. 2 are indicated by the same symbols. As shown in FIG. 5, partition walls 3 are arranged apart from each other on the surface of the heat transfer plate 2. The partition wall 3 forms three flow control channels 5. The flow control flow path 5 has a flow control means 6. The flow control means 6 comprises fins 62 and pins 65.

The fins 62 include the outlet 51 and the inlet 5.
Three are arranged near each two. Fin 62
Corresponds to a separation suppressing member. The pin 65 is made of SUS and has a cylindrical shape. A plurality of pins 65 are arranged between the outflow port 51 and the inflow port 52 and are separated from each other. The pin 65 is a protrusion arranged on the surface of the heat transfer plate 2 and corresponds to a stagnation suppressing member.

In this embodiment, like the first embodiment, the partition walls 3 arranged in the gaps 4 vertically adjacent to each other with the heat transfer plate 2 sandwiched therebetween are different in direction by 90 degrees. Further, the plurality of heat transfer plates 2 are laminated such that some of the pins 65 are located on the partition walls 3 (shown by broken lines in the figure) interposed in the adjacent gaps 4.

The fluid flows into the flow control passage 5 from the inflow port 51. The fluid strikes the fins 62 as they enter. By colliding with the fins 62, the flow direction is changed, and the fluid is controlled to flow parallel to the partition wall 3. That is, since the fluid flows in parallel with the partition wall 3, separation from the partition wall 3 is suppressed, and the fluid easily flows along the partition wall 3.

The inflowing fluid collides with the pin 65 in the flow control channel 5. When the fluid hits the pin 65,
A vortex is generated behind the pin 65. The fluid is agitated by this vortex, and the generated periodic flow approaches the partition wall 3.
Even if the fluid is separated near the inflow port 51, it collides with the pin 65, so that the flow approaches the side of the partition wall and follows the partition wall 3. Like this, pin 6
By arranging 5, the generation of the stagnation area near the side portion of the partition wall 3 is eliminated.

Further, the fins 62 and the pins 65 are provided in the gaps 4 between the heat transfer plates 2 so that the stacked heat transfer plates 2 are supported as compared with the case where only the partition wall 3 is provided. Will increase. Therefore, the joint between the heat transfer plates 2 becomes strong, the fluid sealing property is improved, and the strength of the heat exchanger itself is also improved. In addition, since a part of the pin 65 is located on the partition wall 3 interposed in the adjacent gaps 4, the heat transfer plate 2 can be more firmly supported.

(5) Fifth Embodiment The difference between this embodiment and the fourth embodiment is that baffle plates are arranged instead of pins as stagnation suppressing members. Since the other configurations are the same as those of the fourth embodiment, only different points will be described.

FIG. 6 shows a top view of the heat transfer plate in the plate heat exchanger of this embodiment. The members corresponding to those in FIG. 5 are indicated by the same symbols. As shown in FIG. 6, partition walls 3 are arranged apart from each other on the surface of the heat transfer plate 2. The partition wall 3 forms three flow control channels 5. The flow control flow path 5 has a flow control means 6. The flow control means 6 comprises fins 62 and baffles 66.

The fins 62 include the outlet 51 and the inlet 5.
Three are arranged near each two. Fin 62
Corresponds to the peeling suppressing member. The baffle plate 66 is made of SUS and has a flat plate shape. The baffle plate 66 is the outlet port 5.
A plurality of nozzles 1 and the inflow port 52 are arranged apart from each other. The baffle plate 66 is provided so as to extend vertically from the side portion of the partition wall 3. An uneven portion is formed by the baffle plate 66 and the side portion of the partition wall 3. The baffle plate 66 corresponds to a stagnation suppressing member.

The fluid flows into the flow control passage 5 from the inflow port 51. The fluid strikes the fins 62 as they enter. By colliding with the fin 62, a small vortex is generated at the tip of the fin 62. That is, a vortex is generated in the vicinity of the partition wall 3, the vortex suppresses the separation of the fluid from the partition wall 3 and the generation of the stagnation area, and the fluid easily flows along the partition wall 3.

