JP7270776B2 - Plate heat exchanger, heat pump device with plate heat exchanger and heat pump heating system with heat pump device - Google Patents

Description

The present disclosure relates to a plate heat exchanger with inner fins, a heat pump device with the plate heat exchanger, and a heat pump heating system with the heat pump device.

Conventionally, there is Patent Document 1 as a heat exchanger provided with inner fins. The inner fins of Patent Document 1 are disposed in the exhaust passage and are formed to have a rectangular wave-like cross-sectional shape when viewed from the exhaust flow direction, and the wave-like side portions are offset in the direction in which the waves continue. This is an offset type fin in which a plurality of segments are formed. A triangular cut-and-raised portion protruding inward from the wavy shape is formed on the wavy top surface portion of the fin, and one cut-and-raised portion is formed for each segment, and is inclined with respect to the flow direction of the exhaust gas. formed in this way.

Japanese Patent No. 4683111

In Patent Document 1, a triangular cut-and-raised portion is provided in one segment, and the cut-and-raised portion forms a vortex in the flow of the exhaust gas to improve the heat transfer performance. However, since the cut-and-raised portion is formed so as to be inclined with respect to the flow direction of the exhaust gas, there is a problem that the pressure loss of the fluid increases.

The present disclosure has been made in view of such points, and includes a plate heat exchanger capable of improving heat transfer performance while reducing pressure loss, a heat pump device including the plate heat exchanger, and An object of the present invention is to provide a heat pump heating system equipped with a heat pump device.

A plate-type heat exchanger according to the present disclosure is a plate-type heat exchanger in which a flow channel is formed by each space between a plurality of stacked heat transfer plates, and inner fins are arranged in the flow channel, A direction perpendicular to the first direction is a first direction, a direction perpendicular to the first direction is a second direction, and a direction perpendicular to the first and second directions is a third direction, The inner fin has a side surface extending in the third direction and a contact surface joined to the heat transfer plate, and the width W of the contact surface in the second direction is larger than the height H of the side surface in the third direction. The contact surface is provided with a first opening whose length L in the second direction is equal to or greater than the height H of the side surface in the third direction. A protruding portion protruding in parallel to the is formed .

According to the plate heat exchanger according to the present disclosure, since the width W of the contact surface in the second direction is larger than the height H of the side surface in the third direction, The density of the side surfaces of the inner fins is reduced compared to when the inner fins are made smaller, and the pressure loss can be reduced. In addition, since the contact surface is provided with the first opening whose length L in the second direction is equal to or greater than the height H of the side surface in the third direction, the heat transfer area is equal to that of the inner wall surface of the first opening. can be increased, and the heat transfer performance can be improved.

