JP2018165614A - Heat pump device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat pump device capable of improving heat transmission between a refrigerant and a heat medium.SOLUTION: A heat pump device includes a heat exchanger which exchanges heat between a refrigerant flowing through a refrigerant circuit and a heat medium flowing through a heat medium circuit. The heat exchanger is a plate type heat exchanger in which a plurality of heat transfer plates are stacked, a first flow passage through which a first fluid as the refrigerant flows and a second flow passage through which a second fluid as the heat medium flows are formed alternately in a stacking direction between the heat transfer plates, and the heat transfer plate has a recessed and projecting heat transfer portion having a projection projecting to one side in the stacking direction and a recession recessed in a surface thereof, so that heat exchange is performed between the first fluid and the second fluid. An inner fin is disposed in the first flow passage, and the inner fin is a plate fin having a plate-like flat portion having a plurality of passage holes. The plate-like flat portion is fastened in a state of being brought into contact with the recession of the heat transfer plate on one side of the plate fin and the projection of the heat transfer plate on the other side of the plate fin.SELECTED DRAWING: Figure 6

Description

  The present invention relates to a heat pump device using a plate heat exchanger configured by stacking a plurality of heat transfer plates.

  Conventionally, a plate heat exchanger is configured by laminating a plurality of heat transfer plates, and the first flow path and the second flow path are alternately formed between the heat transfer plates. Each of the fluids is allowed to flow and heat exchange is performed between these fluids.

  As this type of plate-type heat exchanger, the first flow path is formed in a space sandwiched between heat transfer plates having a corrugated uneven shape, and the cross-sectional shape is similar to the heat transfer plate in the first flow path. There is a plate heat exchanger having a configuration in which inner fins having corrugated irregularities are arranged (see, for example, Patent Document 1). In this plate heat exchanger, the heat transfer plate and the inner fin are joined with the uneven shape of the heat transfer plate and the uneven shape of the inner fin shifted from each other without overlapping in the stacking direction of the heat transfer plate. ing.

JP-A-2006-70558

  In the plate heat exchanger of Patent Document 1, both the heat transfer plate and the inner plate are uneven. For this reason, when these are overlapped as described above, the plates are point-contacted in a lattice shape and joined at the point contact portions. Although there are a plurality of point contact portions, there is a problem that heat transfer between the inner fin and the heat transfer plate is not sufficient because of the point contact.

  The present invention has been made to solve the above problems, and provides a heat pump device using a plate heat exchanger capable of improving heat transfer between an inner fin and a heat transfer plate. The purpose is to do.

  A heat pump device according to the present invention is a heat pump device having a heat exchanger that exchanges heat between the refrigerant flowing in the refrigerant circuit and the heat medium flowing in the heat medium circuit, and the heat exchanger includes a plurality of heat transfer plates stacked. The first flow path through which the first fluid as the refrigerant flows and the second flow path through which the second fluid as the heat medium flow are alternately formed in the stacking direction between the heat transfer plates. Plate-type heat that includes a heat transfer part having a concavo-convex shape in which a convex part that is convex on one side and a concave part that is concave is formed in a plane, and performs heat exchange between the first fluid and the second fluid It is an exchanger, an inner fin is arranged in the first flow path, and the inner fin is a plate fin having a flat plate-like flat portion in which a plurality of passage holes are formed, and the flat plate-like flat portion is one of the plate fins. A recess in the heat transfer plate on the side It is sandwiched in contact with the convex part of the heat transfer plate on the other side of the plate fin, and the passage hole is formed between the space between the plate fin and one of the heat transfer plates, the plate fin and the heat transfer plate. It communicates with the space between the other.

  Since the heat pump device according to the present invention includes the plate heat exchanger, the heat exchange performance can be improved.

1 is an exploded perspective view of a plate heat exchanger 100 according to Embodiment 1 of the present invention. It is a schematic front view of the 1st heat exchanger plate 1 of FIG. It is a schematic front view of the 2nd heat exchanger plate 3 of FIG. It is a schematic front view of the inner fin 2 of FIG. It is a fragmentary sectional view of the lamination direction of the heat-transfer set 4 of FIG. It is a structure perspective view of the 1st channel 5 of plate type heat exchanger 100 concerning Embodiment 1 of the present invention. FIG. 2 is a front perspective view of a structure in which plate fins 2 are arranged and stacked between a first heat transfer plate 1 and a second heat transfer plate 3 of a plate heat exchanger 100 according to Embodiment 1 of the present invention. It is a front view which shows the example of a shape of the passage hole 20a of the plate type heat exchanger 100 which concerns on Embodiment 1 of this invention. In the plate heat exchanger 100 according to Embodiment 2 of the present invention, the periphery of the first inflow communication path 14 having a structure in which the plate fins 2 are disposed and stacked between the first heat transfer plate 1 and the second heat transfer plate 3 It is the see-through | perspective local view which saw through from the front. It is a general | schematic expanded cross-section perspective view of a part of heat transfer set 4 of the plate type heat exchanger 100 which concerns on Embodiment 3 of this invention. It is a side view of passage hole 20a of plate fin 2 of plate type heat exchanger 100 concerning Embodiment 3 of the present invention. It is a front view of passage hole 20a of plate fin 2 of plate type heat exchanger 100 concerning Embodiment 3 of the present invention. It is a perspective view of passage hole 20a of plate fin 2 of plate type heat exchanger 100 concerning Embodiment 3 of the present invention. It is a general | schematic expanded cross-section perspective view of a part of heat transfer set 4 of the plate type heat exchanger 100 which concerns on Embodiment 3 of this invention. It is a side view of passage hole 20a of plate fin 2 of plate type heat exchanger 100 concerning Embodiment 4 of the present invention. It is a front view of passage hole 20a of plate fin 2 of plate type heat exchanger 100 concerning Embodiment 4 of the present invention. It is a perspective view of passage hole 20a of plate fin 2 of plate type heat exchanger 100 concerning Embodiment 4 of the present invention. It is the perspective view which looked at the passage hole 20a of the plate fin 2 of the plate type heat exchanger 100 which concerns on Embodiment 4 of this invention from the 2nd flow space 5b side. It is a figure which shows the modification of the passage hole 20a of the rectification | straightening wall 26 of the plate type heat exchanger 100 which concerns on Embodiment 4 of this invention. It is a general | schematic expanded cross-section perspective view of a part of heat transfer set 4 of the plate type heat exchanger 100 which concerns on Embodiment 5 of this invention. It is a schematic sectional drawing in the plate type heat exchanger 100 which concerns on Embodiment 6 of this invention. It is explanatory drawing of the plate fin area ratio (gamma) in the plate type heat exchanger 100 which concerns on Embodiment 7 of this invention. It is a performance examination effect figure in plate type heat exchanger 100 concerning Embodiment 7 of the present invention. It is the schematic which shows the structure of the heat pump type heating hot-water supply system 200 which concerns on Embodiment 8 of this invention.