The fluid flowing in from the inflow port 51 collides with the baffle plate 66 in the flow control channel 5. When the fluid collides with the baffle plate 66, a vortex is generated behind the baffle plate 66. The vortex stirs the fluid, forming a periodic flow. Even if fluid separation occurs near the inflow port 51,
Due to the vortex generated by the collision with the baffle plate 66, the flow is brought close to the side portion of the partition wall and follows the partition wall 3. By disposing the baffle plate 66 in this manner, the occurrence of a stagnation area near the side portion of the partition wall 3 is eliminated.

Further, since the fins 62 and the baffle plates 66 are provided in the gaps 4 between the heat transfer plates 2, the partition wall 3
There are more points to support the heat transfer plates 2 to be laminated, as compared with the case of only one. Therefore, the joint between the heat transfer plates 2 becomes strong, the fluid sealing property is improved, and the strength of the heat exchanger itself is also improved.

(6) Sixth Embodiment In the plate heat exchanger of the present invention, fluids having different temperatures alternately flow through the gaps vertically adjacent to each other with the heat transfer plate interposed therebetween. The difference between the present embodiment and the first embodiment is that the flow control flow paths are different in the vertically adjacent gaps with the heat transfer plate interposed therebetween. Specifically, of the two fluids having different temperatures, the flow control flow path through which the first fluid flows is not linear but curved. On the other hand, the flow control flow path through which the second fluid flows is linearly formed as in the first embodiment. The other configurations are the same as those in the first embodiment. Therefore, in this embodiment, the difference will be described focusing on the flow control flow path through which the first fluid flows.

FIG. 7 shows a top view of the heat transfer plate in the plate heat exchanger of this embodiment, in which the flow control flow path through which the first fluid flows is formed. The members corresponding to those in FIG. 2 are indicated by the same symbols. As shown in FIG. 7, the heat transfer plate 2
A partition wall 3 is arranged on each of the three edges.
The three partition walls 3 form the outer circumference of the flow control channel 5. A partition wall 3 is also arranged in the center of the remaining one edge of the heat transfer plate 2. The partition wall 3 forms an inflow port 51 and an outflow port 52 at both ends of the edge of the heat transfer plate 2. That is, the inflow port 51 and the outflow port 52 are arranged at the same edge of the heat transfer plate 2, and the flow control flow path 5 is formed to be curved in a U shape. Two partition walls 3 are further arranged in the central portion of the heat transfer plate 2. The two partition walls 3 are arranged in parallel with the partition wall 3 forming the inflow port 51 and the outflow port 52. The two partition walls 3 form three branch passages in the flow control passage 5.

The flow control flow path 5 has a flow control means 6.
The flow control means 6 includes a fin 62 and a flow rate distribution adjusting member 67.
Consists of. The fin 62 includes the outflow port 51 and the inflow port 5
Two are arranged near each of the two. Fin 62
Corresponds to the peeling suppressing member. Flow rate distribution adjusting member 67
Is made of SUS and has a thin plate shape. Two flow rate distribution adjusting members 67 are arranged between the inflow port 51 and the outflow port 52. The two flow rate distribution adjusting members 67 are arranged in an inverted C shape from the outflow port 51 and the inflow port 52 toward the edges of the heat transfer plate 2 facing each other.

The fluid flows into the flow control passage 5 from the inflow port 51. The fluid strikes the fins 62 as they enter. The collision of the fins 62 controls the flow direction. Further, the fluid flowing in from the inflow port 51 once branches into each branch passage formed by the partition wall 3, flows in, then merges again, and flows out from the outflow port 52. At that time, the fluid is guided to the flow rate distribution adjusting member 67. That is, the flow rate distribution adjusting member 67 adjusts the flow rate distribution of the flow branched into each branch path. Therefore, there is no bias in the flow rate of each branch in the flow control channel 5, and the flow rate distribution is uniform.

