JP6631664B2 - Heat pump equipment - Google Patents

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 has a configuration in which a plurality of heat transfer plates are stacked, and first and second flow passages are alternately formed between the heat transfer plates. , And a fluid is caused to flow between the fluids.

  As a plate-type heat exchanger of this type, a first flow path is formed in a space interposed between heat transfer plates having a corrugated uneven shape in cross section, and the first flow path has a cross sectional shape similar to that of the heat transfer plate. There is a plate heat exchanger having a configuration in which inner fins having a corrugated uneven shape are arranged (for example, see Patent Document 1). In this plate heat exchanger, the heat transfer plate and the inner fin are overlapped and joined in an arrangement where the uneven shape of the heat transfer plate and the uneven shape of the inner fin are not shifted in the stacking direction of the heat transfer plate. ing.

JP-A-2006-70558

  In the plate heat exchanger of Patent Literature 1, both the heat transfer plate and the inner plate have irregularities. For this reason, when these are superimposed as described above, the plates are in point contact with each other in a lattice and are 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 that can improve heat transfer between an inner fin and a heat transfer plate. It is intended to be.

  A heat pump device according to the present invention is a heat pump device having a heat exchanger that exchanges heat between a refrigerant flowing in a refrigerant circuit and a heat medium flowing in a heat medium circuit, wherein the heat exchanger is formed by stacking a plurality of heat transfer plates. The first flow path in which the first fluid as the refrigerant flows and the second flow path in which the second fluid as the heat medium flows between the heat transfer plates are alternately formed in the stacking direction. A plate-type heat exchanger that has a heat transfer portion having an uneven shape in which a convex portion having a convex portion and a concave portion having a concave portion are formed in a plane, and performs heat exchange between the first fluid and the second fluid. An inner fin disposed in the first flow path, wherein the inner fin is a plate fin having a flat plate-shaped portion having a plurality of passage holes formed therein, and the flat plate-shaped flat portion is one of the plate fins. With the recess of the heat transfer plate on the side The plate fin is sandwiched in contact with the convex portion of the heat transfer plate on the other side, and the passage hole is formed between the plate fin and one of the heat transfer plates and the space between the plate fin and the heat transfer plate. And the space between the other.

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

FIG. 2 is an exploded perspective view of the 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. 1. It is a schematic front view of the 2nd heat transfer plate 3 of FIG. It is a schematic front view of the inner fin 2 of FIG. FIG. 2 is a partial cross-sectional view of the heat transfer set 4 of FIG. 1 in a stacking direction. FIG. 2 is a structural perspective view of a first flow path 5 of the plate heat exchanger 100 according to 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 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. FIG. 3 is a front view illustrating a shape example of a passage hole 20a of the plate heat exchanger 100 according to Embodiment 1 of the present invention. In the plate heat exchanger 100 according to Embodiment 2 of the present invention, around the first inflow communication passage 14 having 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. FIG. 3 is a perspective view of a fluoroscope viewed from the front. FIG. 10 is a schematic enlarged cross-sectional perspective view of a part of a heat transfer set 4 of a plate heat exchanger 100 according to Embodiment 3 of the present 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. FIG. 10 is a schematic enlarged cross-sectional perspective view of a part of a heat transfer set 4 of a plate heat exchanger 100 according to Embodiment 3 of the present 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 passage hole 20a of plate fin 2 of plate heat exchanger 100 concerning Embodiment 4 of the present invention from the 2nd flow space 5b side. It is a figure which shows the modification of the passage hole 20a of the straightening wall 26 of the plate heat exchanger 100 which concerns on Embodiment 4 of this invention. FIG. 13 is a schematic enlarged cross-sectional perspective view of a part of a heat transfer set 4 of a plate heat exchanger 100 according to Embodiment 5 of the present invention. It is a schematic sectional view in plate type heat exchanger 100 concerning Embodiment 6 of the present invention. It is an explanatory view of a plate fin area ratio γ in the plate heat exchanger 100 according to Embodiment 7 of the present invention. It is a performance examination effect figure in plate heat exchanger 100 concerning Embodiment 7 of the present invention. It is a schematic diagram showing a configuration of a heat pump type heating and hot water supply system 200 according to Embodiment 8 of the present invention.

  Hereinafter, a plate heat exchanger according to an embodiment of the present invention will be described with reference to the drawings and the like. Here, in the following drawings including FIG. 1, the components denoted by the same reference numerals are the same or equivalent, and are common to the entire text of the embodiments described below. The forms of the constituent elements described in the entire text of the specification are merely examples, and are not limited to the forms described in the specification. Further, in the following drawings, the relationship between the sizes of the components may be different from the actual one.

