JP2012002425A - Plate type heat exchanger, and heat pump device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent the occurrence of stagnation of fluid in a plate type heat exchanger without reducing heat transfer area.SOLUTION: There is provided the plate type heat exchanger in which a plurality of rectangular plates where inflow and outflow ports 9, 10 for a first fluid or a second fluid are formed in the four corners thereof are laminated, and a first flow passage where the first fluid flows and a second flow passage where the second fluid flows are alternately formed between each plate. In the first flow passage, a bypass flow passage 22 is formed for bypassing some of the first fluid flowed in from the inflow port 9 for the first fluid to a heat exchanging flow passage through an area between an outflow port 12 for the second fluid which is provided on one side in the longitudinal direction and the corner of the rectangular plate.

Description

  The present invention relates to a plate heat exchanger formed by laminating a plurality of heat transfer plates.

In a conventional plate heat exchanger, a part of a flow path formed between heat transfer plates is closed in the vicinity of a fluid outflow inlet (see Patent Document 1).
Further, there is a plate heat exchanger in which the position of the fluid inlet / outlet is changed in order to avoid fluid stagnation in the plate heat exchanger and freezing of the fluid in the plate heat exchanger (Patent Document 2). reference).

JP-T 61-500626 JP 11-037677 A

Conventionally, the fluid flowing in the plate heat exchanger is difficult to flow in the region opposite to the outflow inlet and the short axis direction, and stagnation is likely to occur in that region. For example, when a plate heat exchanger is used as an evaporator for exchanging heat between water and a refrigerant, if the stagnation occurs in the flow path on the water side, the water temperature in that region rapidly decreases compared to the surroundings. . As a result, water freezes in the area, and the heat exchanger is damaged.
As a countermeasure, in Patent Document 2, the position of the outflow inlet is changed, and a blocking portion is provided in a region where water near the outflow inlet stagnates to prevent stagnation. However, in the closed portion, water does not flow, the heat transfer area is reduced, and the heat exchange performance is deteriorated.
An object of the present invention is to prevent the occurrence of fluid stagnation in a plate heat exchanger without reducing the heat transfer area.

The plate heat exchanger according to the present invention is
A plurality of rectangular plates with passage holes serving as outflow inlets of the first fluid or the second fluid provided at the four corners are stacked, and the first flow path through which the first fluid flows and the second fluid flow between the plates. It is a plate type heat exchanger in which the flowing second flow paths are alternately formed,
The first flow path is a passage hole provided on the other side in the long axis direction for the first fluid that has flowed in from an inflow port that is a passage hole provided on one side in the long axis direction of each plate. A flow path for flowing out from a certain outlet, and a heat exchange path for exchanging heat between the first fluid and the second fluid flowing in the adjacent second path between the inlet and the outlet. Formed flow path,
The first flow path includes an upstream adjacent hole which is a passage hole provided on the one side in the long axis direction and is different from the inflow port, and the upstream adjacent hole. An upstream bypass flow path that bypasses a part of the first fluid that has flowed in from the inflow port to the heat exchange flow path is formed through a region between the corners of the plate located.

  In the plate heat exchanger according to the present invention, the first fluid flows from the bypass channel into the heat exchange channel on the side opposite to the inflow port in the short axis direction. Therefore, it is possible to prevent the stagnation of the first fluid.