Further, a flow control flow path through which the second fluid flows,
The difference from the first embodiment is that only the fins are arranged in place of the narrow width portion and the fins as the peeling suppressing member. FIG. 8 shows the plate heat exchanger of the present embodiment,
The top view of the heat-transfer plate in which the flow control flow path in which a 2nd fluid flows is formed is shown. The members corresponding to those in FIG. 7 are indicated by the same symbols. As shown in FIG. 8, partition walls 3 are arranged apart from each other on the surface of the heat transfer plate 2. Three flow control channels 5 are linearly formed by the partition wall 3. The flow control flow path 5 has a flow control means 6. The flow control means 6 comprises fins 62. Three fins 62 are arranged near each of the outflow port 51 and the inflow port 52. The fin 62 corresponds to a peeling suppressing member.

The fluid collides with the fins 62 when flowing in.
By colliding with the fins 62, the flow direction is controlled, and the fluid flows in parallel with the partition wall 3. That is, the fluid is controlled to flow in parallel with the partition wall 3. For this reason,
Separation from the partition wall 3 is suppressed, and the fluid flows along the partition wall 3. Since the fluid flows along the partition wall 3, a stagnation area near the side of the partition wall 3 is less likely to occur.

In this embodiment, the two types of flow control channels are alternately formed in the vertical direction with the heat transfer plate sandwiched therebetween. By homogenizing the flow of the first fluid in the flow control channel, heat can be sufficiently exchanged in the limited surface area of the heat transfer plate. Further, since the separation and deviation of the fluid in the flow control channel are suppressed, the flow rate distribution becomes uniform and the heat transfer efficiency improves.

(7) Seventh Embodiment The difference between this embodiment and the sixth embodiment is that the number of flow rate distribution adjusting members arranged in the flow control flow path through which the first fluid flows is increased. Specifically, the flow distribution adjusting member is arranged also in the branch passage formed in the flow control passage. Since the other configurations are the same as those in the sixth embodiment, only the differences will be described here.

FIG. 9 is a top view of the heat transfer plate in the plate heat exchanger of this embodiment in which the flow control flow path through which the first fluid flows is formed. The members corresponding to those in FIG. 7 are indicated by the same symbols. As shown in FIG. 9, the flow control channel 5
Is formed in a U shape. Further, in the flow control passage 5, the partition wall 3 forms three branch passages. The flow rate distribution adjusting member 6 is provided in the three branch paths.
7 are arranged. Three flow rate distribution adjusting members 67 are arranged in parallel with the partition wall 3, respectively. Each branch path is divided into four equal parts by the flow rate distribution adjusting member 67.

The fluid flows into the flow control passage 5 from the inflow port 51. The fluid flowing in from the inflow port 51 is guided by the flow rate distribution adjusting member 67 and flows into each branch passage formed by the partition wall 3. At this time, since the flow rate distribution adjusting member 67 adjusts the flow rate distribution of the flow even in each branch path,
Flow bias is suppressed. Therefore, not only the flow rate distribution into the branch passages but also the flow deviation in each branch passage is suppressed. Further, by gradually narrowing the flow path width by the flow rate distribution adjusting member 67, the deviation due to the flow direction change is suppressed.

(8) Eighth Embodiment The difference between this embodiment and the sixth embodiment is that three pairs of flow rate distribution adjusting members are arranged in the flow control flow path through which the first fluid flows. In addition, the fin of the peeling suppressing member is not arranged. The rest of the configuration is the same as the sixth embodiment, so only the differences will be described.

FIG. 10 shows a top view of the heat transfer plate in the plate heat exchanger of this embodiment, in which the flow control flow path through which the first fluid flows is formed. The members corresponding to those in FIG. 7 are indicated by the same symbols. As shown in FIG. 10, the flow control channel 5 is formed in a U shape. Further, in the flow control passage 5, the partition wall 3 forms three branch passages. On the other hand, the flow rate distribution adjusting members 67 are arranged in three pairs. All of the three pairs of flow rate distribution adjusting members 67 are arranged in an inverted V shape from the inflow port 51 and the outflow port 52 toward the edges of the heat transfer plate 2 facing each other. Of these, the pair of flow distribution adjustment members 67 arranged on the outermost side
Guides the first fluid to the branch path farthest from the inflow port 51. Further, the pair of innermost flow distribution adjusting members 67 arranged inside guide the first fluid from the inflow port 51 to the nearest branch passage. The remaining pair of flow rate distribution adjusting members 67 guide the first fluid to the central branch passage.