  Also, in the following description, terms indicating directions (for example, “up,” “down,” “right,” “left,” “front,” “back,” etc.) are used as appropriate to facilitate understanding, This is for explanation, and these terms do not limit the invention. Further, in the first embodiment, when 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, “up”, “down”, “right” , "Left", "front", "back". The “concave” and “convex” are “convex” on the front side and “concave” is the portion 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 an inner fin 2 is arranged between a first heat transfer plate 1 and a second heat transfer plate 3 as shown in FIG. A plurality of heat transfer sets 4 having different configurations are stacked. The first flow path formed between the first heat transfer plate 1 forming the heat transfer set 4 and the second heat transfer plate 3 forming the heat transfer set 4 by stacking a plurality of heat transfer sets 4. 5 and the second flow path 6 formed between the heat transfer sets 4 are alternately laminated, and the first fluid flowing through the first flow path 5 and the second fluid flowing through the second flow path 6 Heat is exchanged between the two. The first fluid is, for example, a refrigerant such as R410A, R32, R290, or CO2, and the second fluid is, for example, water. In FIG. 1, the solid arrows indicate the flow of the first fluid, and the dotted arrows indicate the flow of the second fluid.

  Further, a first reinforcing side plate 7 and a second reinforcing side plate 8 are arranged on the outermost surface of the heat transfer set 4 in the stacking direction. In FIG. 1, the plate laminated on the forefront 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. At the four corners of the first reinforcing side plate 7, circular holes serving as fluid inlets or outlets are formed. A cylindrical inflow pipe or outflow pipe is provided at the periphery of each hole. Specifically, a first inflow pipe 10 into which the first fluid flows is provided at the lower right of the first reinforcing side plate 7, and a first outflow pipe from which the first fluid flows out is provided at the upper right of the first reinforcing side plate 7. 11 are provided. A second inflow pipe 12 through which the second fluid flows 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 is provided at the upper left.

  Each of the first heat transfer plate 1 and the second heat transfer plate 3 is a substantially rectangular plate with rounded corners as shown in FIGS. 2 and 3. The first heat transfer plate 1 and the second heat transfer plate 3 have heat transfer portions 100a and 100b having a cross section in which a corrugated uneven shape (see FIG. 5 described later) is repeated. The material of the first heat transfer plate 1 and the second heat transfer plate 3 is desirably a metal having good heat conductivity, for example, aluminum, copper, or an alloy thereof. Further, in order to improve the strength, the material of the first heat transfer plate 1 and the second heat transfer plate 3 is desirably stainless steel or the like.

  Then, at each of the four corners of the first heat transfer plate 1 and the second heat transfer plate 3, a first inflow pipe 10, a first outflow pipe 11, a second inflow pipe 12, and a second outflow pipe 13 are provided. 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 inflow holes 14a and 14b are inlets of the first flow path 5, the first outflow holes 15a and 15b are outlets of the first flow path 5, the second inflow holes 16a and 16b are inlets of the second flow path 6, The two outflow holes 17a and 17b serve as outlets of the second flow path 6.

  In the following, when there is no need to distinguish between the first heat transfer plate 1 and the second heat transfer plate 3, they are collectively referred to as "heat transfer plates". When there is no need to distinguish between the first reinforcing side plate 7 and the second reinforcing side plate 8, they are collectively referred to as “side plates”.

  As shown in FIG. 4, the inner fin 2 is also a substantially rectangular plate with rounded corners similarly to 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, and a second outflow hole 15c 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 second outflow holes 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. The plate fin 2 has a flat plate-shaped flat portion 20 at a portion facing the heat transfer portions 100a and 100b of the heat transfer plate, and a plurality of passage holes 20a are formed in the flat portion 20. As shown in FIGS. 1 and 4, the passage hole 20a is not provided in the portion of the heat transfer plate facing the rib 3c, around the second inflow hole 16c, and around the second outflow hole 17c. . The passage hole 20a may be a hole having a size smaller than the period of the waveform of the heat transfer plate or a slit having a small width.

  It is desirable that the plate fins 2 be thinner than the heat transfer plate. This is to prevent the size of the entire plate heat exchanger from being increased by disposing the plate fins 2.

  In addition, in order to improve the heat exchange efficiency of the plate heat exchanger 100 and achieve high performance, the material of the plate fin 2 is a metal having good heat conduction, for example, aluminum, copper, or an alloy thereof. It is desirable.