  Hereinafter, a plate heat exchanger according to an embodiment of the invention will be described with reference to the drawings. Here, in FIG. 1 and the following drawings, the same reference numerals denote the same or corresponding parts, and are common to the whole text of the embodiments described below. And the form of the component represented by the whole specification is an illustration to the last, Comprising: It does not limit to the form described in the specification. Moreover, in the following drawings, the relationship of the size of each component may be different from the actual one.

  Further, in the following description, terms indicating directions (for example, “up”, “down”, “right”, “left”, “front”, “back”, etc.) are used as appropriate for easy understanding. This is for explanation and these terms do not limit the present invention. Further, in the first embodiment, “up”, “down”, “right” in the state where the plate heat exchanger 100 is viewed from the front, that is, when the plate heat exchanger 100 is viewed in the stacking direction of the heat transfer plates. , “Left”, “Front”, “Rear” are used. In addition, “concave” and “convex” are defined as “convex” on the front side and “convex” on the rear side.

Embodiment 1 FIG.
FIG. 1 is an exploded perspective view of a plate heat exchanger 100 according to Embodiment 1 of the present invention. FIG. 2 is a schematic front view of the first heat transfer plate 1 of FIG. FIG. 3 is a schematic front view of the second heat transfer plate 3 of FIG. FIG. 4 is a schematic front view of the inner fin 2 of FIG.

  The plate heat exchanger 100 according to the first embodiment is a plate fin type, and the inner fins 2 are arranged between the first heat transfer plate 1 and the second heat transfer plate 3 as shown in FIG. A plurality of heat transfer sets 4 having the above-described configuration are stacked. And the 1st flow path formed between the 1st heat-transfer plate 1 which comprises the heat-transfer set 4, and the 2nd heat-transfer plate 3 which comprises the heat-transfer set 4 because two or more heat-transfer sets 4 are laminated | stacked. 5 and the second flow path 6 formed between the heat transfer sets 4 are alternately stacked, and the first fluid flowing in the first flow path 5 and the second fluid flowing in the second flow path 6 Heat exchange between them. The first fluid is, for example, refrigerant R410A, R32, R290, CO2, and the like, and the second fluid is, for example, water. In FIG. 1, the solid line arrow indicates the flow of the first fluid, and the dotted line arrow indicates the flow of the second fluid.

  A first reinforcing side plate 7 and a second reinforcing side plate 8 are disposed on the outermost surface of the heat transfer set 4 in the stacking direction. In FIG. 1, the plate laminated on the foremost surface is the first reinforcing side plate 7, and the plate laminated on the rearmost surface is the second reinforcing side plate 8.

  Further, the first reinforcing side plate 7 and the second reinforcing side plate 8 are formed in a rounded rectangular plate shape as shown in FIG. Circular holes serving as fluid inlets or outlets are formed at the four corners of the first reinforcing side plate 7. A cylindrical inflow pipe or outflow pipe is provided at the periphery of each hole. Specifically, a first inflow pipe 10 through which the first fluid flows is provided at the lower right of the first reinforcing side plate 7, and a first outflow pipe through which the first fluid flows out at the upper right of the first reinforcing side plate 7. 11 is provided. A second inflow pipe 12 into which the second fluid flows in is provided at the lower left of the second reinforcing side plate 8, and a second outflow pipe 13 through which the second fluid flows out is provided at the upper left.

  The first heat transfer plate 1 and the second heat transfer plate 3 are both substantially rectangular plates with rounded corners, as shown in FIGS. 2 and 3. And the 1st heat-transfer plate 1 and the 2nd heat-transfer plate 3 have the heat-transfer parts 100a and 100b which have the cross section where the uneven | corrugated uneven | corrugated shape (refer FIG. 5 mentioned later) was repeated. The material of the first heat transfer plate 1 and the second heat transfer plate 3 is preferably a metal having good heat conduction, such as aluminum, copper, or an alloy thereof. In order to improve the strength, the material of the first heat transfer plate 1 and the second heat transfer plate 3 is preferably stainless steel.

  And in the four corners of each of the first heat transfer plate 1 and the second heat transfer plate 3, the first inflow pipe 10, the first outflow pipe 11, the second inflow pipe 12, and the second outflow pipe 13, One inflow hole 14a, 14b, first outflow hole 15a, 15b, second inflow hole 16a, 16b, and second outflow hole 17a, 17b are formed. The first inlet holes 14a and 14b are inlets of the first channel 5, the first outlet holes 15a and 15b are outlets of the first channel 5, the second inlets 16a and 16b are inlets of the second channel 6, The two outflow holes 17 a and 17 b serve as outflow ports of the second flow path 6.

  In the following, when it is not necessary to distinguish the first heat transfer plate 1 and the second heat transfer plate 3, they are collectively referred to as “heat transfer plates”. Further, when it is not necessary to distinguish the first reinforcing side plate 7 and the second reinforcing side plate 8, they are collectively referred to as “side plates”.

  Further, as shown in FIG. 4, the inner fin 2 is also a plate having a substantially rectangular shape with rounded corners like the heat transfer plate, and an outer wall peripheral edge 21 protruding in the thickness direction is provided on the outer periphery. The inner fin 2 also has a first inflow hole 14c, a first outflow hole 15c, a first inflow position at positions corresponding to the first inflow pipe 10, the first outflow pipe 11, the second inflow pipe 12, and the second outflow pipe 13, respectively. Two inflow holes 16c and a second outflow hole 17c are formed.

  Since the entire inner fin 2 is substantially flat, the inner fin 2 is hereinafter referred to as a plate fin 2. In the plate fin 2, a portion facing the heat transfer portions 100 a and 100 b of the heat transfer plate is a flat plate-like flat portion 20, and a plurality of passage holes 20 a are formed in the flat portion 20. As shown in FIGS. 1 and 4, the passage hole 20 a is not provided in a portion facing the rib 3 c of the heat transfer plate, around the second inflow hole 16 c, and around the second outflow hole 17 c. . The passage hole 20a may be a hole having a smaller size than the corrugated period of the heat transfer plate, or a slit having a small width.

  The plate fin 2 is preferably thinner than the heat transfer plate. This is for avoiding the enlargement of the whole plate type heat exchanger by arranging the plate fins 2.

  Further, in order to improve the heat exchange efficiency of the plate heat exchanger 100 and improve the performance, the material of the plate fins 2 is a metal having good heat conduction, such as aluminum, copper, or an alloy thereof. It is desirable.

  In addition to improving the performance of the plate heat exchanger 100, the plate fin 2 is made of the same material as the first heat transfer plate 1 and the second heat transfer plate 3 in order to improve the strength. Is desirable. If the plate fins 2 are made of the same material as that of the first heat transfer plate 1 and the second heat transfer plate 3, it is desirable that joining is easy and deformation due to a difference in thermal expansion coefficient hardly occurs.