The fluid flows into the flow control passage 5 from the inflow port 51. The fluid flowing in from the inflow port 51 is guided to each branch by the flow rate distribution adjusting member 67. Since the fluid is forcibly distributed to each branch, the deviation of the flow rate flowing into each branch is suppressed.

(9) Others The embodiments of the plate heat exchanger of the present invention have been described above. However, the embodiment of the plate heat exchanger of the present invention is not limited to the above embodiment. The plate heat exchanger of the present invention can be implemented in various forms with various modifications and improvements based on the knowledge of those skilled in the art.

For example, in the above embodiment, all the interlayer flow passages are flow control passages. However, at least one of the interlayer flow passages may be a flow control passage, and the number of flow control passages is not particularly limited. The flow control channel may be one of a plurality of interlayer channels formed in one gap between the heat transfer plate layers. Also, the number may be different for each gap between the heat transfer plate layers. Flow control channel width,
That is, the separation width of the partition wall is not particularly limited.

In the above embodiment, the flow control passage is formed linearly or in a U-shape. However, the shape of the flow control channel is not particularly limited, and may be formed in a curved shape, a zigzag shape, or the like. Further, the shape of the flow control channel may be the same or different for each gap between the heat transfer plate layers. In the first to fifth embodiments described above, the flow control channels in the vertically adjacent gaps are formed so as to intersect with each other with the heat transfer plate in between. However, the flow control flow paths in the vertically adjacent gaps may be formed in the same direction.

In the above embodiment, the heat transfer plate made of SUS is used, but heat transfer plates made of various materials such as aluminum, copper and resin can be used. Further, the size of the heat transfer plate and the number of stacked layers are not particularly limited, and may be appropriately determined in consideration of the application and the like. Also, the partition wall and the flow control means were made of the same material as the heat transfer plate,
The partition wall and the flow control means may be made of various materials, and may be made of different materials.

In the above embodiment, the heat exchanger of the present invention was incorporated into the hydrogen reformer and used, but the use of the heat exchanger of the present invention is not particularly limited. For example, it can be used in a chemical plant such as an oil refining device.

The flow control means in the first embodiment comprises a narrow width portion and fins. Of these, the narrow part is
It has a pointed shape toward the edge of the heat transfer plate. However, the shape of the narrow portion can be various shapes such as an arc shape, a knife shape, a step shape, and a bottleneck shape. Figure 11
Examples of the shape of the narrow width portion are shown in (a) to (d). In FIG. 11, (a) shows an arc shape, (b) shows a knife shape, (c) shows a step shape, and (d) shows a bottleneck shape. Above all,
When the narrow portion has an arc shape, fluid separation can be more effectively suppressed. Further, the narrow width portions are arranged at both ends of the partition wall, respectively, but they may be arranged only at the end portion on the inlet side. On the other hand, three fins are arranged near each of the inlet and the outlet, but the number of fins is not particularly limited. Further, the fin may be arranged only at the inlet. Further, the fins may not be arranged and only the narrow width portion may be arranged. It is more effective to dispose a stagnation suppressing member in addition to the narrow portion and the fin.