1 is an exploded perspective view of plate heat exchanger 100 according to Embodiment 1. FIG. 2 is a front view of a first heat transfer plate of plate heat exchanger 100 according to Embodiment 1. FIG. 2 is a front view of a second heat transfer plate of plate heat exchanger 100 according to Embodiment 1. FIG. FIG. 3 is a cross-sectional view of the fin portion of the laminated portion where two heat transfer sets 200 of the plate-type heat exchanger 100 according to Embodiment 1 are laminated, taken along the line AA in FIG. FIG. 3 is a cross-sectional view of the header portion of the laminated portion in which two heat transfer sets 200 of the plate-type heat exchanger 100 according to Embodiment 1 are laminated, taken along the line BB in FIG. FIG. 3 is a cross-sectional view of the header portion of the laminated portion where two heat transfer sets 200 of the plate-type heat exchanger 100 according to Embodiment 1 are laminated, taken along CC in FIG. 4 is a perspective view of part of inner fins 4 of plate heat exchanger 100 according to Embodiment 1. FIG. 4 is a front view of part of inner fins 4 of plate heat exchanger 100 according to Embodiment 1. FIG. FIG. 9 is a cross-sectional view taken along the line AA of FIG. 8; 4 is a front view of slit portions of inner fins 4 of the plate heat exchanger 100 according to Embodiment 1. FIG. 4 is a diagram showing calculation results of a pressure loss ratio and a heat transfer performance ratio of inner fins of the plate heat exchanger 100 of Embodiment 1. FIG. FIG. 11 is a perspective view of part of inner fins 4 of the plate heat exchanger 100 according to Embodiment 2; FIG. 11 is a front view of part of inner fins 4 of the plate heat exchanger 100 according to Embodiment 2; FIG. 14 is a cross-sectional view taken along the line AA of FIG. 13; FIG. 10 is a cross-sectional view of part of a component where inner fins 4 are joined between first heat transfer plate 1 and second heat transfer plate 2 of plate heat exchanger 100 according to Embodiment 2; FIG. 9 is a diagram showing calculation results of a pressure loss ratio and a heat transfer performance ratio of inner fins of the plate heat exchanger 100 according to Embodiment 2; FIG. 11 is a cross-sectional view of a portion of a plate heat exchanger 100 according to Embodiment 3, in which inner fins 4 are joined between the first heat transfer plate 1 and the second heat transfer plate 2; FIG. 18 is a cross-sectional view taken along line AA of FIG. 17; FIG. 18 is a cross-sectional view taken along the line BB of FIG. 17; FIG. 5 is a flow distribution diagram of fluid when the inner fins are not provided with protrusions as a comparative example. FIG. 10 is a flow distribution diagram of fluid in the plate heat exchanger 100 according to Embodiment 3; FIG. 11 is a cross-sectional view of a portion of a plate heat exchanger 100 according to Embodiment 4, in which inner fins 4 are joined between first heat transfer plates 1 and second heat transfer plates 2; FIG. 23 is a cross-sectional view taken along the line AA of FIG. 22; FIG. 23 is a cross-sectional view taken along the line BB of FIG. 22; FIG. 10 is a cross-sectional view of a portion of the plate heat exchanger 100 of pattern 1 according to Embodiment 5, in which inner fins 4 are joined between the first heat transfer plate 1 and the second heat transfer plate 2; FIG. 10 is a cross-sectional view of a part of a configuration portion where inner fins 4 are joined between the first heat transfer plate 1 and the second heat transfer plate 2 of the plate heat exchanger 100 of pattern 2 according to Embodiment 5; FIG. 14 is a cross-sectional view of a portion of a plate heat exchanger 100 according to Embodiment 6, in which inner fins 4 are joined between the first heat transfer plate 1 and the second heat transfer plate 2; FIG. 11 is a perspective view of a part of inner fins 4 of a plate heat exchanger 100 according to Embodiment 6; FIG. 12 is a front view of inner fins 4 of the plate heat exchanger 100 according to Embodiment 6; FIG. 30 is a cross-sectional view taken along the line AA of FIG. 29; FIG. 30 is a cross-sectional view taken along the line BB of FIG. 29; FIG. 11 is a schematic diagram showing the configuration of a heat pump heating system including a plate heat exchanger 100 according to Embodiment 7;

Embodiments of the present disclosure will be described below with reference to the drawings. It should be noted that the present disclosure is not limited by the embodiments described below. Also, in the following drawings, the size relationship of each component may differ from the actual size. In addition, in the following description, terms representing directions (for example, "up", "down", "right", "left", "front", "back", etc.) are used as appropriate for ease of understanding. For the purpose of description, these terms are not intended to limit this disclosure. In the following description, "top", "bottom", "right", "left", "front", and "rear" are used when the plate heat exchanger is viewed from the front.

Embodiment 1.
FIG. 1 is an exploded perspective view of a plate heat exchanger 100 according to Embodiment 1. FIG. FIG. 2 is a front view of the first heat transfer plate of the plate heat exchanger 100 according to Embodiment 1. FIG. FIG. 3 is a front view of the second heat transfer plate of the plate heat exchanger 100 according to Embodiment 1. FIG. FIG. 4 is a cross-sectional view of the fin portion of the laminated portion in which two heat transfer sets 200 of the plate heat exchanger 100 according to Embodiment 1 are laminated, taken along line AA in FIG. FIG. 5 is a cross-sectional view of the header portion of the laminated portion where two heat transfer sets 200 of the plate heat exchanger 100 according to Embodiment 1 are laminated, taken along the line BB in FIG. FIG. 6 is a cross-sectional view of the header portion of the laminated portion where two heat transfer sets 200 of the plate heat exchanger 100 according to Embodiment 1 are laminated, taken along CC in FIG. FIG. 7 is a perspective view of part of the inner fins 4 of the plate heat exchanger 100 according to Embodiment 1. FIG. FIG. 8 is a front view of part of the inner fins 4 of the plate heat exchanger 100 according to Embodiment 1. FIG. 9 is a cross-sectional view taken along the line AA of FIG. 8. FIG. FIG. 10 is a front view of the slit portion of the inner fin 4 of the plate heat exchanger 100 according to Embodiment 1. FIG.