  And the 1st inflow through which the 1st fluid passes because each 1st inflow hole 14a-14c of the 1st heat transfer plate 1, plate fin 2, and 2nd heat transfer plate 3 comprised as mentioned above overlaps. A communication path 14 (see FIG. 7 described later) is formed. Further, the first outflow holes 15 a to 15 c of the first heat transfer plate 1, the plate fin 2, and the second heat transfer plate 3 overlap each other, so that the first outflow communication passage 15 (described later) passes through the first fluid. 7) is formed. Similarly, the second inflow communication passage 16 (described later) through which the second fluid passes by overlapping the second inflow holes 16a to 16c of the first heat transfer plate 1, the plate fin 2, and the second heat transfer plate 3 respectively. 7) is formed. Further, the second outflow holes 17a to 17c of the first heat transfer plate 1, the plate fin 2, and the second heat transfer plate 3 overlap each other, whereby a second outflow communication passage 17 (described later) through which the second fluid passes. 7) is formed.

  The first inflow communication path 14 and the first outflow communication path 15 communicate with the first flow path 5 and do not communicate with the second flow path 6. For this reason, the first fluid that has flowed into the first inflow pipe 10 from the outside flows into the first flow path 5 through the first inflow communication passage 14. The first fluid that has flowed into the first flow path 5 passes through the first flow path 5 and then flows out from the first outflow pipe 11 via the first outflow communication path 15. The flow of the first fluid in the first flow path 5 will be described again.

  Further, the second inflow communication passage 16 and the second outflow communication passage 17 are configured to communicate with the second flow path 6 and not to communicate with the first flow path 5. For this reason, the second fluid that has flowed into the second inflow pipe 12 from the outside flows through the second inflow communication passage 16 and flows into the second flow path 6. The second fluid that has flowed into the second flow path 6 passes through the second flow path 6 and then flows out from the second outflow pipe 13 via the second outflow communication path 17.

  FIG. 5 is a partial cross-sectional view of the heat transfer set 4 in FIG. 1 in the stacking direction. FIG. 6 is a structural perspective view of the first flow path 5 of the plate heat exchanger 100 according to Embodiment 1 of the present invention. In FIG. 6, the solid line arrows indicate the flow of the first fluid. FIG. 7 is a front perspective view of a structure in which the plate fins 2 are arranged and stacked between the first heat transfer plate 1 and the second heat transfer plate 3 of the plate heat exchanger 100 according to Embodiment 1 of the present invention. It is.

  In each of the first heat transfer plate 1 and the second heat transfer plate 3, the corrugation is regularly formed with a convex and a concave. Then, the corrugated ridge line in the first heat transfer plate 1 is inclined from the upper left to the lower right as shown in FIG. 2, and the corrugated ridge line in the second heat transfer plate 3 is shown in FIG. As shown, it is inclined from the upper right to the lower left. Therefore, as shown in FIG. 6, in the state where the first heat transfer plate 1 and the second heat transfer plate 3 are overlapped, the ridge line directions of the respective waveforms intersect and the corrugations have an angle. Yes. For this reason, when these plates are seen through in the stacking direction, the ridge line on the first heat transfer plate 1 side and the ridge line on the second heat transfer plate 3 side intersect in a lattice pattern.

  As shown in FIGS. 5 and 6, the first flow path 5 includes a first flow space 5 a on the first heat transfer plate 1 side and a second flow space on the second heat transfer plate 3 side with the plate fin 2 as a boundary. It is divided into 5b. The first flow space 5a has a configuration in which a plurality of small spaces extending in the corrugated ridge line direction of the first heat transfer plate 1 are formed in a direction intersecting the ridge line direction. Similarly, the second flow space 5a has a configuration in which a plurality of small spaces extending in the ridge line direction of the second heat transfer plate 3 are formed in a direction intersecting the ridge line direction. The first flow space 5a and the second flow space 5b communicate with each other through passage holes 20a provided in the plate fins 2.

  Of the two adjacent heat transfer sets 4, the second flow path 6 is between the second heat transfer plate 3 of one heat transfer set 4 and the first heat transfer plate 1 of the other heat transfer set 4. It is composed of space. The corrugated ridge line direction of the second heat transfer plate 3 and the corrugated ridge line direction of the first heat transfer plate 1 intersect as described above. For this reason, the contact portion between the second heat transfer plate 3 and the first heat transfer plate 1, that is, the concave ridge line 3 aa in which the corrugated recesses 3 a of the second heat transfer plate 3 are continuous, A contact portion with the convex ridge line 1ba where the convex portions 1b are continuous is local, and a second flow path 6 through which the second fluid freely flows is formed between the second heat transfer plate 3 and the first heat transfer plate 1. Has been.

Next, the flow of fluid and the action of the plate fins 2 in the plate heat exchanger 100 configured as described above will be described.
The first fluid that has flowed into the first inflow pipe 10 from the outside flows into the first flow path 5 through the first inflow communication passage 14. The first fluid that has flowed into the first flow path 5 flows upward in the first flow path 5 while gradually spreading toward the left and right outer wall peripheries 21 of the plate fins 2, and passes through the first outflow communication path 15. It flows out from the first outflow pipe 11.

  Here, since the plate fins 2 are provided in the first flow path 5, the first fluid flows alternately through the passage holes 20a into the first flow space 5a and the second flow space 5b. At this time, the heat of the first fluid comes into contact with the respective surfaces of the first heat transfer plate 1 and the second heat transfer plate 3 by the turbulent heat transfer promotion and the leading edge effect heat transfer promotion by the passage hole 20a. In addition, it effectively exchanges heat with the surface of the plate fin 2. That is, by arranging the plate fins 2 in the first flow path 5, the heat transfer area of the first fluid increases. The heat transferred to the surface of the plate fin 2 is transferred to the inside of the plate fin 2 by heat conduction, and is transferred to the respective ridge lines of the first heat transfer plate 1 and the second heat transfer plate 3 by heat transfer.

  In this way, in addition to the path through which the heat of the first fluid directly transfers from the first fluid to the first heat transfer plate 1 and the second heat transfer plate 3, the first heat transfer plate 1 via the plate fins 2. And the path | route which transmits to the 2nd heat-transfer plate 3 is formed. For this reason, the heat of the first fluid is efficiently transmitted to the first heat transfer plate 1 and the second heat transfer plate 3, and the heat transfer property of the first flow path 5 can be enhanced.

  The second fluid flows through the second flow path 6, and the heat of the second fluid is transmitted to the second heat transfer plate 3 and the first heat transfer plate 1 of the adjacent heat transfer set 4, As a result, heat exchange between the first fluid and the second fluid is performed.

  Here, the heat conductivity of the first flow path 5 is higher than that of the second flow path 6 by providing the plate fins 2 in the first flow path 5. For this reason, it is good to flow the 1st fluid with lower heat conductivity than the 2nd fluid to the 1st flow path 5. Thereby, the low heat conductivity of the first fluid can be covered, and as a result, the performance of the plate heat exchanger 100 can be improved. Regarding the heat transfer level, the heat transfer is higher in a fluid having only a gas phase or a two-phase fluid including a liquid phase and a gas phase than in a fluid having only a liquid phase.