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

  The first inflow through which the first fluid passes by overlapping the first inflow holes 14a to 14c of the first heat transfer plate 1, the plate fins 2, and the second heat transfer plate 3 configured as described above. A communication passage 14 (see FIG. 7 described later) is formed. The first outflow holes 15a to 15c of the first heat transfer plate 1, the plate fins 2, and the second heat transfer plate 3 overlap each other, so that the first outflow communication passage 15 through which the first fluid passes (see FIG. 7) is formed. Similarly, the second inflow communication passage 16 through which the second fluid passes by overlapping the second inflow holes 16a to 16c of the first heat transfer plate 1, the plate fins 2, and the second heat transfer plate 3 (described later). FIG. 7) is formed. Also, the second outflow holes 17a to 17c of the first heat transfer plate 1, the plate fins 2, and the second heat transfer plate 3 overlap each other, so that the second outflow communication passage 17 through which the second fluid passes (see FIG. 7) is formed.

  The first inflow communication path 14 and the first outflow communication path 15 are configured to communicate with the first flow path 5 and not with the second flow path 6. Therefore, the first fluid that has flowed into the first inflow pipe 10 from the outside flows into the first flow path 5 via the first inflow communication path 14. The first fluid that has flowed into the first flow path 5 flows through the first flow path 5 and then flows out of the first outflow pipe 11 through 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 with the first flow path 5. Therefore, the second fluid flowing into the second inflow pipe 12 from the outside flows through the second inflow communication passage 16 and flows into the second flow passage 6. The second fluid that has flowed into the second flow path 6 passes through the second flow path 6 and then flows out of the second outflow pipe 13 through the second outflow communication path 17.

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

  In each of the first heat transfer plate 1 and the second heat transfer plate 3, the corrugations are regularly formed with projections and depressions. Then, the ridge line of the waveform in the first heat transfer plate 1 is inclined from upper left to lower right as shown in FIG. 2, and the ridge line of the waveform in the second heat transfer plate 3 is as shown in FIG. As shown, it is inclined from upper right to lower left. Therefore, as shown in FIG. 6, in a state where the first heat transfer plate 1 and the second heat transfer plate 3 are overlapped, the ridge directions of the respective waveforms intersect with each other, and the corrugations have angles. I have. Therefore, 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.

  The first flow path 5 has a first flow space 5a 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 shown in FIGS. 5b. The first flow space 5a has a configuration in which a plurality of small spaces extending in the ridge direction of the waveform of the first heat transfer plate 1 are formed in a direction intersecting the ridge direction. Similarly, the second flow space 5a has a configuration in which a plurality of small spaces extending in the ridge direction of the second heat transfer plate 3 are formed in a direction intersecting the ridge direction. The first flow space 5a and the second flow space 5b communicate with each other via a passage hole 20a provided in the plate fin 2.

  The second flow path 6 is provided 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 among two adjacent heat transfer sets 4. It is made up of space. The ridge direction of the waveform of the second heat transfer plate 3 and the ridge direction of the waveform 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 3aa in which the concave portion 3 a of the waveform of the second heat transfer plate 3 continues, and the waveform of the first heat transfer plate 1 The contact portion between the convex portion 1b and the convex ridge line 1ba is local, and the 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. Have 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 via the first inflow communication path 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 outer peripheral edges 21 on the left and right sides of the plate fin 2, and flows through the first outflow communication path 15. It flows out of the first outflow pipe 11.

  Here, since the plate fins 2 are provided in the first flow path 5, the first fluid alternately flows 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 is brought into contact with the respective surfaces of the first heat transfer plate 1 and the second heat transfer plate 3 due to the promotion of the turbulent heat transfer and the promotion of the leading edge effect heat transfer by the passage holes 20a, thereby exchanging heat. In addition, the heat exchange with the surface of the plate fin 2 is also effective. That is, by disposing the plate fins 2 in the first flow path 5, the heat transfer area of the first fluid increases. The heat transmitted to the surface of the plate fin 2 is transmitted to the inside of the plate fin 2 by heat conduction, and is transmitted to the respective ridges of the first heat transfer plate 1 and the second heat transfer plate 3 by heat transfer.

  As described above, in addition to the path in which the heat of the first fluid is directly transmitted from the first fluid to the first heat transfer plate 1 and the second heat transfer plate 3, the first heat transfer plate 1 And a path for transmission to the second heat transfer plate 3 is formed. Therefore, 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 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 due to the provision of the plate fins 2 in the first flow path 5. For this reason, it is preferable to flow the first fluid having a lower heat conductivity than the second fluid in the first 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 degree of heat transfer, a fluid having only a gas phase or a two-phase fluid including a liquid phase and a gas phase has higher heat transfer than a fluid having only a liquid phase.