As shown in FIG. 1, the plate heat exchanger 100 of Embodiment 1 has a configuration in which first heat transfer plates 1 and second heat transfer plates 2 are alternately laminated, and adjacent heat transfer plates 1 and 2 are alternately laminated. A channel is formed by the space between the plates. The channels arranged in the stacking direction are alternately composed of the first channels 6 through which the first fluid flows and the second channels 7 through which the second fluid flows. Inner fins 4 are arranged in the first flow path 6 and inner fins 5 are arranged in the second flow path 7 . In this manner, the heat transfer set 200 is configured by laminating the inner fins 4, the first heat transfer plate 1, the inner fins 5, and the second heat transfer plate 2 in order from the front. The first heat transfer plate 1, the second heat transfer plate 2, the inner fins 4, and the inner fins 5 are each configured in a long plate shape.

The plate heat exchanger 100 is configured by stacking a plurality of heat transfer sets 200, and heat exchange is performed between the first fluid flowing through the first flow path 6 and the second fluid flowing through the second flow path 7. conduct. Contact portions of the stacked heat transfer sets 200 are joined by brazing or the like, and the plate heat exchanger 100 as a whole is configured in a rectangular parallelepiped shape.

The first fluid is, for example, water or brine. The first fluid is passed through in a liquid state and carries heat with sensible heat. The second fluid is, for example, a refrigerant R410A, R32, R290, HFOmix or _CO2 . The second fluid transfers the latent heat of phase change, such as gas-liquid, to the first fluid by evaporating or condensing in the flow path. In FIG. 1, dotted line arrows indicate the first fluid, and solid line arrows indicate the second fluid. In FIG. 1, the fluid flow system is a countercurrent flow system in which the first fluid and the second fluid flow in opposite directions, but the first embodiment is not limited to this flow system. . The fluid flow system may be a parallel flow system in which the first fluid and the second fluid flow in the same direction.

The operating pressure on the first fluid side is the pressure of the pump that flows the first fluid, and is always operated at a low pressure. Further, the operating pressure on the second fluid side is the saturation pressure of the second fluid, and is always operated at a high pressure.

A first reinforcing side plate 3 and a second reinforcing side plate 12 are arranged on the outermost surface of the heat transfer set 200 in the stacking direction. In FIG. 1, the first reinforcing side plate 3 is laminated on the frontmost side, and the second reinforcing side plate 12 is laminated on the rearmost side.

Also, the first reinforcing side plate 3 and the second reinforcing side plate 12 are formed in a long plate shape as shown in FIG. 1, and the four corners thereof are rounded. Circular holes are formed at the four corners of the first reinforcing side plate 3 to serve as inlets or outlets for the fluid. A cylindrical inflow pipe or outflow pipe is provided on the periphery of each hole. Specifically, a first inflow pipe 9 into which the first fluid flows is provided on the lower left side of the first reinforcing side plate 3, and a first outflow pipe from which the first fluid flows out is provided on the upper left side of the first reinforcing side plate 3. 10 are provided. A second inflow pipe 11 into which the second fluid flows is provided on the upper right of the first reinforcing side plate 3, and a second outflow pipe from which the second fluid flows out is provided on the lower right of the first reinforcing side plate 3. 8 is provided.

Although FIG. 1 shows a configuration in which the thickness of the side plate is uniform over the entire surface, it is not limited to a uniform configuration. For example, the thickness of the side plate near the inflow pipe and the outflow pipe may be made thicker than the thickness of the other portions. In addition, although the inflow pipe and the outflow pipe have the same size in FIG. 1, the size is not limited to this and may not be the same.