The flow control means in the second embodiment is a prism. One prism is arranged near each of the outlet and the inlet, but the number of prisms is not particularly limited. The prism may be arranged only at the inlet. Also, the prisms are arranged so that the distances from the ends of the partition walls arranged on both sides of the prism are almost equal,
The position of the prism is not particularly limited. In FIG.
FIG. 3 is a top view of a heat transfer plate in which two prisms are arranged near each of the inlet and the outlet. As shown in FIG. 12, two prisms 63 are arranged near each of the inflow port 51 and the outflow port 52. In this embodiment, the two prisms 63 and the ends of the partition walls 3 arranged on both sides thereof are trapezoidal. Therefore, the heat transfer plate 2 is supported more firmly. In addition to the prism, a narrow portion may be arranged. It is more effective to dispose a stagnation suppressing member.

Although the prism is equivalent to the peeling suppressing member, the peeling suppressing member is not limited to the prism,
In addition to the fins, various shapes such as a cylinder, an elliptic cylinder, and a blade-shaped plate can be used. FIG. 13 shows a top view of a heat transfer plate in which fins and cylinders are arranged. As shown in FIG. 13, three fins 62 are arranged near each of the inflow port 51 and the outflow port 52. Two cylinders 68 are arranged on the extension line of the partition wall 3 near the inflow port 51 and the outflow port 52, respectively.
In this aspect, the fluid collides with the fins 62 and the cylinder 68 as it flows in. When the fluid collides with the fins 62, the flow direction is changed, and the flow along the partition wall 3 is controlled. When the fluid collides with the cylinder 68, a vortex is generated behind the cylinder 68. The vortex stirs the fluid and brings it closer to the partition wall 3. That is, by disposing the two types of members, the separation of the fluid is further suppressed. In this aspect, since the cylinder is arranged, there is an advantage that the pressure loss when the fluid collides is smaller than that of the prism.

The flow control means in the third embodiment is composed of stacked blocks. Five blocks are stacked and arranged near the outlet and the inlet, respectively. However, the number of blocks and the stacking method are not particularly limited. The block may be arranged only at the inlet. Furthermore, it is more effective to dispose a stagnation suppressing member.

The flow control means in the fourth embodiment comprises fins and pins. A plurality of pins are arranged between the outflow port and the inflow port, but the number thereof is not particularly limited. The pin has a cylindrical shape and corresponds to a stagnation suppressing member, but the stagnation suppressing member is not limited to the pin. For example, various shapes such as an elliptic cylinder and a prism can be used. In addition, it is more effective to arrange the narrow width portion in addition to the fin as the peeling suppressing member.

The flow control means in the fifth embodiment comprises fins and baffles. As a peeling suppression member,
It is more effective to arrange the narrow portion in addition to the fin.
A plurality of baffle plates are arranged between the outflow port and the inflow port, but the number thereof is not particularly limited. The baffle plate corresponds to the stagnation suppressing member, but the stagnation suppressing member is not limited to the baffle plate. For example, a thin plate having a corrugated surface may be arranged on the side of the partition wall.
Further, the partition wall itself may be formed into a corrugated shape and the partition wall may be arranged. In this case, the partition wall also serves as a stagnation suppressing member. FIG. 14 shows a top view of a heat transfer plate in which a corrugated partition wall is arranged. As shown in FIG. 14, the flow control flow path 5 has a corrugated partition wall 3 formed therein.
It is formed by. Since the side portion of the partition wall 3 has an uneven shape, the flow portion is agitated by the uneven portion, and it becomes difficult for the flow to stay in the vicinity of the side portion of the partition wall.

In the sixth embodiment, the flow control means of the flow control passage through which the first fluid flows is composed of fins and a flow rate distribution adjusting member. The flow rate distribution adjusting member has a thin plate shape, but the shape thereof is not particularly limited.
For example, the flow rate distribution adjusting member may be a plate having holes, and the height of the flow rate distribution adjusting member may be the same as or lower than that of the partition wall. Two flow rate distribution adjusting members are arranged between the inflow port and the outflow port, but the number and the arrangement method are not limited. For example, only those that restrict the flow from the inlet to the downstream may be arranged,
On the contrary, only the one that widens the flow from the middle of the flow control channel toward the outlet may be arranged. Although three branch passages are formed in the flow control passage, the number and arrangement of the branch passages are not particularly limited.