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

  As described above, the portion of the plate fin 2 that is joined to the heat transfer portion 100a of the first heat transfer plate 1 and the heat transfer portion 100b of the second heat transfer plate 3 is a flat plate-shaped flat portion 20. The contact portion between the heat transfer portions 100a and 100b having a waveform is not a point but a line. For this reason, the contact area between the heat transfer plate and the plate fins 2 can be increased, and the heat exchange efficiency can be increased, as compared with a structure in which the joints are point joints as in the conventional case where the plate fins 2 are corrugated. be able to.

  Further, as shown in FIG. 7, the passage holes 20a of the plate fins 2 are formed in a lattice formed by the intersection of the ridge line on the first heat transfer plate 1 side and the ridge line on the second heat transfer plate 3 side. Have been. That is, the passage hole 20a is formed at a position avoiding the joint 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 is reduced. On the other hand, since the passage hole 20a is provided so as to avoid the joining portion between the heat transfer plate and the plate fin 2, the disadvantage that the heat exchange efficiency is reduced 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 portion of the heat transfer plate. For this reason, the contact area between the heat transfer plate and the plate fins 2 can be increased, and the heat exchange efficiency can be increased, as compared with a structure in which the joints are point joints as in the conventional case where the plate fins 2 are corrugated. be able to.

  Further, by disposing the plate fins 2 having the passage holes 20a between the heat transfer plates in the flow path in which the two-phase (liquid phase and gas phase) or the fluid having low heat conductivity flows, the turbulent heat transfer is promoted. And both the leading edge effect heat transfer enhancement. Further, the two flow path structures of the plate heat exchanger 100 can be individually designed. In addition, the heat transfer area on the fluid side having low heat conductivity can be increased. As described above, the performance of the plate heat exchanger 100 can be improved as a whole.

  In addition, since the heat transfer plate and the plate fins 2 are line-joined, the strength of the plate heat exchanger 100 can be improved.

  In addition, the distance from the point other than the line contact portion to the line contact portion on the surface of the plate fin 2 is shorter than that of the point contact structure, and the distance for conducting heat inside the plate fin 2 is shorter. Can be improved.

  Further, if the passage hole 20a is provided at a portion of the plate fin 2 which is 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. , Joint area is reduced. However, in the first embodiment, since the passage holes 20a are arranged in the lattice-like lattice while avoiding the portion joined to the ridge line of the heat transfer plate in the plate fin 2, the plate type by the passage holes 20a is used. Inconvenience such as the performance of the heat exchanger 100 does not occur.

  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 unavoidably 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 a plate-type heat exchanger without the plate fins 2 is provided in the housing of the heat pump device, the plate-type heat exchanger can be replaced with the first embodiment without changing the size of the housing. Can be replaced with the plate heat exchanger 100 of the first embodiment having the plate fins 2 of the first embodiment. In this case, the performance of the heat pump device can be improved by a simple operation of merely replacing the plate heat exchanger.

  Also, a plurality of passage holes 20a are formed in the plate fin 2, and the first fluid alternately flows through the passage holes 20a to the first flow space 5a and the second flow space 5b, so that turbulent heat transfer is promoted. And both the leading edge effect heat transfer enhancement.

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

  Further, since the heat exchange part of the plate heat exchanger 100 is constituted only by the heat transfer plate, the side plates and the plate fins 2, the structure can be simplified, the size of the heat exchanger can be reduced, and the cost can be reduced. .

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

  In addition, the plate heat exchanger of 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 side of the first flow path 5 through which the first fluid having lower heat conductivity flows, but the plate fins 2 are disposed on the side of the second flow path 6 through which second fluid having higher heat conductivity flows. It may be arranged. However, depending on the size of the passage hole 20a, the flow resistance of the second fluid may increase. In this case, it is better not to dispose the plate fin 2 in the second flow passage 6. Which of the first flow path 5 and the second flow path 6 the plate fins 2 should be arranged may be determined in consideration of the effects of heat transfer and resistance between the first fluid and the second fluid.

  Further, 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 structures. When the plate fins 2 are provided in both the first flow path 5 and the second flow path 6, the structures are different from each other in order to make the first flow path 5 and the second flow path 6 different in heat conductivity. The plate fins 2 may be arranged. In order to make the configuration of the plate fin 2 different, for example, the size, shape, density, position, and the like of the passage hole 20a may be changed. As described above, when the plate fins 2 are arranged 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 20a. Can be designed.