The side view of the plate type heat exchanger 30. FIG. The front view of the side plate 1 for reinforcement. The front view of the heat-transfer plate 2. FIG. The front view of the heat-transfer plate 3. FIG. The front view of the side plate 4 for reinforcement. The figure which shows the state which laminated | stacked the heat-transfer plate 2 and the heat-transfer plate 3. FIG. The disassembled perspective view of the plate-type heat exchanger 30. FIG. Explanatory drawing of the shape of the heat-transfer plate 2. FIG. Explanatory drawing of the shape of the heat-transfer plate 3. FIG. 1 is a front view of a heat transfer plate 2 according to Embodiment 1. FIG. The figure which shows the AA partial cross section of FIG. 10 in the state which laminated | stacked the heat-transfer plate 2 and the heat-transfer plate 3. As shown in FIG. The front view of the heat-transfer plate 2 which concerns on Embodiment 2. FIG. The front view of the heat-transfer plate 3 which concerns on Embodiment 2. FIG. BB sectional drawing of FIG. 12 and FIG. 13 at the time of laminating | stacking the heat-transfer plate 2 shown in FIG. 12, and the heat-transfer plate 3 shown in FIG. The front view of the heat-transfer plate 2 which concerns on Embodiment 3. FIG. Explanatory drawing of the plate-type heat exchanger 30 which concerns on Embodiment 4. FIG. The perspective view of the state which laminated | stacked the heat-transfer plate 2 and the heat-transfer plate 3 which concern on Embodiment 5. FIG. The perspective view which shows the state which removed the heat-transfer plate 2 of the 1st inflow port 9 side part of DD of FIG. The figure which shows the example which comprised the weir 24 with the board which opened the hole. The figure which shows the example which comprised the weir 24 by the rectangular parallelepiped block. The figure which shows the example which comprised the weir 24 by the column or elliptical columnar block. The figure which shows the example which deform | transformed some wave shapes 15 and 16 and comprised the weir 24. FIG. The figure which shows the relationship between the flow-path cross-sectional area ratio of the bypass flow path 22 and the main inflow flow path 23, and a heat passage rate and flow velocity ratio. Schematic which shows the structure of the heat pump type heating hot-water supply system 110 which concerns on Embodiment 7. FIG.

Embodiment 1 FIG.
A basic configuration of the plate heat exchanger 30 according to the first embodiment will be described.
FIG. 1 is a side view of the plate heat exchanger 30. FIG. 2 is a front view of the reinforcing side plate 1 (viewed from the stacking direction). FIG. 3 is a front view of the heat transfer plate 2. FIG. 4 is a front view of the heat transfer plate 3. FIG. 5 is a front view of the reinforcing side plate 4. FIG. 6 is a view showing a state in which the heat transfer plate 2 and the heat transfer plate 3 are stacked. FIG. 7 is an exploded perspective view of the plate heat exchanger 30. FIG. 8 is an explanatory diagram of the shape of the heat transfer plate 2. FIG. 9 is an explanatory diagram of the shape of the heat transfer plate 3.

  As shown in FIG. 1, in the plate heat exchanger 30, the heat transfer plates 2 and the heat transfer plates 3 are alternately stacked. In the plate heat exchanger 30, the reinforcing side plate 1 is stacked on the front surface, and the reinforcing side plate 4 is stacked on the back surface.

As shown in FIG. 2, the reinforcing side plate 1 is formed in a substantially rectangular plate shape. The reinforcing side plate 1 is provided with a first inflow pipe 5, a first outflow pipe 6, a second inflow pipe 7, and a second outflow pipe 8 at four corners of a substantially rectangular shape.
As shown in FIGS. 3 and 4, each heat transfer plate 2, 3 is formed in a substantially rectangular plate shape like the reinforcing side plate 1, and includes a first inlet 9, a first outlet 10, A second inlet 11 and a second outlet 12 are provided. Each of the heat transfer plates 2 and 3 has wave shapes 15 and 16 that are displaced in the laminating direction of the plates, and the wave shapes 15 and 16 that are substantially V-shaped when viewed from the laminating direction are formed. The In particular, in the wave shape 15 formed on the heat transfer plate 2 and the wave shape 16 formed on the heat transfer plate 3, the substantially V-shaped direction is reversed.
As shown in FIG. 5, the reinforcing side plate 4 is formed in a substantially rectangular plate shape, like the reinforcing side plate 1 and the like. The reinforcing side plate 4 is not provided with the first inflow pipe 5, the first outflow pipe 6, the second inflow pipe 7, and the second outflow pipe 8. In FIG. 5, positions of the first inflow pipe 5, the first outflow pipe 6, the second inflow pipe 7, and the second outflow pipe 8 are indicated by broken lines on the reinforcing side plate 4. These are not provided.

  As shown in FIG. 6, when the heat transfer plate 2 and the heat transfer plate 3 are laminated, the substantially V-shaped wave shapes 15 and 16 having different directions are overlapped, so that the heat transfer plate 2 and the heat transfer plate 3 In the meantime, a flow path causing a complicated flow is formed.