Further, in the sixth embodiment, the flow control channel is formed in a U shape, but the shape of the flow control channel in which the flow rate distribution adjusting member is arranged is not particularly limited. For example, the flow rate distribution adjusting member can be arranged also in the flow control flow path in which the inflow port and the outflow port are respectively arranged at the opposite edges of the heat transfer plate. As an example thereof, FIG. 15 shows a top view of a heat transfer plate in which a flow control channel is formed in which an inflow port and an outflow port are respectively arranged at opposing edges of the heat transfer plate. As shown in FIG. 15, by the partition wall 3, the outer circumference of the flow control flow path 5,
An inflow port 51 and an outflow port 52 are formed. The inflow port 51 and the outflow port 52 are arranged at the opposite edges of the heat transfer plate 2. Two partition walls 3 are further arranged in the central portion of the heat transfer plate 2. The two partition walls 3 form three branch passages in the flow control passage 5. The flow control flow path 5 has fins 62 and a flow rate distribution adjusting member 67 as the flow control means 6. Two fins 62 are arranged near each of the outflow port 51 and the inflow port 52. Flow distribution adjusting member 6
Two 7 are arranged between the inflow port 51 and the outflow port 52. The two flow rate distribution adjusting members 67 are arranged parallel to each other from the inflow port 51 and the outflow port 52 toward the edges of the heat transfer plate 2 facing each other. The fluid that has flowed in from the inflow port 51 once branches into each branch passage formed by the partition wall 3, flows in, then merges again and flows out from the outflow port 52. At that time, the fluid is guided to the flow rate distribution adjusting member 67. That is, the flow of the fluid is controlled by the flow rate distribution adjusting member 67, so that the fluid can smoothly flow through the flow control flow path 5.

In the seventh embodiment, the flow control means of the flow control passage through which the first fluid flows is composed of a flow rate distribution adjusting member. Here, three flow distribution adjustment members are arranged in each of the three branch passages, but the number and arrangement of the flow distribution adjustment members are not particularly limited. For example, one may be arranged at each branch.

In the eighth embodiment, the flow control means of the flow control passage through which the first fluid flows comprises a flow rate distribution adjusting member. Here, the flow rate distribution adjusting members are arranged in three pairs in an inverted C shape so as to guide the fluid flowing in from the inflow port to each branch passage. However, the number of flow distribution adjustment members is
It is not particularly limited, and for example, it may be arranged in every other branch path. Further, only the one for guiding the fluid flowing from the inflow port to each branch may be arranged,
Only those that guide the fluid from each branch to the outlet may be arranged.

[0085]

In the plate heat exchanger of the present invention, at least one of the interlayer flow paths formed between the layers of the heat transfer plate is a flow control flow path having flow control means for controlling the flow of fluid. It was done. By controlling the flow of the fluid, it is possible to suppress the separation and uneven distribution of the fluid and the occurrence of the stagnation area. Therefore, the plate heat exchanger of the present invention is
A plate heat exchanger with low pressure loss and high heat transfer efficiency.

[Brief description of drawings]

FIG. 1 shows a perspective view of a flow path structure in a plate heat exchanger according to a first embodiment.

FIG. 2 shows a top view of a heat transfer plate in the plate heat exchanger of the first embodiment.

FIG. 3 shows a top view of a heat transfer plate in the plate heat exchanger of the second embodiment.

FIG. 4 shows a top view of a heat transfer plate in the plate heat exchanger of the third embodiment.

FIG. 5 shows a top view of a heat transfer plate in a plate heat exchanger of a fourth embodiment.

FIG. 6 shows a top view of a heat transfer plate in a plate heat exchanger of a fifth embodiment.

FIG. 7 is a top view of a heat transfer plate in which a flow control channel through which a first fluid flows is formed in the plate heat exchanger of the sixth embodiment.

FIG. 8 is a top view of a heat transfer plate in which a flow control channel through which a second fluid flows is formed in the plate heat exchanger of the sixth embodiment.