Holes are formed in the first heat transfer plate 1 and the second heat transfer plate 2 so as to face the first inflow pipe 9, the first outflow pipe 10, the second inflow pipe 11, and the second outflow pipe 8, respectively. there is Specifically, as shown in FIG. 2, the first heat transfer plate 1 is provided with a first inlet hole 13 through which the first fluid flows at the lower left, and a first outlet hole 14 through which the first fluid flows out at the upper left. is provided. A second inlet hole 15 through which the second fluid flows is provided on the upper right of the first heat transfer plate 1 , and a second outlet hole 16 through which the second fluid flows out is provided on the lower right. In the first heat transfer plate 1, a cylindrical peripheral wall W is provided around the second inflow hole 15 and the second outflow hole 16, and the second inflow hole 15 and the second outflow hole 16 are arranged in the first direction. It is configured so as not to communicate with the flow path 6 . This prevents the second fluid from flowing into the first channel 6 from the second inlet 15 and the second outlet 16 .

In addition, as shown in FIG. 3, the second heat transfer plate 2 is provided with a first inlet hole 17 through which the first fluid flows at the lower left, and a first outlet hole 18 through which the first fluid flows out at the upper left. be provided. A second inlet hole 19 through which the second fluid flows is provided at the upper right of the second heat transfer plate 2, and a second outlet hole 20 through which the second fluid flows is provided at the lower right. In the second heat transfer plate 2, a cylindrical peripheral wall W is provided around the first inflow hole 17 and the first outflow hole 18, and the first inflow hole 17 and the first outflow hole 18 are arranged in the second direction. It is configured so as not to communicate with the flow path 7 . This prevents the first fluid from flowing into the second channel 7 through the first inlet 17 and the first outlet 18 .

In the following, when there is no need to distinguish between the first heat transfer plate 1 and the second heat transfer plate 2, they are collectively referred to as "heat transfer plates". Further, when there is no need to distinguish between the first reinforcing side plate 3 and the second reinforcing side plate 12, they are collectively referred to as "side plates". Moreover, when it is not necessary to distinguish between the first flow path 6 and the second flow path 7, they are collectively referred to as "flow paths".

Moreover, below, the flow direction of the fluid, ie, the up-down direction of FIG. 1, is called 1st direction. A direction perpendicular to the first direction, that is, the left-right direction in FIG. 1 is referred to as a second direction. A direction orthogonal to the first direction and the second direction and a direction in which the heat transfer plates are stacked is referred to as a third direction.

As shown in FIG. 4, the heat transfer plate has flat portions 22 and outer wall portions 23 extending outward from both ends of the flat portions 22 in the second direction. The portions 23 are in contact with each other. A space is formed between adjacent flat portions 22 , and this space serves as the first flow path 6 or the second flow path 7 . In FIG. 4 , the first flow path 6 is between the two heat transfer sets 200 , and the second flow path 7 is between the first heat transfer plate 1 and the second heat transfer plate 2 . Further, as shown in FIG. 3, header portions 21 are provided at both end portions of the heat transfer plate in the first direction.

Materials such as stainless steel, carbon steel, aluminum, copper, and alloys thereof are used for the heat transfer plate, and the case where stainless steel is used will be described below.

The inner fins 4 have the same height H (see FIG. 9) as the flow path height l ₁ (see FIG. 4) of the first flow path 6, and the flat portion 22 of the first heat transfer plate 1 and the second heat transfer plate It is in contact with the flat portion 22 of the heat plate 2 . The contact portion may be joined by brazing or the like, or may not be joined. In addition, the inner fins 5 have the same height as the flow channel height l ₂ (see FIG. 4) of the second flow channel 7, and the flat portion 22 of the first heat transfer plate 1 and the second heat transfer plate 2 It is in contact with the flat portion 22 . Although the height H of the inner fins 4 is higher than the height of the inner fins 5 here, the heights may be the same, or the relationship may be reversed.