  As shown in FIG. 7, the heat transfer plates 2 and 3 are laminated so that the first inlets 9, the first outlets 10, the second inlets 11, and the second outlets 12 overlap each other. The Further, the reinforcing side plate 1 and the heat transfer plate 2 have the first inflow pipe 5 and the first inflow port 9 overlapped, the first outflow pipe 6 and the first outflow port 10 overlapped, and the second inflow pipe 7. And the second inflow port 11 are stacked, and the second outflow pipe 8 and the second outflow port 12 are stacked. Then, the heat transfer plates 2 and 3 and the reinforcing side plates 1 and 4 are laminated so that the outer peripheral edges thereof overlap and are joined by brazing or the like. At this time, each of the heat transfer plates 2 and 3 is not only joined at the outer peripheral edge, but also when viewed from the stacking direction, the wave shape bottom of the upper plate and the wave shape top of the lower plate Overlapping parts are also joined.

Accordingly, the first flow path 13 through which the first fluid (for example, water) flowing in from the first inflow pipe 5 flows out from the first outflow pipe 6 is formed between the back surface of the heat transfer plate 3 and the front surface of the heat transfer plate 2. Formed between. Similarly, the second flow path 14 through which the second fluid (for example, refrigerant) flowing in from the second inflow pipe 7 flows out from the second outflow pipe 8 is formed between the back surface of the heat transfer plate 2 and the front surface of the heat transfer plate 3. Formed between.
The first fluid that has flowed into the first inflow pipe 5 from the outside flows through the passage holes formed by overlapping the first inlets 9 of the heat transfer plates 2 and 3, and flows into the first flow paths 13. The first fluid that has flowed into the first flow path 13 flows in the long axis direction while gradually spreading in the short axis direction, and flows out from the first outlet 10. The first fluid that has flowed out of the first outlet 10 flows through the passage hole formed by the overlapping of the first outlets 10, and flows out from the first outlet pipe 6 to the outside.
Similarly, the second fluid that has flowed into the second inflow pipe 7 from the outside flows through the passage holes formed by overlapping the second inlets 11 of the heat transfer plates 2 and 3, and enters the second flow paths 14. Inflow. The second fluid that has flowed into the second flow path 14 flows in the long axis direction while gradually spreading in the short axis direction, and flows out from the second outlet 12. The second fluid that has flowed out of the second outlet 12 flows through the passage hole formed by the overlapping of the second outlet 12, and flows out from the second outlet pipe 8 to the outside.
The first fluid flowing in the first flow path 13 and the second fluid flowing in the second flow path 14 are heat-exchanged via the heat transfer plates 2 and 3 when flowing through the portions where the wave shapes 15 and 16 are formed. The In the first flow path 13 and the second flow path 14, a portion where the wave shapes 15 and 16 are formed is referred to as a heat exchange flow path 17 (see FIGS. 3, 4 and 6).

As shown in FIG. 8, the hatched portions 18 around the first inlet 9 and the first outlet 10 of the heat transfer plate 2 are approximately the same height as the bottom of the wave shape 15. On the other hand, the hatched portion 19 around the second inlet 11 and the second outlet 12 of the heat transfer plate 2 has the same height as the top of the wave shape 15.
Similarly, as shown in FIG. 9, the hatched portion 20 around the first inlet 9 and the first outlet 10 of the heat transfer plate 3 is approximately the same height as the top of the wave shape 16. On the other hand, the hatched portion 21 around the second inlet 11 and the second outlet 12 of the heat transfer plate 3 has the same height as the bottom of the wave shape 16.
And when the heat-transfer plate 2 and the heat-transfer plate 3 are laminated | stacked by turns, the hatching part 21 of the heat-transfer plate 3 and the heat-transfer plate are the back side of the heat-transfer plate 3 and the front side of the heat-transfer plate 2. The hatched portion 19 of the plate 2 is in close contact. On the other hand, a space is formed between the hatched portion 20 of the heat transfer plate 3 and the hatched portion 18 of the heat transfer plate 2. Therefore, the first fluid flowing through the first inlet 9 flows into the first flow path 13 formed between the back surface side of the heat transfer plate 3 and the front surface side of the heat transfer plate 2, but the second inlet port. The second fluid flowing through 11 does not flow into the first flow path 13. Further, the first fluid flowing through the first flow path 13 does not flow out to the second inlet 11 or the second outlet 12.
Similarly, the hatched portion 18 of the heat transfer plate 2 and the hatched portion 20 of the heat transfer plate 3 are in close contact with the back surface side of the heat transfer plate 2 and the front surface side of the heat transfer plate 3. On the other hand, a space is formed between the hatched portion 19 of the heat transfer plate 2 and the hatched portion 21 of the heat transfer plate 3. Therefore, the second fluid flowing through the second inlet 11 flows into the second flow path 14 formed between the back surface side of the heat transfer plate 2 and the front surface side of the heat transfer plate 3. The first fluid flowing through 9 does not flow into the second flow path 14. Further, the second fluid flowing through the second flow path 14 does not flow out to the first inlet 9 or the first outlet 10.