Next, the features of the plate heat exchanger 100 according to Embodiment 1 will be described with reference to FIGS.
The plate fins 2 are joined in a state of being sandwiched between the first heat transfer plate 1 and the second heat transfer plate 3 that are arranged before and after in the stacking direction. More specifically, the plate fin 2 includes a flat ridge 20 having a passage hole 20 a, a concave ridge line 1 aa in which a corrugated concave portion 1 a of the first heat transfer plate 1 continues, and a corrugated convex portion of the second heat transfer plate 3. It is linearly contacted and line-connected to the convex ridgeline 3ba that 3b continues.

  Thus, since the part joined with the heat-transfer part 100a of the 1st heat-transfer plate 1 and the heat-transfer part 100b of the 2nd heat-transfer plate 3 in the plate fin 2 was made into the flat flat part 20, the flat part 20 And the corrugated heat transfer parts 100a, 100b are not points but lines. For this reason, compared with the conventional structure in which the plate fins 2 are corrugated, the contact area between the heat transfer plate and the plate fins 2 can be increased, and the heat exchange efficiency can be increased, compared to a structure in which the joint portion is a point joint. be able to.

  Moreover, the passage hole 20a of the plate fin 2 is formed in a lattice formed by intersecting the ridge line on the first heat transfer plate 1 side and the ridge line on the second heat transfer plate 3 side as shown in FIG. Has been. That is, the passage hole 20a is formed at a position avoiding the joint portion between the heat transfer plate and the plate fin 2. If the passage hole 20a is formed at a portion where the heat transfer plate and the plate fin 2 are joined, the contact area between the plate fin 2 and the heat transfer plate is reduced by the area of the passage hole 20a. , Heat exchange efficiency decreases. On the other hand, since the passage hole 20a is provided so as to avoid the joint portion between the heat transfer plate and the plate fin 2, inconvenience that the heat exchange efficiency is lowered can be avoided.

  As described above, according to the first embodiment, the plate fin 2 has a planar shape, and the heat transfer plate and the plate fin 2 are line-joined at the ridge line portion of the heat transfer plate. For this reason, compared with the conventional structure in which the plate fins 2 are corrugated, the contact area between the heat transfer plate and the plate fins 2 can be increased, and the heat exchange efficiency can be increased, compared to a structure in which the joint portion is a point joint. be able to.

  Also, turbulent heat transfer enhancement is achieved by placing plate fins 2 with passage holes 20a formed between heat transfer plates in a flow path through which two-phase (liquid phase and gas phase) or low heat transfer fluid flows. And leading edge effect heat transfer enhancement can be utilized. Further, the two flow path structures of the plate heat exchanger 100 can be individually designed. Further, the heat transfer area on the fluid side having low heat transfer property can be expanded. From the above, overall performance of the plate heat exchanger 100 can be improved.

  Further, since the heat transfer plate and the plate fins 2 are wire-bonded, the strength of the plate heat exchanger 100 can be improved.

  Further, since the distance from the line contact portion to the line contact portion on the surface of the plate fin 2 is shorter than the point contact structure, and the distance for conducting heat in the plate fin 2 is short, the performance of the plate heat exchanger 100 is improved. Can be improved.

  If the plate fin 2 is provided with a passage hole 20a at a portion to be joined to the ridge line of the heat transfer plate, the plate fin 2 and the ridge line portion of the heat transfer plate are not joined at the passage hole portion. , The bonding area is reduced. However, in this Embodiment 1, since it was set as the structure which arrange | positions the channel | path hole 20a in a grid | lattice-like grid | lattice avoiding the part joined with the ridgeline of the heat-transfer plate in the plate fin 2, the plate type by the channel | path hole 20a There is no inconvenience such as performance of the heat exchanger 100.

  If the plate fins 2 are corrugated, the thickness in the stacking direction of the heat transfer set 4 in which the first heat transfer plate 1, the plate fins 2, and the second heat transfer plate 3 are inevitably increased. However, since the plate fin 2 of the first embodiment has a planar shape and is thinner than the heat transfer plate, the thickness does not increase significantly even when these three plates are stacked. Therefore, when the plate type heat exchanger without the plate fins 2 is provided in the housing of the heat pump device, the plate type heat exchanger is replaced with the first embodiment without changing the size of the housing. The plate fin 2 can be replaced with the plate heat exchanger 100 of the first embodiment. In this case, it is possible to improve the performance of the heat pump device with a simple operation that simply replaces the plate heat exchanger.

  The plate fin 2 is formed with a plurality of passage holes 20a, and the first fluid flows alternately through the passage holes 20a to the first flow space 5a and the second flow space 5b, thereby promoting turbulent heat transfer. And leading edge effect heat transfer enhancement can be utilized.

  Moreover, since the dimension and arrangement of the diameter of the passage hole 20a of the plate fin 2 can be freely designed, distribution of the plate heat exchanger 100 can be improved.

  In addition, since the heat exchanging portion of the plate heat exchanger 100 is composed of only the heat transfer plate, the side plate, and the plate fin 2, the structure can be simplified, and the heat exchanger can be reduced in size and cost. .

  In addition, the above performance improvement can reduce the size and cost of a plate heat exchanger having the same performance.

  The plate heat exchanger according to the first embodiment is not limited to the above-described structure, and can be implemented with various modifications as follows, for example, without departing from the gist of the present invention.

  In the above description, the plate fins 2 are arranged on the first flow path 5 side through which the first fluid having lower heat conductivity flows. However, the plate fins 2 are arranged on the second flow path 6 side through which the second fluid having higher heat conductivity flows. You may arrange. However, the flow resistance of the second fluid may increase depending on the size of the passage hole 20a. In this case, it is better not to arrange the plate fins 2 in the second flow path 6. Whether the plate fin 2 is disposed in the first flow path 5 or the second flow path 6 may be determined in consideration of the effects of heat transfer and resistance of the first fluid and the second fluid.

  In the above description, the plate fins 2 are provided only in the first flow path 5, but the plate fins 2 may be provided in both the first flow path 5 and the second flow path 6. In this case, the plate fins 2 may have the same structure or different configurations. Moreover, when providing the plate fin 2 in both the 1st flow path 5 and the 2nd flow path 6, in order to make a heat conductivity different in the 1st flow path 5 and the 2nd flow path 6, a structure differs mutually. The plate fins 2 may be arranged. In order to change the configuration of the plate fins 2, for example, the size, shape, density, position, etc. of the passage hole 20a may be changed. As described above, when the plate fins 2 are disposed in each of the first flow path 5 and the second flow path 6, the structure of the two flow paths is individually determined depending on the size, shape, density, position, and the like of the passage hole 20 a. Can be designed.

  In the above description, the shape of the passage hole 20a is circular in front view, but the shape of the passage hole 20a is not limited to a circle. The shape of the passage hole 20a can be appropriately changed according to the type of fluid, the direction of the first flow space 5a and the second flow space 5b of the first flow path 5, and for example, as shown in the following FIG. Also good.

FIG. 8 is a front view showing a shape example of the passage hole 20a of the plate heat exchanger 100 according to Embodiment 1 of the present invention.
As shown in FIG. 8, the shape of the passage hole 20a may be a semicircle, an ellipse, an arc, a triangle, a quadrangle, a polygon having five or more corners, and the like. Moreover, the shape of the passage hole 20a provided in the plate fin 2 may be unified into one shape, or different shapes may be provided in combination. The standard design of the passage hole 20a is to reduce the processing cost of the plate fin 2 while having heat transfer performance, to reduce the flow resistance of the flow path, to increase the heat transfer area, and the like.