  In the above description, the shape of the passage hole 20a is circular when viewed from the front, 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 direction of the second flow space 5b of the first flow path 5, and for example, as shown in FIG. Is 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, or the like, as shown in FIG. Further, the shape of the passage hole 20a provided in the plate fin 2 may be unified into one shape, or different shapes may be mixed and provided. The standard of the design of the passage hole 20a is to reduce the processing cost of the plate fin 2 while maintaining the heat transfer performance, to reduce the flow resistance of the flow path, to increase the heat transfer area, and the like.

  Although the plate fins 2 are flat, local unevenness may be present at the edge 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 size of each passage hole 20a is considered in consideration of the in-plane distribution of fluid in the first flow path 5. The size is changed. Hereinafter, the second embodiment will be described focusing on the differences from the first embodiment, and the configuration that is not described in the second embodiment is the same as the first embodiment.

  FIG. 9 shows a first inflow of a plate-type heat exchanger 100 according to Embodiment 2 of the present invention in which plate fins 2 are arranged and stacked between first heat transfer plate 1 and second heat transfer plate 3. FIG. 2 is a perspective view of the vicinity of the communication passage viewed from the front. Although FIG. 9 shows a front perspective local view around the first inflow communication passage 14, the structure around the first outflow communication passage 15 is almost 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 outer peripheral edge 19 on the left side respectively indicate the flow of the flow in the first flow path 5. Shows the 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, the first fluid flows in from the first inflow communication passage 14, so that the flow velocity in a portion near the first inflow communication passage 14 is faster than the flow velocity in a portion far from the first inflow communication passage 14. . For this reason, if no countermeasures are taken, the first fluid is biased to a region that linearly goes from the first inflow communication passage 14 to the first outflow communication passage 15, and the first fluid reaches the left and right outer wall peripheral edges 21 of the plate fin 2. The first fluid does not spread, and the in-plane distribution of the first fluid in the first flow path 5 becomes uneven.

  Therefore, in the plate heat exchanger 100 according to the second embodiment, as shown in FIG. 9, each passage hole 20a formed in the plate fin 2 is moved away from the first inflow communication passage 14 as the distance from the first inflow communication passage 14 increases. The hole diameter is large. In other words, each hole diameter of each passage hole 20a is formed to be larger from the first inflow communication passage 14 toward the outer wall peripheral edge 21. Accordingly, the flow path resistance of the passage hole 20a becomes smaller to larger as going from the first inflow communication passage 14 to 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 not only flows upward but also spreads toward the left and right outer wall peripheral edges 21, and has a uniform in-plane distribution of the first fluid. Can be achieved. In this way, each passage hole 20a formed such that the hole diameter increases as the position from the first inflow communication passage 14 moves away forms a uniform portion of the present invention.

  The area in which the diameter of the passage hole 20a is changed may be around the first inflow communication passage 14, and need not be the entire first passage 5. The periphery of the first inflow communication passage 14 may be, for example, an area below a height position set a distance away from the first inflow communication passage 14 in the direction of the first outflow communication passage 15.

  As described above, according to the second embodiment, the same effect as that of the first embodiment can be obtained, and each passage hole 20a around the first inflow communication passage 14 is moved from the first inflow communication passage 14 The holes were formed such that the hole diameter became larger as the position became larger. 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 enlarged to improve the heat exchange efficiency. Hereinafter, the third embodiment will be described focusing on the differences from the first embodiment, and the configuration not described in the third embodiment is the same as 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 of the concave portion of the second heat transfer plate 3 cut in the ridge direction. 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. 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 the passage hole 20a of the plate fin 2 of the plate heat exchanger 100 according to Embodiment 3 of the present invention. FIG. 13 is a perspective view of the passage hole 20a of the plate fin 2 of the 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 that is high enough not to contact the second heat transfer plate 3. The height H of each heat transfer wall 24 is configured to be uniform.

  In the first flow path 5 in which the heat transfer wall 24 is formed, the main flow 25 of the first fluid flowing from the first inflow communication passage 14 into the second flow space 5b flows through the second flow space 5b as it is, A 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 peripheral edge of the passage hole 20a, the heat transfer area of the first fluid is increased as compared with 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 subsequently 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 effects as those of the first embodiment can be obtained, and the following effects can be further obtained because the heat transfer wall 24 is provided on the periphery of the passage hole 20a. That is, the provision of the heat transfer wall 24 increases the heat transfer area. For this reason, the heat transfer efficiency from the first fluid to the plate fins 2 is increased, and as a result, the heat conductivity of the plate heat exchanger 100 can be improved.