In the first flow path 13, the nearby hatched portion 19 and the hatched portion 21 are in close contact with each other, and the flow path in that portion is closed. Therefore, the vicinity of the second inlet 11 and the vicinity of the second outlet 12 (broken line portion 25 in FIG. 7) in the heat exchange channel 17 of the first channel 13 are portions where the first fluid is difficult to flow and is easily stagnated.
Similarly, in the 2nd flow path 14, the hatching part 18 and the hatching part 20 contact | adhere, and it will be in the state where the flow path of the part was obstruct | occluded. Therefore, the vicinity of the first inlet 9 and the vicinity of the first outlet 10 (broken line portion 26 in FIG. 7) in the heat exchange channel 17 of the second channel 14 are portions where the second fluid is difficult to flow and is easily stagnant.

Next, features of the plate heat exchanger 30 according to Embodiment 1 will be described. The plate heat exchanger 30 according to the first embodiment includes a bypass channel 22 (upstream side) that passes through the channel between the second outlet 12 (upstream adjacent hole) and the corner of the plate in the first channel 13. It is a feature that a bypass channel is provided.
FIG. 10 is a front view of the heat transfer plate 2 according to the first embodiment. FIG. 11 is a diagram illustrating a partial cross section taken along the line AA of FIG.

As shown in FIGS. 10 and 11, the first flow path 13 is provided with a bypass flow path 22 in a portion that is closed in a normal plate heat exchanger. When viewed from one side of the plate stacking direction, the bypass flow path 22 allows the first fluid flowing in from the first inlet 9 to pass between the second outlet 12 and the short side of the plate, The air flows into the end on the second outlet 12 side in the short axis direction of the heat exchange channel 17 through between the outlet 12 and the long side of the plate.
Therefore, the first fluid that has flowed into the first flow path 13 from the first inlet 9 not only flows into the heat exchange flow path 17 from the main inflow flow path 23, but also bypasses, as in a normal plate heat exchanger. It flows into the heat exchange channel 17 from the channel 22. As described above, if the first fluid just flows into the heat exchange channel 17 from the main inflow channel 23, the first fluid does not easily flow to the vicinity of the second outlet 12 in the heat exchange channel 17 and is stagnant. . However, by providing the bypass flow path 22, it is possible to flow the first fluid to the vicinity of the second outlet 12 in the heat exchange flow path 17 and to prevent stagnation.

  For example, when the first fluid is water, the second fluid is a refrigerant, and the plate heat exchanger 30 functions as an evaporator, if the water stays in the first flow path 13, the staying water is changed by the refrigerant. It is cooled rapidly. As a result, water may freeze and the plate heat exchanger 30 may be damaged due to volume expansion. However, in the plate heat exchanger 30 according to the first embodiment, since water does not stay in the first flow path 13, it is possible to prevent the plate heat exchanger 30 from being damaged.

Further, the portion where the first fluid has been stagnant conventionally has not been effectively heat exchanged. However, in the plate heat exchanger 30 according to the first embodiment, the stagnation of the portion where the first fluid has been stagnation is eliminated, and the effective heat exchange area increases. Furthermore, since heat is also exchanged in the bypass channel 22, an effective heat exchange area increases. Therefore, the heat exchange efficiency is improved. Therefore, the plate heat exchanger 30 may be used not only as an evaporator but also as a condenser.
Further, when the plate heat exchanger 30 is used in an air conditioner, the heat exchange performance of the plate heat exchanger 30 is improved, so that the required number of plates of the plate heat exchanger 30 with respect to the necessary capacity of the air conditioner can be reduced. Can be reduced. Further, as described above, freezing in the plate heat exchanger 30 can be prevented, and damage can be prevented. Therefore, it is possible to provide a highly reliable plate heat exchanger 30 while reducing costs.