  Further, although the plate fin 2 is planar, local unevenness may be present at the edge portion of the passage hole 20a.

Embodiment 2. FIG.
In the first embodiment, the size of each passage hole 20a is the same. However, in the second embodiment, the in-plane distribution of the fluid in the first flow path 5 is taken into consideration, and each passage hole 20a has a different size. The configuration is changed in size. Hereinafter, the second embodiment will be described mainly with respect to differences from the first embodiment, and configurations not described in the second embodiment are the same as those in the first embodiment.

  FIG. 9 shows the first inflow of the structure in which the plate fins 2 are arranged and laminated between the first heat transfer plate 1 and the second heat transfer plate 3 in the plate heat exchanger 100 according to the second embodiment of the present invention. It is the see-through | perspective local view which permeate | transmitted the communicating path 14 periphery from the front. Although FIG. 9 shows a front perspective local view around the first inflow communication passage 14, the configuration around the first outflow communication passage 15 is substantially the same. Further, in FIG. 9, a plurality of arrows 22 directed upward from the first inflow communication passage 14 and a plurality of arrows 23 directed from the first inflow communication passage 14 to the left outer wall peripheral edge 19 are respectively flow flows in the first flow path 5. Shows mainstream.

Hereinafter, the flow of the first fluid in the first flow path 5 will be described with reference to FIG.
In the first flow path 5, since the first fluid flows in from the first inflow communication path 14, the flow velocity near the first inflow communication path 14 is faster than the flow velocity in the portion far from the first inflow communication path 14. . For this reason, if no measures are taken, the first fluid is biased to a region that linearly moves from the first inflow communication passage 14 to the first outflow communication passage 15, and the first fluid flows to the left and right outer wall peripheral edges 21 of the plate fin 2. The in-plane distribution of the first fluid in the first flow path 5 is not uniform.

  Therefore, in the plate heat exchanger 100 according to the second embodiment, as shown in FIG. 9, each passage hole 20 a formed in the plate fin 2 is moved away from the first inflow communication passage 14. The hole diameter is large. In other words, each hole diameter of each passage hole 20a is formed to increase from the first inflow communication passage 14 toward the outer wall peripheral edge 21. Therefore, the flow path resistance of the passage hole 20a increases from small to large as it goes from the first inflow communication passage 14 toward the outer wall peripheral edge 21. For this reason, the first fluid that has flowed into the first flow path 5 from the first inflow communication passage 14 flows upward toward the left and right outer wall peripheral edges 21 in addition to flowing upward, and the in-plane distribution of the first fluid is uniform. Can be achieved. In this way, each passage hole 20a formed so that the hole diameter increases as the position away from the first inflow communication passage 14 forms a uniform portion of the present invention.

  In addition, the area | region which changes the hole diameter of the passage hole 20a should just be the circumference | surroundings of the 1st inflow communication path 14, and does not need to be the 1st flow path 5 whole. What is necessary is just to let the periphery of the 1st inflow communication path 14 be the area | region below the set position and the height position away in the direction of the 1st outflow communication path 15 from the 1st inflow communication path 14, for example.

  As described above, according to the second embodiment, the same effects as those of the first embodiment can be obtained, and each passage hole 20a around the first inflow communication passage 14 can be connected to the first inflow communication passage 14. The hole diameter was increased as the position of was increased. Thereby, the resistance of the first flow path 5 is adjusted, and the in-plane distribution of the first fluid can be improved.

Embodiment 3 FIG.
In the third embodiment, the heat transfer area of the plate fin 2 is expanded to improve the heat exchange efficiency. In the following, the third embodiment will be described mainly with respect to the points different from the first embodiment, and the configuration not described in the third embodiment is the same as that of the first embodiment.

  FIG. 10 is a schematic enlarged cross-sectional perspective view of a part of the heat transfer set 4 of the plate heat exchanger 100 according to Embodiment 3 of the present invention. FIG. 10 is a cross-sectional perspective view cut in the ridge line direction at the concave portion of the second heat transfer plate 3. In addition, in order to show the flow characteristics of the in-plane flow path, a part of the first flow space 5a between two concave ridge lines adjacent to the plate fin 2 and the first heat transfer plate 1 is also shown in the drawing. The arrows in FIG. 10 indicate the flow direction of the first fluid. FIG. 11 is a side view of passage hole 20a of plate fin 2 of plate heat exchanger 100 according to Embodiment 3 of the present invention. FIG. 12 is a front view of passage hole 20a of plate fin 2 of plate heat exchanger 100 according to Embodiment 3 of the present invention. FIG. 13 is a perspective view of passage hole 20a of plate fin 2 of plate heat exchanger 100 according to Embodiment 3 of the present invention.

  The plate heat exchanger 100 according to the third embodiment has a configuration in which a cylindrical heat transfer wall 24 protruding toward the second flow space 5b is provided on the periphery of the passage hole 20a of the first embodiment. The heat transfer wall 24 is like a fin collar having a height that does not contact the second heat transfer plate 3. The height H of each heat transfer wall 24 is configured uniformly.

  In the first flow path 5 in which the heat transfer wall 24 is formed in this way, the main flow 25 of the first fluid that has flowed into the second flow space 5b from the first inflow communication path 14 flows through the second flow space 5b as it is, The tributary flow 25a of the first fluid flows into the first flow space 5a through each passage hole 20a. Here, since the heat transfer wall 24 is provided at the periphery of the passage hole 20a, the heat transfer area of the first fluid is increased compared to the configuration without the heat transfer wall 24, and the heat of the first fluid is efficiently transferred to the plate. It is transmitted to the fin 2. Then, the first fluid that has flowed into the first flow space 5a then flows into the second flow space 5b, and alternately flows through the first flow space 5a and the second flow space 5b.

  As described above, according to the third embodiment, the same effect as in the first embodiment can be obtained, and the heat transfer wall 24 is provided on the periphery of the passage hole 20a, and thus the following effect can be further obtained. That is, the heat transfer area is increased by providing the heat transfer wall 24. For this reason, the heat transfer efficiency from the first fluid to the plate fins 2 is increased, and as a result, the heat transfer performance of the plate heat exchanger 100 can be improved.

  Moreover, since the height of each heat-transfer wall 24 was made the same, the effect that the processing cost of a fin can be reduced, increasing a heat-transfer area is acquired.

  The heat transfer wall 24 is erected with respect to the plate fin 2 in a state where the periphery of the passage hole 20a is bent. The heat transfer wall 24 can be integrally formed with the plate material serving as a base together with the passage hole 20a by burring. For this reason, the heat transfer wall 24 can be manufactured at low cost.

  In addition, here, a configuration in which the heat transfer wall 24 is provided on the entire periphery of the passage hole 20a is shown, but a configuration in which the heat transfer wall 24 is provided on a part of the periphery of the passage hole 20a may be employed. Also in this case, since the heat transfer area can be increased, the same effect can be obtained.