  Further, since the heights of the heat transfer walls 24 are the same, the effect of reducing the fin processing cost while increasing the heat transfer area can be obtained.

  The heat transfer wall 24 is provided upright 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 at a time. Therefore, the heat transfer wall 24 can be manufactured at low cost.

  Although the configuration in which the heat transfer wall 24 is provided on the entire periphery of the passage hole 20a is shown here, 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, the same effect can be obtained because the heat transfer area can be increased.

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. The fourth embodiment has a configuration in which a rectifying wall mainly for rectifying the first fluid is provided at a part of the periphery of the passage hole 20a. Hereinafter, the present embodiment 4 will be described focusing on the 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 of the concave portion of the second heat transfer plate 3 cut in the ridge line direction. 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 hole 20a of the plate fin 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 Embodiment 4 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 at a peripheral edge of the first flow path 5 downstream of the main flow 25 of the first fluid in the peripheral edge 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, as it moves toward the outer wall peripheral edge 21. ing.

  In the case of this configuration, paying attention to one rectifying wall 26, in a place where the height of the rectifying wall 26 is low, the first fluid flowing into the second flow space 5b passes through the second flow space 5b as it is. It easily flows toward the outer peripheral edge 21. Accordingly, the flow rate of the first fluid flowing toward the first flow space 5a through the passage hole 20a in which the short flow straightening wall 26 is formed is reduced as much as the first fluid easily flows into the second flow space 5b. Conversely, at a place where the height of the flow regulating wall 26 is high, the first fluid that has flowed into the second flow space 5b is unlikely to flow through the second flow space 5b. Therefore, as 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 function by changing the height H from the plate fin 2. For this reason, by increasing the height H of the rectifying wall 26 from the plate fin 2 as the position from the first inflow communication passage 14 increases, the second H that has flowed into the first flow passage 5 from the first inflow communication passage 14. In addition to flowing upward, the one fluid spreads and flows toward the outer peripheral edges 21 on the left and right sides, so that the in-plane distribution of the first fluid can be made uniform. The rectifying wall 26 configured as described above constitutes the equalizing section of the present invention.

  The flow regulating wall 26 does not need to be provided in all the passage holes 20a, but may be provided in the passage holes 20a around the first inflow communication passage 14. The periphery of the first inflow communication passage 14 may be, for example, an area below a height position set a distance away from the first inflow communication passage 14 in the direction of the first outflow communication passage 15.

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

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

  The plate heat exchanger according to Embodiment 4 is not limited to the above-described structure, and can be variously modified as follows without departing from the spirit of the present 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, which generates a vortex at the tip and can promote heat transfer. In particular, when the plate heat exchanger 100 is used as an evaporator, the gas near the outlet of the evaporator becomes almost gas. Therefore, by disposing the rectifying wall 26 of the delta blade at the outlet of the evaporator, a vortex is generated at the tip. A high heat transfer promoting effect is obtained.

Embodiment 5 FIG.
In the fourth embodiment, all the flow regulating walls 26 are perpendicular to the plate fins 2. However, in the fifth embodiment, the inclination of the flow regulating walls 26 with respect to the plate fins 2 is different. Hereinafter, the fifth embodiment will be described focusing on the differences from the fourth embodiment, and the configuration that is not described in the fifth embodiment is the same as the fourth embodiment.

FIG. 20 is a schematic enlarged cross-sectional perspective view of a part of heat transfer set 4 of plate heat exchanger 100 according to Embodiment 5 of the present invention. FIG. 20 is a cross-sectional perspective view of the concave portion of the second heat transfer plate 3 cut in the ridge direction. The arrow in FIG. 20 indicates the flow direction of the first fluid.
The plate-type heat exchanger 100 according to the fifth embodiment has, like the fourth embodiment, the peripheral edge of the passage hole 20a on the downstream side of the flow 25 of the first fluid in the main flow direction in the first flow path 5. And a rectifying wall 27 protruding toward the second flow space 5b. Each rectifying wall 27 is formed of a square plate, and the height H from the plate fin 2 is uniform. In addition, as the position of each flow straightening wall 27 is further away from the first inflow communication passage 14, in other words, as it approaches the outer wall peripheral edge 21, the erection angle θ of the flow straightening wall 27 with respect to the plate fin 2 becomes larger. Is provided on the plate fin 2.

  The operation of the rectifying wall 27 configured in this manner is the same as that of the rectifying wall 26 of the fourth embodiment, and increases the ease of fluid flow in each passage hole 20 a in a direction away from the side closer to the first inflow communication passage 14. It grows as you go.