  The bypass flow path 22 bends smoothly along the periphery of the circular second outlet 12 to connect the vicinity of the first inlet 9 and the heat exchange path 17. Therefore, the pressure loss due to the first fluid flowing through the bypass channel 22 can be reduced.

In the above description, it has been described that the bypass channel 22 that passes through the region between the second outlet 12 and the corner of the plate is provided on the first inlet 9 side of the first channel 13. However, the present invention is not limited to this, and a bypass channel (downstream bypass) that passes through the region between the second inlet 11 (downstream adjacent hole) and the corner of the plate on the first outlet 10 side of the first channel 13. A flow path) may be provided.
Similarly, a bypass channel that passes between the first outlet 10 and the end of the plate may be provided on the second inlet 11 side of the second channel 14, or the second outlet 12 side. In addition, a bypass channel that passes between the first inlet 9 and the end of the plate may be provided.

Embodiment 2. FIG.
In the second embodiment, a plate heat exchanger 30 in which the cross-sectional area of the bypass channel 22 is constant will be described.
FIG. 12 is a front view of the heat transfer plate 2 according to the second embodiment. FIG. 13 is a front view of the heat transfer plate 3 according to the second embodiment. 14 is a BB cross-sectional view of FIGS. 12 and 13 when the heat transfer plate 2 shown in FIG. 12 and the heat transfer plate 3 shown in FIG. 3 are stacked.

As shown in FIGS. 12 and 13, when the heat transfer plate 2 and the heat transfer plate 3 are stacked, a bypass flow path 22 is formed at a position just overlapping in the stacking direction. As shown in FIG. 14, the heat transfer plate 2 has a bypass passage 22 portion convex, and the heat transfer plate 3 has a bypass flow passage 22 portion concave. And the bypass flow path 22 is formed because the convex part of the heat-transfer plate 2 and the concave part of the heat-transfer plate 3 overlap. The cross-sectional area in the direction perpendicular to the direction in which the first fluid flows in the hollow portion of the convex portion in the heat transfer plate 2 is constant, and is perpendicular to the direction in which the first fluid flows in the hollow portion in the concave portion of the heat transfer plate 3. The cross-sectional area in the direction is also constant. Therefore, the flow path cross-sectional area of the bypass flow path 22 (the cross-sectional area perpendicular to the direction in which the first fluid flows) is constant.
Since the channel cross-sectional area of the bypass channel 22 is constant, dust clogging and stagnation in the bypass channel 22 are difficult to occur. Moreover, since the convex part and concave part which form the bypass flow path 22 can be joined with the convex part and concave part of an adjacent plate similarly to a wave-shaped top and bottom, a plate-type heat exchanger The strength of 30 is increased.

  In the above description, it has been described that the convex portion formed on the heat transfer plate 2 and the concave portion formed on the heat transfer plate 3 overlap in the stacking direction to form the bypass flow path 22. However, one of the heat transfer plate 2 and the heat transfer plate 3 may be flattened to reduce the flow passage cross-sectional area of the bypass flow passage 22.

Embodiment 3 FIG.
In the third embodiment, a plate heat exchanger 30 in which the bypass channel 22 is connected to one wave of the wave shape 15 or the wave shape 16 by a smooth curve will be described.
FIG. 15 is a front view of the heat transfer plate 2 according to the third embodiment.

As shown in FIG. 15, the bypass flow path 22 formed in the heat transfer plate 2 bends smoothly in a direction parallel to the ridgeline of the wave shape 15 and is connected to the end of one wave of the wave shape 15. .
Therefore, the pressure loss when the first fluid flowing through the bypass channel 22 flows into the channel formed by the wave shape 15 can be reduced. In addition, since the flow from the bypass channel 22 to the channel formed by the wave shape 15 becomes smooth and the velocity distribution in the short axis direction in the first channel 13 becomes uniform, the entire first channel 13 is Pressure loss is reduced. Since the velocity distribution in the minor axis direction in the first flow path 13 is uniform, it is difficult to cause dust clogging and stagnation in the first flow path 13 and the heat exchange efficiency is improved.