Embodiment 4 FIG.
In the third embodiment, the heat transfer wall 24 is provided on the periphery of the passage hole 20a for the purpose of increasing the heat transfer area. In the fourth embodiment, a rectifying wall mainly for the purpose of rectifying the first fluid is provided on a part of the periphery of the passage hole 20a. In the following, the fourth embodiment will be described mainly with respect to differences from the third embodiment, and the configuration not described in the fourth embodiment is the same as that of the third embodiment.

  FIG. 14 is a schematic enlarged cross-sectional perspective view of a part of the heat transfer set 4 of the plate heat exchanger 100 according to Embodiment 3 of the present invention. FIG. 14 is a cross-sectional perspective view cut in the ridge line direction at the concave portion of the second heat transfer plate 3. The arrows in FIG. 14 indicate the flow direction of the first fluid. FIG. 15 is a side view of passage hole 20a of plate fin 2 of plate heat exchanger 100 according to Embodiment 4 of the present invention. FIG. 16 is a front view of passage hole 20a of plate fin 2 of plate heat exchanger 100 according to Embodiment 4 of the present invention. FIG. 17 is a perspective view of passage hole 20a of plate fin 2 of plate heat exchanger 100 according to Embodiment 4 of the present invention. FIG. 18 is a perspective view of the passage holes 20a of the plate fins 2 of the plate heat exchanger 100 according to Embodiment 4 of the present invention as viewed from the second flow space 5b side.

  The plate heat exchanger 100 according to the fourth embodiment has a configuration in which a rectifying wall 26 protruding toward the second flow space 5b is provided on the periphery of the passage hole 20a. The rectifying wall 26 is provided on the peripheral edge on the downstream side of the main flow 25 of the first fluid in the first flow path 5 among the peripheral edges of the passage hole 20a. The rectifying wall 26 is a square plate and is provided perpendicular to the plate fin 2. Further, each rectifying wall 26 is configured such that the height H from the plate fin 2 increases as the position from the first inflow communication passage 14 moves away, in other words, toward the outer wall peripheral edge 21. ing.

  In the case of such a configuration, the description will be made by paying attention to one rectifying wall 26. At a place where the height of the rectifying wall 26 is low, the first fluid that has flowed into the second flow space 5b passes through the second flow space 5b as it is. It tends to flow toward the outer wall peripheral edge 21. Therefore, since the first fluid easily flows into the second flow space 5b, the flow rate toward the first flow space 5a through the passage hole 20a formed with the short rectifying wall 26 is reduced. On the contrary, in the location where the height of the rectifying wall 26 is high, the first fluid that has flowed into the second flow space 5b hardly flows through the second flow space 5b. Therefore, since the second flow space 5b hardly flows, the flow rate toward the first flow space 5a through the passage hole 20a in which the rectifying wall 26 having a high height is formed increases.

  The rectifying wall 26 exhibits the above-described action by changing the height H from the plate fin 2. For this reason, the height H of the rectifying wall 26 from the plate fin 2 is increased as the position away from the first inflow communication passage 14 increases, so that the first inflow into the first flow path 5 from the first inflow communication passage 14 is achieved. In addition to flowing upward, one fluid can flow toward the left and right outer wall peripheries 21 to make the in-plane distribution of the first fluid uniform. The uniformizing portion of the present invention is constituted by the rectifying wall 26 configured as described above.

  The rectifying wall 26 does not need to be provided in all the passage holes 20a, and may be provided in the passage holes 20a around the first inflow communication passage 14. What is necessary is just to let the periphery of the 1st inflow communication path 14 be the area | region below the set position and the height position away in the direction of the 1st outflow communication path 15 from the 1st inflow communication path 14, for example.

  According to the fourth embodiment configured as described above, by providing the rectifying wall 26, the effect of improving the heat transfer performance by increasing the heat transfer area as in the third embodiment is obtained, and the following effects are further obtained. Is obtained. That is, by configuring each rectifying wall 26 so that the height H increases as the position from the first inflow communication passage 14 increases, the resistance of the first flow path 5 is adjusted, and the surface of the first fluid Uniformity of the internal distribution can be achieved.

  Moreover, since the standing angle θ of each rectifying wall 26 is the same, there is an effect that the processing cost of the rectifying wall 26 can be reduced while improving the in-plane distribution by adjusting the height H of the rectifying wall 26. can get.

  In addition, the plate type heat exchanger of this Embodiment 4 is not limited to the structure mentioned above, For example, various deformation | transformation implementation is possible as follows in the range which does not deviate from the summary of this invention.

FIG. 19 is a diagram showing a modification of the passage hole 20a of the rectifying wall 26 of the plate heat exchanger 100 according to Embodiment 4 of the present invention. In FIG. 19, the arrows indicate the flow direction of the first fluid.
Although the rectifying wall 26 is a square plate, the rectifying wall 26 is not limited to a square plate, and may be a triangular plate as shown in FIG. The triangular plate is a so-called delta wing and can generate a vortex at the tip to promote heat transfer. In particular, when the plate heat exchanger 100 is used as an evaporator, the vicinity of the outlet of the evaporator is almost gas. Therefore, by arranging the rectifying wall 26 of the delta blade at the outlet of the evaporator, a vortex is generated at the tip. High heat transfer promoting effect can be obtained.

Embodiment 5. FIG.
In the fourth embodiment, all the rectifying walls 26 are perpendicular to the plate fins 2, but in the fifth embodiment, the inclination of the rectifying walls 26 with respect to the plate fins 2 is different. In the following, the fifth embodiment will be described mainly with respect to the differences from the fourth embodiment, and the configuration not described in the fifth embodiment is the same as that of the fourth embodiment.

FIG. 20 is a schematic enlarged cross-sectional perspective view of a part of the heat transfer set 4 of the plate heat exchanger 100 according to Embodiment 5 of the present invention. FIG. 20 is a cross-sectional perspective view cut in the ridge line direction at the concave portion of the second heat transfer plate 3. The arrows in FIG. 20 indicate the flow direction of the first fluid.
In the plate heat exchanger 100 according to the fifth embodiment, as in the fourth embodiment, the peripheral edge on the downstream side of the flow 25 in the main flow direction of the first fluid in the first flow path 5 among the peripheral edges of the passage hole 20a. In addition, a rectifying wall 27 protruding toward the second flow space 5b is provided. Each rectifying wall 27 is formed of a square plate, and the height H from the plate fin 2 is uniform. Further, as each rectifying wall 27 moves away from the first inflow communication passage 14, in other words, as it moves toward the outer wall peripheral edge 21, the standing angle θ of the rectifying wall 27 with respect to the plate fin 2 increases. As shown in FIG.

  The operation of the rectifying wall 27 configured in this way is the same as that of the rectifying wall 26 of the fourth embodiment, and the fluid flowability of each passage hole 20a is set in a direction away from the side close to the first inflow communication passage 14. It will grow as you go.

  According to the fifth embodiment, the same effect as in the fourth embodiment can be obtained.