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

  Further, here, the shape of the flow regulating wall 27 has been described as a square, but as in the modification described in the fourth embodiment, the shape is not limited to a square and may be a delta wing or the like. In the case of a delta wing, as described above, a vortex can be generated at the tip to promote heat transfer.

Embodiment 6 FIG.
In the first to fifth embodiments, the uneven shape provided on each of the first heat transfer plate 1 and the second heat transfer plate 3 is a waveform in which the peak portion of the waveform is a peak of a curve. On the other hand, in the sixth embodiment, the concavo-convex shape is a waveform in which the apex of the waveform is trapezoidal. Hereinafter, the sixth embodiment will be described focusing on the differences from the first embodiment, and the configuration not described in the sixth embodiment is the same as the first embodiment.

  FIG. 21 is a schematic sectional view of plate heat exchanger 100 according to Embodiment 6 of the present invention. In FIG. 21, the solid arrows indicate the flow of the first fluid, and the dotted arrows indicate the flow of the second fluid. As shown in FIG. 21, the vertexes of the waveforms of the first heat transfer plate 1 and the second heat transfer plate 3 are trapezoidal. With this configuration, the joint between the concave ridge line 1aa of the first heat transfer plate 1 and the plate fin 2, the joint between the plate fin 2 and the convex ridge line 3ba of the second heat transfer plate 3, the second heat transfer The respective joint surfaces of the joint between the concave ridge line 3aa of the plate 3 and the convex ridge line 1ba of the first heat transfer plate 1 are enlarged as compared with the case where the peak portion of the waveform is formed into a curved mountain shape.

  Therefore, according to the sixth embodiment, the following effects can be further obtained in addition to the effects similar to those of the first embodiment. In other words, the heat transfer area between the plates is increased as compared with the case where the apex of the waveform is a peak of a curve, so that the heat exchange efficiency can be increased. In addition, the strength of the plate heat exchanger 100 can be improved as compared with the case where the apex of the waveform is a peak of a curve.

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

  The “index relating to the area of the passage hole 20a” refers to “the area of the grid 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”. Of the passage hole 20a (hereinafter, referred to as a plate fin area ratio γ). More specifically, the following definition is made 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 : The area of the grid in the plate fin
A _hole : In the plate fin, the area of the passage hole in the lattice

FIG. 23 is a performance study effect diagram of 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 a heat transfer characteristic 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, performance can be improved as compared with the configuration in which the plate fin 2 is not provided.
Note that the upper limit is set to 0.8 because if it exceeds 0.8, the pressure loss increases significantly.

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

  Here, the plate fin area ratio of “1” corresponds to a configuration in which the plate fin 2 has no passage hole 20a. As shown in FIG. 23, the performance ratio when the plate fin area ratio is “1” exceeds 1.0. That is, even if the plate fin 2 does not have the passage hole 20a, the performance can be improved as long as the plate fin 2 is provided, as compared with the configuration without the plate fin. As described above, even when 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 each a plate heat exchanger. The case where it is parallel to the side surface of 100 is applicable. In addition, a 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 corresponds to the case.

  Also, here, the configuration in which the position of the passage hole 20a is the center of the grid-like lattice has been illustrated and described, but substantially the same effect can be obtained even if the position slightly deviates from the center.

  In addition, although each of the above-described first to seventh embodiments has been described as another embodiment, a plate-type heat exchanger may be configured by appropriately combining the characteristic configurations of each embodiment. 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 the periphery of each passage hole 20a. It may be a plate heat exchanger. Further, the second embodiment and the sixth embodiment are combined to provide a configuration in which the diameter of each passage hole 20a is changed, and a concavo-convex shape provided in each of the first heat transfer plate 1 and the second heat transfer plate 3. A plate heat exchanger having a trapezoidal configuration may be used.

Further, in each of the first to seventh embodiments, the plate heat exchanger 100 is described as a single wall type, but may be a double wall type. The single wall type is a plate type heat exchanger in which the first heat transfer plates 1 and the second heat transfer plates 3 are alternately stacked one by one. Further, the double wall type has a configuration in which the first heat transfer plate 1 and the second heat transfer plate 3 are alternately stacked two by two, and the two heat transfer plates are communicated 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 type heating and hot water supply system will be described as an example of a usage mode of the heat pump device 50.

FIG. 24 is a schematic diagram showing a configuration of a heat pump heating and hot water supply system 200 according to Embodiment 8 of the present invention.
The heat pump type hot water supply system 200 includes a heat pump device 50 housed in a housing. The heat pump device 50 has 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 device 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 such that the refrigerant flows through the first flow path 5 having higher heat conductivity than the second flow path 6 and the heat medium flows through the second flow path 6. It is built into the refrigerant circuit.