Embodiment 4 FIG.
In the fourth embodiment, a plate type heat exchanger 30 in which the inlet side (first inlet 9 side) and outlet side (heat exchange channel 17 side) of the bypass channel 22 are branched into a plurality will be described.
FIG. 16 is an explanatory diagram of the plate heat exchanger 30 according to the fourth embodiment.

As shown in FIG. 16, the bypass channel 22 is formed with a plurality of channels on the inlet side, merges into one channel in the middle, and branches again to the plurality of channels on the outlet side.
For this reason, the cross-sectional area of the flow path near the inlet or the outlet of the bypass flow path 22 is increased, and the pressure loss can be reduced. In addition, even if a part of the branched flow path is blocked with dust or sludge, other flow paths can be used, so that the heat exchange performance can be prevented from being deteriorated or damaged due to the block of the bypass flow path 22.
In addition, the first fluid can flow out to a wide range in the minor axis direction by branching the outlet-side flow path. Therefore, the flow velocity distribution can be made uniform by adjusting the direction of the outlet-side flow path branched according to the distribution of the portion where stagnation is likely to occur and the number of branches. Note that the branched outlet-side flow paths may be smoothly bent in the direction parallel to the ridgeline of the wave shape 15 and connected to the wave ends. Note that the spread angle (angle C in FIG. 16) of the flow path accompanying the branch on the outlet side is 180 degrees at the maximum.

Embodiment 5 FIG.
In the fifth embodiment, a plate heat exchanger 30 provided with a weir 24 on the side of the main inlet channel 23 (see FIG. 10) of the first inlet 9 will be described.
FIG. 17 is a perspective view of a state in which the heat transfer plate 2 and the heat transfer plate 3 according to Embodiment 5 are stacked. FIG. 18 is a perspective view showing a state in which the heat transfer plate 2 on the first inlet 9 side half of DD of FIG. 17 is removed.

As shown in FIGS. 17 and 18, the first fluid flows along the edge of the first inlet 9 in the first channel 13 so as to cover the main inlet channel 23 side of the first inlet 9. A plate-like weir 24 is provided. The weir 24 is formed in a semicircular shape at the maximum so as to cover at most half of the circumference of the first inflow port 9.
By providing the bypass flow path 22, the flow path cross-sectional area through which the first fluid flowing in from the first inflow port 9 flows out increases, so that the flow velocity of the first fluid flowing through the heat exchange flow path 17 becomes slow. As a result, the heat transfer coefficient decreases. Therefore, by providing the weir 24, the first fluid flowing in from the first inlet 9 is prevented from flowing to the main inflow channel 23 side, and the flow velocity of the first fluid flowing through the main inflow channel 23 is increased. As a result, the flow rate of the first fluid flowing through the heat exchange channel 17 is increased, and the heat transfer rate can be improved.
When the area covered by the weir 24 is enlarged, the flow velocity is increased. When the area covered by the weir 24 is reduced, the flow velocity is reduced. Therefore, for example, if a weir 24 that closes the same area as the flow path cross-sectional area of the bypass flow path 22 is provided, the flow velocity becomes the same as that without the bypass flow path 22, and the effective heat transfer area is maintained while maintaining the heat transfer coefficient. Can be increased.

The weir 24 is not limited to the shape shown in FIGS. 17 and 18 and may have other shapes. 19 to 22 are diagrams showing other shapes of the weir 24. 19 to 22 show a state in which the heat transfer plate 2 on the first inlet 9 side half is removed.
For example, as shown in FIG. 19, the weir 24 may be formed by opening a hole in the weir 24 shown in FIGS. 17 and 18 and adjusting the area covered by the weir 24.
In addition, as shown in FIG. 20, a plurality of rectangular parallelepiped blocks may be arranged as weirs 24 on the main inflow channel 23 side of the first inlet 9.
In addition, as shown in FIG. 21, a plurality of cylindrical or elliptical blocks may be arranged as weirs 24 on the main inflow channel 23 side of the first inlet 9.
In addition, as shown in FIG. 22, the weir 24 may be configured such that a part of the wave shapes 15 and 16 is deformed to close the main inflow channel 23 side of the first inflow port 9.

  In the above description, the weir 24 is provided on the first inlet 9 side, that is, on the upstream side. However, the weir 24 may be provided on the first outlet 10 side, that is, on the downstream side.