  Although the shape of the rectifying wall 27 is described as a quadrangle here, it is not limited to a quadrangle and may be a delta wing or the like, as in the modification described in the fourth embodiment. In the case of a delta blade, as described above, a vortex can be generated at the tip to promote heat transfer.

Embodiment 6 FIG.
In the said Embodiment 1-5, the uneven | corrugated shape provided in each of the 1st heat-transfer plate 1 and the 2nd heat-transfer plate 3 was made into the waveform where the vertex part of a waveform is a mountain shape of a curve. On the other hand, in the sixth embodiment, the concavo-convex shape is a waveform in which the peak portion of the waveform is a trapezoidal shape. In the following, the sixth embodiment will be described mainly with respect to the differences from the first embodiment, and the configuration not described in the sixth embodiment is the same as that of the first embodiment.

  FIG. 21 is a schematic cross-sectional view of a plate heat exchanger 100 according to Embodiment 6 of the present invention. In FIG. 21, the solid line arrow indicates the flow of the first fluid, and the dotted line arrow indicates the flow of the second fluid. As shown in FIG. 21, the apexes of the respective waveforms of the first heat transfer plate 1 and the second heat transfer plate 3 have a trapezoidal shape. By comprising in this way, the junction part of the concave ridgeline 1aa of the 1st heat transfer plate 1 and the plate fin 2, the junction part of the plate fin 2 and the convex ridgeline 3ba of the 2nd heat transfer plate 3, and 2nd heat transfer Each joining surface of the joining part of the concave ridgeline 3aa of the plate 3 and the convex ridgeline 1ba of the first heat transfer plate 1 is enlarged as compared with the case where the apex portion of the waveform is a mountain shape of a curve.

  Therefore, according to the sixth embodiment, in addition to the same effects as those of the first embodiment, the following effects can be further obtained. That is, since the heat transfer area between the plates increases as compared with the case where the apex portion of the waveform is a mountain shape of the curve, the heat exchange efficiency can be increased. Further, the strength of the plate heat exchanger 100 can be improved as compared with the case where the apex of the waveform is a mountain shape of a curve.

Embodiment 7 FIG.
The seventh embodiment relates to the range of “an index related to the area of the passage hole 20a”, which can improve the heat exchange performance. The following description will focus on the differences of the seventh embodiment from the first embodiment, and the configuration not described in the seventh embodiment is the same as that of the first embodiment.

  The “index for the area of the passage hole 20a” is “to the area of the lattice formed by the intersection of the concave ridge line 1aa on the first heat transfer plate 1 side and the convex ridge line 3ba on the second heat transfer plate 3 side”. The ratio of the area of the passage hole 20a (hereinafter referred to as plate fin area ratio γ). Specifically, it is defined as follows with reference to FIG.

FIG. 22 is an explanatory diagram of the plate fin area ratio γ in the plate heat exchanger 100 according to Embodiment 7 of the present invention.
The plate fin area ratio γ is defined as follows.
γ = (A _mesh -A _hole ) / A _mesh
here,
A _mesh : Grid area for plate fins
A _hole : In the plate fin, the area of the passage hole in the lattice

FIG. 23 is a performance study effect diagram in the plate heat exchanger 100 according to Embodiment 7 of the present invention. In FIG. 23, the horizontal axis represents the plate fin area ratio γ [−], and the vertical axis represents the performance ratio [−]. The performance ratio is the ratio of the AK value in the “configuration with plate fins” to the AK value in the “configuration without plate fins”.
Here, the AK value is a value obtained by multiplying the heat transfer rate K and the heat transfer area A in the heat exchanger, and represents the heat transfer characteristics of the heat exchanger.
As shown in FIG. 23, by setting the plate fin area ratio to 0.1 or more and 0.8 or less, the performance can be improved as compared with the configuration in which the plate fin 2 is not provided.
The reason why the upper limit is set to 0.8 is that when 0.8 is exceeded, the pressure loss significantly increases.

  According to the seventh embodiment configured as described above, the fin efficiency is increased as a whole, and there is a coexistence effect of expansion of the heat transfer area, suppression of increase in pressure loss and suppression of increase in material cost.

  Here, the plate fin area ratio “1” corresponds to a configuration in which the plate fin 2 does not have the passage hole 20a. As shown in FIG. 23, the performance ratio when the plate fin area ratio is “1” is over 1.0. That is, even if the plate fin 2 does not have the passage hole 20a, the performance can be improved over the configuration without the plate fin if the plate fin 2 is provided. Thus, even if the plate fin 2 has no passage hole 20a, the performance is improved because the concave ridge line 1aa of the first heat transfer plate 1 and the convex ridge line 3ba of the second heat transfer plate 3 are respectively plate heat exchangers. This corresponds to the case of being parallel to 100 side surfaces. In addition, the case where the first fluid flows into the inflow hole of the first flow path 5 and can flow out of the outflow hole of the first flow path 5 is applicable.

  In addition, here, the configuration in which the position of the passage hole 20a is the central portion of the lattice-like lattice has been illustrated and described, but substantially the same effect can be obtained even if it is slightly deviated from the central portion.

  In addition, although each said Embodiment 1-7 demonstrated as each another embodiment, you may comprise a plate-type heat exchanger combining the characteristic structure of each embodiment suitably. For example, the second embodiment and the third embodiment are combined to provide a configuration in which the diameter of each passage hole 20a is changed, and a configuration in which a heat transfer wall 24 is provided on each peripheral edge of each passage hole 20a. It is good also as a plate type heat exchanger. In addition, the second embodiment and the sixth embodiment are combined, and the configuration in which the diameter of each passage hole 20a is changed, and the uneven shape provided on each of the first heat transfer plate 1 and the second heat transfer plate 3 are provided. It is good also as a plate-type heat exchanger provided with the structure made into a trapezoid shape.

Moreover, although the plate type heat exchanger 100 has been described as a single wall type in each of the first to seventh embodiments, it may be a double wall type. The single wall type is a plate type heat exchanger in which the first heat transfer plate 1 and the second heat transfer plate 3 are alternately stacked one by one. In addition, the double wall type has a configuration in which the first heat transfer plate 1 and the second heat transfer plate 3 are alternately laminated, and the two heat transfer plates communicate with the atmosphere. It is a plate heat exchanger that can prevent refrigerant leakage.

Embodiment 8 FIG.
In the eighth embodiment, a heat pump device to which the plate heat exchanger 100 described in the first to seventh embodiments is applied will be described. Here, a heat pump heating and hot water supply system will be described as an example of a usage form of the heat pump device 50.

FIG. 24 is a schematic diagram showing a configuration of a heat pump heating / hot water system 200 according to Embodiment 8 of the present invention.
The heat pump heating and hot water supply system 200 includes a heat pump device 50 housed in a housing. The heat pump device 50 includes a refrigerant circuit 30 and a heat medium circuit 40. The refrigerant circuit 30 is configured by sequentially connecting a compressor 31, a heat exchanger 32, a decompression device 33 including an expansion valve or a capillary tube, and a heat exchanger 34. The heat medium circuit 40 is configured by sequentially connecting a heat exchanger 32, a heating and hot water supply apparatus 41, and a pump 42 for circulating the heat medium.