FIG. 9 is a top view of a heat transfer plate in which a flow control channel through which a first fluid flows is formed in the plate heat exchanger of the seventh embodiment.

FIG. 10 is a top view of a heat transfer plate in which a flow control channel through which a first fluid flows is formed in the plate heat exchanger of the eighth embodiment.

FIG. 11 shows a shape example of a narrow portion.

FIG. 12 is a top view of a heat transfer plate in which two prisms are arranged near the inlet and two in the vicinity of the outlet.

FIG. 13 is a top view of a heat transfer plate in which fins and cylinders are arranged.

FIG. 14 shows a top view of a heat transfer plate in which corrugated partition walls are arranged.

FIG. 15 shows a top view of a heat transfer plate in which a flow control channel is formed in which an inlet and an outlet are respectively arranged at opposite edges of the heat transfer plate.

FIG. 16 shows a perspective view of a flow path structure in a conventional plate heat exchanger.

[Explanation of symbols]

1: Plate type heat exchanger 2: Heat transfer plate 3: Partition wall 4: Gap 5: Flow control flow path 51: Inflow port 52: Outflow port 6: Flow control means 61: Narrow width part 62: Fin 63: Square column 64 : Block 65: Pin 66: Baffle plate 67: Flow rate distribution adjusting member

─────────────────────────────────────────────────── ─── Continuation of front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) H01M 8/04 H01M 8/04 N

Claims (13)

[Claims] 1. A plurality of heat transfer plates that are laminated and have a gap between layers, and a heat transfer plate that has an inflow port and an outflow port that are interposed in the gap and that open to an edge of the heat transfer plate. A partition wall that forms an interlayer flow path that extends in the surface direction is formed, and fluids having different temperatures alternately flow through the gaps adjacent to each other in the stacking direction with the heat transfer plate interposed therebetween,
A plate heat exchanger in which heat is exchanged via the heat transfer plate, wherein at least one of the interlayer flow paths controls a flow of the fluid flowing from the inflow port and flowing out from the outflow port. A plate heat exchanger having a flow control passage having a flow control means for 2. The plate heat exchanger according to claim 1, wherein the inflow port and the outflow port of the flow control channel are respectively arranged at opposite edges of the heat transfer plate. 3. The plate heat exchanger according to claim 1, wherein the inflow port and the outflow port of the flow control channel are arranged at the same edge of the heat transfer plate. 4. The partition wall is arranged so that the fluid flowing from the inflow port is once branched and then merged again to flow out from the outflow port.
The plate heat exchanger according to item 1. 5. The flow control means according to claim 4, wherein the flow control means has a flow rate distribution adjusting member arranged between the inflow port and the outflow port and adjusting a flow rate distribution of the flow of the branched fluid. Plate heat exchanger. 6. The plate heat exchanger according to claim 5, wherein the flow rate distribution adjusting member is arranged apart from one of the two heat transfer plates sandwiching the flow rate distribution adjusting member. 7. The plate heat exchanger according to claim 1, wherein the flow control means has a separation suppressing member that suppresses separation of the fluid generated at an end portion of the partition wall. 8. The plate heat exchanger according to claim 7, wherein the separation suppressing member is arranged near the inflow port. 9. The plate heat exchanger according to claim 8, wherein the separation suppressing member is a narrow portion arranged at an end portion of the partition wall and having a width narrowing toward an upstream side of the fluid flow. . 10. The flow control means according to claim 1, wherein the flow control means has a stagnation suppressing member which is arranged between the inflow port and the outflow port and changes a flow direction of the fluid to suppress stagnation of the fluid. Plate heat exchanger. 11. The plate heat exchanger according to claim 10, wherein the stagnation suppressing member is a protrusion arranged on the surface of the heat transfer plate. 12. The plate heat exchanger according to claim 10, wherein the stagnation suppressing member is an uneven portion arranged on a side portion of the partition wall. 13. The plate heat exchanger according to claim 1, wherein the plate heat exchanger is used in a hydrogen reformer for supplying hydrogen as fuel for a fuel cell.