  If the weir 24 is created by burring by a press, the manufacturing cost can be reduced.

Embodiment 6 FIG.
In the sixth embodiment, the ratio of the channel cross-sectional area between the bypass channel 22 and the main inflow channel 23 will be described.
FIG. 23 is a diagram illustrating the relationship between the flow path cross-sectional area ratio between the bypass flow path 22 and the main inflow flow path 23, and the heat passage rate and flow rate ratio. In FIG. 23, the horizontal axis is the value of “cross-sectional area of the main inflow channel 23 / cross-sectional area of the bypass channel 22”, and the vertical axis is the heat passage rate and the flow rate ratio. The heat passage rate and the flow rate ratio are based on the case where the bypass flow path 22 is not provided (1.00).

As described above, by providing the bypass flow path 22, the flow rate of the first fluid flowing through the first flow path 13 is slowed, and the heat passage rate is reduced. However, if the decrease in the heat transfer rate is within 5%, the increase in the effective heat transfer area can sufficiently compensate for the decrease in the heat exchange amount due to the decrease in the heat transfer rate.
Here, as shown in FIG. 23, when the flow passage cross-sectional area of the main inflow flow passage 23 is 8 times or more than the flow passage cross-sectional area of the bypass flow passage 22, the decrease in the heat passage rate is within 5%. Therefore, it is preferable that the cross-sectional area of the main inflow channel 23 is eight times or more than the cross-sectional area of the bypass channel 22.

Embodiment 7 FIG.
In the seventh embodiment, a heat pump heating and hot water supply system 110 that is an example of utilization of the plate heat exchanger 30 described in the above embodiment will be described.

FIG. 24 is a schematic diagram showing a configuration of a heat pump heating / hot water supply system 110 according to the seventh embodiment.
The heat pump heating / hot water supply system 110 includes a main refrigerant circuit 116 that sequentially connects a compressor 111, a first heat exchanger 112, a first expansion valve 113, and a second heat exchanger 114, a first heat exchanger 112, and a heating hot water supply. A water circuit 117 that sequentially connects the water use devices 115.
Here, the first heat exchanger 112 is the plate heat exchanger 30 described in the above embodiment. Further, the compressor 111, the first heat exchanger 112, the first expansion valve 113, the second heat exchanger 114, and the main refrigerant circuit 116 that sequentially connects them are housed in a unit, which is connected to the heat pump device 118. Call.

In the first heat exchanger 112, the refrigerant compressed by the compressor 111 and the fluid (here, water) flowing through the water circuit 117 are heat-exchanged. Here, the heat is exchanged in the first heat exchanger 112, whereby the refrigerant is cooled and the water is warmed. The first expansion valve 113 expands the refrigerant heat-exchanged by the first heat exchanger 112. The second heat exchanger 114 performs heat exchange between the expanded refrigerant and air in accordance with the control of the first expansion valve 113. Here, the heat is exchanged in the second heat exchanger 114, whereby the refrigerant is warmed and the air is cooled. Then, the warmed refrigerant is sucked into the compressor 111.
On the other hand, in the water circuit 117, as described above, the water is warmed by heat exchange in the first heat exchanger 112, and the warmed water flows to the water heater for hot water supply 115 and is used for hot water supply and heating. Is done.

As described in the above embodiment, the plate heat exchanger 30 has good heat exchange efficiency and high reliability. Therefore, when the plate-type heat exchanger 30 is mounted on the heat pump type heating and hot water supply system 110 described in the present embodiment, a heat pump type heating and hot water supply system that can efficiently reduce power consumption and reduce CO ₂ emission can be realized. .
Here, the heat pump type heating hot water supply system that exchanges heat between the refrigerant and water in the plate heat exchanger 30 described in the above embodiment has been described. However, the present invention is not limited to this, and the plate heat exchanger 30 described in the above embodiment can be used in many industrial and household equipment such as power generation and food sterilization equipment.

  1, 4 Reinforcement side plate, 2, 3 Heat transfer plate, 5 First inflow pipe, 6 First outflow pipe, 7 Second inflow pipe, 8 Second outflow pipe, 9 First inflow port, 10 First outflow port , 11 2nd inlet, 12 2nd outlet, 13 1st flow path, 14 2nd flow path, 15, 16 Wave shape, 17 Heat exchange flow path, 18, 19, 20, 21 Hatching part, 22 Bypass flow Road, 23 main inflow channel, 24 weir, 25, 26 broken line part, 30 plate heat exchanger.