  The heating and hot water supply device 41 includes a hot water storage tank (not shown), an indoor unit (not shown) for air-conditioning the room, and the like. When the heat medium is water, the water is heated by exchanging heat with the refrigerant of the refrigerant circuit 30 in 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 to exchange heat with indoor air. Note that the configuration of the heating and hot water supply device 41 is not particularly limited to the above configuration, and any configuration may be used as long as heating and hot water supply can be performed using the heat of the heat medium of the heat medium circuit 40.

  As described in the above embodiment, the plate heat exchanger 100 has good heat exchange efficiency, and has improved strength and high reliability. Therefore, when the plate heat exchanger 100 is mounted on the heat pump heating and hot water supply system 200 described in the eighth embodiment, the heat pump heating and hot water supply system 200 can be efficient, reduce power consumption, and 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, the heat pump heating / hot water supply system 200 that exchanges heat between refrigerant and water has been described. However, the plate type heat exchanger 100 described in the above embodiment is not limited to the heat pump type heating and hot water supply system 200, but may be used for many industrial devices and households such as a cooling chiller, a power generation device, and a food heat sterilization processing device. Available to 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 device that requires easy production, improved heat exchange performance, and improved energy saving performance. .

  DESCRIPTION OF SYMBOLS 1 1st heat transfer plate, 1a concave part, 1aa concave ridge line, 1b convex part, 1ba convex ridge line, 2 plate fin (inner fin), 3rd heat transfer plate, 3a concave part, 3aa concave ridge line, 3b convex part, 3ba convex Ridgeline, 3c rib, 4 heat transfer set, 5 first channel, 5a space, 5b space, 6 second channel, 7 first reinforcing side plate, 8 second reinforcing side plate, 10 first inlet pipe, 11th 1 outflow pipe, 12 second inflow pipe, 13 second outflow pipe, 14 first inflow communication path, 14 a first inflow hole, 14 b first inflow hole, 14 c first inflow hole, 15 first outflow communication path, 15 a 1 outflow hole, 15b first outflow hole, 15c first outflow hole, 16 second inflow communication passage, 16a second inflow hole, 16b second inflow hole, 16c second inflow hole, 17 second outflow communication passage, 17a Second outflow , 17b second outlet hole, 17c second outlet hole, 19 outer wall peripheral edge, 20 flat portion, 20a passage hole, 21 outer wall peripheral edge, 22 arrow, 23 arrow, 24 heat transfer wall, 25 main stream, 26 rectifying wall, 27 rectifying wall , 30 refrigerant circuit, 31 compressor, 32 heat exchanger, 33 pressure reducing device, 34 heat exchanger, 40 heat medium circuit, 41 heating and hot water supply device, 42 pump, 50 heat pump device, 100 plate heat exchanger, 100a heat transfer Unit, 100b heat transfer unit, 200 heat pump heating and hot water supply system.

Claims (11)

A heat pump device having a heat exchanger that performs heat exchange between a refrigerant flowing in a refrigerant circuit and a heat medium flowing in a heat medium circuit,
In the heat exchanger, a plurality of heat transfer plates are stacked, and between the heat transfer plates, 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. The heat transfer plate is provided with a heat transfer portion having a concavo-convex shape in which a convex portion and a concave portion which are convex in one of the stacking directions are formed in a plane. A plate heat exchanger that performs heat exchange between the first fluid and the second fluid,
An inner fin is arranged in the first flow path,
The inner fin is a plate fin having a flat plate-shaped portion in which a plurality of passage holes are formed, and the flat plate-shaped portion is the concave portion of the heat transfer plate on one side of the plate fin, It is sandwiched in a state of contact with the convex portion of the heat transfer plate on the other side of the plate fin,
The heat pump device, wherein 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 device according to claim 1. The uneven 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 heat transfer plates having the ridge line directions different from each other,
The heat pump device according to claim 1.   4. The heat pump device according to claim 1, wherein the flat plate-shaped 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 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, an 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 stacked with an outer 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 along the outer wall peripheral edge where the passage hole is not formed. 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.
The hole according to any one of claims 1 to 8, 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 equipment. 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 from the second flow path with the heat transfer portion interposed therebetween. Has,
The heat pump device according to claim 9, wherein the inner fin is configured such that a hole is not formed in a direction in which the ribs are stacked.   The heat pump device according to claim 1, wherein a plate thickness of the inner fin is smaller than a thickness of the heat transfer plate.

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