  Here, the heat exchanger 32 is the plate heat exchanger 100 described in the above embodiment, and performs heat exchange between the refrigerant circulating in the refrigerant circuit 30 and the heat medium flowing in the heat medium circuit 40. The heat medium used in the heat medium circuit 40 may be any fluid that can exchange heat with the refrigerant in the refrigerant circuit 30 such as water, ethylene glycol, propylene glycol, or a mixture thereof.

  Further, in the plate heat exchanger 100, the plate heat exchanger 100 is configured so that the refrigerant flows in the first flow path 5 having higher heat transfer than the second flow path 6 and the heat medium flows in the second flow path 6. Built into the refrigerant circuit.

  The heating and hot water supply apparatus 41 includes a hot water storage tank (not shown), an indoor unit (not shown) that air-conditions the room, and the like. When the heat medium is water, the water is heated by exchanging heat between the refrigerant in the refrigerant circuit 30 and the plate heat exchanger 100, and the heated water is stored in a hot water storage tank (not shown). The indoor unit (not shown) heats the room by guiding the heat medium of the heat medium circuit 40 to a heat exchanger inside the indoor unit and exchanging heat with room air. In addition, the structure of the heating hot-water supply apparatus 41 is not specifically limited to said structure, What is necessary is just the structure which can be heated and hot-water supply using the heat of the heat medium of the heat-medium circuit 40. FIG.

  As described in the above embodiment, the plate heat exchanger 100 has high heat exchange efficiency and high reliability due to improved strength. Therefore, when the plate heat exchanger 100 is mounted on the heat pump type heating and hot water supply system 200 described in the eighth embodiment, the heat pump type heating and hot water supply system 200 is efficient, can reduce power consumption, and can reduce CO2 emissions. Can be realized.

  In the eighth embodiment, as an application example of the plate heat exchanger 100 described in the above embodiment, a heat pump heating / hot water supply system 200 that exchanges heat between refrigerant and water has been described. However, the plate heat exchanger 100 described in the above embodiment is not limited to the heat pump heating and hot water supply system 200, but is used in many industrial equipment and households such as cooling chillers, power generation devices, and food sterilization treatment equipment. Available for equipment.

  As an application example of the present invention, the plate heat exchanger 100 described in the above embodiment can be used in a heat pump apparatus that is easy to manufacture, has improved heat exchange performance, and needs to improve energy saving performance. .

  DESCRIPTION OF SYMBOLS 1 1st heat transfer plate, 1a recessed part, 1aa recessed ridge line, 1b convex part, 1ba convex ridge line, 2 plate fin (inner fin), 2nd heat transfer plate, 3a recessed part, 3aa concave ridge line, 3b convex part, 3ba convex Ridge line, 3c rib, 4 heat transfer set, 5 first flow path, 5a space, 5b space, 6 second flow path, 7 first reinforcing side plate, 8 second reinforcing side plate, 10 first inflow pipe, 11 first 1 outflow pipe, 12 second inflow pipe, 13 second outflow pipe, 14 first inflow communication path, 14a first inflow hole, 14b first inflow hole, 14c first inflow hole, 15 first outflow communication path, 15a first 1 outflow hole, 15b first outflow hole, 15c first outflow hole, 16 second inflow communication path, 16a second inflow hole, 16b second inflow hole, 16c second inflow hole, 17 second outflow communication path, 17a first Second spill 17b 2nd outflow hole, 17c 2nd outflow hole, 19 outer wall peripheral edge, 20 flat part, 20a passage hole, 21 outer wall peripheral edge, 22 arrow, 23 arrow, 24 heat transfer wall, 25 main flow, 26 rectification wall, 27 rectification wall , 30 Refrigerant circuit, 31 Compressor, 32 Heat exchanger, 33 Pressure reducing device, 34 Heat exchanger, 40 Heat medium circuit, 41 Heating hot water supply device, 42 Pump, 50 Heat pump device, 100 Plate heat exchanger, 100a Heat transfer Part, 100b Heat transfer part, 200 Heat pump type heating hot water supply system.

Claims (11)

A heat pump device having a heat exchanger for exchanging heat between a refrigerant flowing in the refrigerant circuit and a heat medium flowing in the heat medium circuit,
The heat exchanger includes a plurality of heat transfer plates stacked, and a first flow path through which the first fluid as the refrigerant flows and a second flow path through which the second fluid as the heat medium flows are stacked between the heat transfer plates. The heat transfer plate is provided with a heat transfer portion having a concavo-convex shape in which a convex portion that is convex in one of the stacking directions and a concave portion that is concave are formed in a plane. A plate heat exchanger that performs heat exchange between the first fluid and the second fluid;
Inner fins are arranged in the first flow path,
The inner fin is a plate fin having a flat plate-like flat portion in which a plurality of passage holes are formed, and the flat plate-like flat portion is the concave portion of the heat transfer plate on one side of the plate fin; Sandwiched in contact with the convex portion of the heat transfer plate on the other side of the plate fin,
The passage hole communicates a space between the plate fin and one of the heat transfer plates and a space between the plate fin and the other of the heat transfer plates. The second flow path through which the heat medium flows does not include an inner fin, and the flow path is formed by contacting the convex portion and the concave portion of the adjacent heat transfer plate.
The heat pump apparatus according to claim 1. The concavo-convex shape of the heat transfer plate is a waveform having a ridge line, and the first flow path and the second flow path are formed in a space sandwiched between the corrugated heat transfer plates having different ridge line directions.
The heat pump apparatus according to claim 1 or 2.   4. The heat pump device according to claim 1, wherein the flat plate-like flat portion is joined to the heat transfer plate on the one side and the heat transfer plate on the other side. 5.   The heat pump device according to claim 4, wherein the passage hole is formed so as to avoid a joint portion between the plate fin and the heat transfer plate.   The heat pump device according to any one of claims 1 to 5, wherein in the plate fin, the area ratio of the fin is 0.1 or more and 0.8 or less.   The heat pump device according to any one of claims 1 to 6, wherein the heat transfer plate and the inner fin are laminated with an outer wall peripheral edge protruding in a thickness direction on an outer periphery.   The heat pump device according to claim 7, wherein the inner fin has a region where the passage hole is not formed along a peripheral edge of the outer wall. The heat transfer plate has a first inflow hole through which the first fluid flows into the first flow path and a first outflow hole through which the first fluid flows out of the first flow path with the heat transfer portion interposed therebetween,
9. The hole according to claim 1, wherein a hole through which the first fluid flows is formed in the inner fin at a position corresponding to the first inflow hole and the first outflow hole of the heat transfer plate. Heat pump device. The heat transfer plate has ribs around a second inflow hole through which the second fluid flows into the second flow path and a second outflow hole through which the second fluid flows out of the second flow path with the heat transfer portion interposed therebetween. Have
The heat pump device according to claim 9, wherein the inner fin is configured such that no hole is formed in the lamination direction of the ribs.   The heat pump device according to any one of claims 1 to 10, wherein a thickness of the inner fin is thinner than that of the heat transfer plate.

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