Claims (10)

A plurality of rectangular plates with passage holes serving as outflow inlets of the first fluid or the second fluid provided at the four corners are stacked, and the first flow path through which the first fluid flows and the second fluid flow between the plates. It is a plate type heat exchanger in which the flowing second flow paths are alternately formed,
The first flow path is a passage hole provided on the other side in the long axis direction for the first fluid that has flowed in from an inflow port that is a passage hole provided on one side in the long axis direction of each plate. A flow path for flowing out from a certain outlet, and a heat exchange path for exchanging heat between the first fluid and the second fluid flowing in the adjacent second path between the inlet and the outlet. Formed flow path,
The first flow path includes an upstream adjacent hole which is a passage hole provided on the one side in the long axis direction and is different from the inflow port, and the upstream adjacent hole. A plate type characterized in that an upstream bypass flow path is formed for bypassing a part of the first fluid flowing in from the inflow port to the heat exchange flow path through a region between the corners of the plate located. Heat exchanger. The plate-type heat exchanger according to claim 1, wherein the upstream bypass flow path is formed along a peripheral edge of the upstream adjacent hole. The first flow path has a downstream adjacent hole which is a passage hole provided on the other side in the major axis direction and is different from the outflow port, and the downstream adjacent hole. The downstream bypass flow path for bypassing a part of the first fluid flowing through the heat exchange flow path to the outlet is formed through a region between the corners of the plate located. Or the plate type heat exchanger of 3. The plate heat exchanger according to claim 3, wherein at least one of the upstream bypass flow path and the downstream bypass flow path has a constant flow path cross-sectional area. Each of the plates is formed with a wave shape that is displaced in the stacking direction in a portion that forms the heat exchange flow path.
At least one of the upstream bypass flow path and the downstream bypass flow path is one of the two plates forming the first flow path when viewed from one side in the plate stacking direction. The plate-type heat exchanger according to any one of claims 1 to 4, wherein the plate-type heat exchanger is smoothly bent in a direction parallel to the wavy ridgeline formed on the surface and connected to the heat exchange flow path. 6. The upstream bypass flow path is characterized in that the inlet side branches into a plurality of flow paths, and the heat exchange flow path side branches into a plurality of flow paths. Plate heat exchanger. 7. The downstream bypass flow path according to claim 1, wherein the heat exchange flow path side branches into a plurality of flow paths and the outlet side branches into a plurality of flow paths. Plate heat exchanger. The first flow path prevents the first fluid flowing out from the inlet from flowing into the heat exchange path and flows into the heat exchange path on the heat exchange path side of the inlet. The plate heat exchanger according to any one of claims 1 to 7, further comprising a weir for adjusting a flow rate of the first fluid. The upstream bypass channel has a channel cross-sectional area at a predetermined position that is 1/8 or less of the cross-sectional area in the minor axis direction of the main inflow channel connecting the inlet and the heat exchange channel. The plate heat exchanger according to any one of claims 1 to 8, wherein Comprising a refrigerant circuit in which a compressor, a first heat exchanger, an expansion mechanism, and a second heat exchanger are connected by piping;
The first heat exchanger connected to the refrigerant circuit is
A plurality of rectangular plates with passage holes serving as outflow inlets of the first fluid or the second fluid provided at the four corners are stacked, and the first flow path through which the first fluid flows and the second fluid flow between the plates. It is a plate type heat exchanger in which the flowing second flow paths are alternately formed,
The first flow path is a passage hole provided on the other side in the long axis direction for the first fluid that has flowed in from an inflow port that is a passage hole provided on one side in the long axis direction of each plate. A flow path for flowing out from a certain outlet, and a heat exchange path for exchanging heat between the first fluid and the second fluid flowing in the adjacent second path between the inlet and the outlet. Formed flow path,
The first flow path includes an upstream adjacent hole which is a passage hole provided on the one side in the long axis direction and is different from the inflow port, and the upstream adjacent hole. A heat pump device characterized in that an upstream bypass passage is formed for bypassing a part of the first fluid flowing in from the inlet to the heat exchange passage through a region between the corners of the plate located. .

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