As shown in FIGS. 4, 7 and 9, the inner fin 4 has a side surface 24 extending in the third direction and a contact surface 25 that contacts the heat transfer plate. More specifically, the inner fins 4 are composed of offset fins. That is, in the inner fin 4, a plurality of wavy portions formed by alternately connecting the side surfaces 24 and the contact surfaces 25 in the second direction are alternately arranged in the first direction with a half-wave shift. have a configuration. As shown in FIGS. 7 to 9, the contact surface 25 has a rectangular shape when viewed from the front, and the width W in the second direction (see FIG. 9) is greater than the height H of the side surface 24 in the third direction. Largely configured. As a result, compared to a configuration in which the width W of the contact surface 25 in the second direction is smaller than the height H of the side surface 24 in the third direction, the density of the side surfaces 24 is reduced. Thereby, pressure loss of the fluid can be reduced. Further, since the height H of the side surface 24 is lower than the width W in the second direction, the withstand voltage performance can be improved compared to the case where the height H is higher than the width W. In addition, although the contact surface 25 is configured to have a square shape in a front view here, the shape is not limited to this. When the contact surface 25 has a shape other than a square, the maximum width of the contact surface 25 in the second direction is made larger than the height H of the side surface 24 in the third direction.

As shown in FIG. 9 , the contact surface 25 is provided with a first opening 26 whose length L in the second direction is equal to or greater than the height H of the side surface 24 . The first opening 26 is formed such that the length L in the second direction is longer than the length D in the first direction, as shown in FIG. Here, since the contact surface 25 is formed in a rectangular shape elongated in the second direction, the first opening 26 is also formed in a rectangular shape elongated in the second direction in accordance with the shape of the contact surface 25, in other words, a slit shape. It is However, the first opening 26 may have the same length in the first direction and the second direction. Also, the shape of the first opening 26 is not limited to a square, but may be any one of circular, triangular, polygonal, D-shaped, arrow-shaped, etc. shown in FIG. A combination of shapes may be provided. FIG. 10 shows an example of a pentagon as an example of a polygon, and an example of a straight arrow shape and a concave arrow shape as arrow shapes.

Also, although FIG. 7 shows a configuration in which all the contact surfaces 25 have a width W larger than the height H, the inner fin 4 includes contact surfaces 25 having a width W smaller than the height H. You can stay. In this case, the first opening 26 is formed in a portion of the contact surface 25 having a width W greater than the height H. In other words, the inner fin 4 has a contact surface in which the width W in the second direction is greater than the height H of the side surface 24 in the stacking direction, and the first opening 26 is formed in the contact surface.

The width W of the contact surface 25 is set in the range of 2 to 5 times the height H of the side surface 24 . Further, the width W of the contact surface 25 preferably satisfies H≤WL≤3H in order to maintain the bonding strength between the contact surface 25 and the flat portion 22 of the heat transfer plate. When the width W of the contact surface 25 is set so as to satisfy this relationship, and the first opening 26 is provided in the central portion of the contact surface 25 in the second direction, on both sides of the first opening 26 in the second direction, A joint surface with a width of 0.5 to 1.5H can be formed. Therefore, the bonding strength between the contact surface 25 and the flat portion 22 of the heat transfer plate is maintained, and heat exchange between the inner fins 4 and the heat transfer plate can be sufficiently performed.

Next, the flow of fluid in the plate heat exchanger 100 configured as described above and the action of the first openings 26 of the inner fins 4 will be described.
The first fluid that has flowed into the first inflow pipe 9 for the first fluid from the outside flows into the first flow path 6 via the first inflow hole 13 for the first fluid. The first fluid that has flowed into the first flow path 6 spreads gradually toward the outer wall portions 23 at both end portions of the first heat transfer plate 1 in the second direction, and spreads upward toward the inner fins 4 as shown in FIG. and exits the first fluid first outflow tube 10 via the first fluid first outflow hole 14 .

Further, a second fluid flows through the second flow path 7, and the heat of the second fluid is transferred to the first heat transfer plate 1 or the second heat transfer plate 2. As a result, the first fluid and the second fluid heat exchange with

Here, in the conventional structure in which the inner fin is provided with a triangular cut-and-raised portion inclined with respect to the flow direction of the fluid, the contact surface of the inner fin has a triangular cut-and-raised portion and a triangular opening. is formed. On the other hand, the inner fin of the first embodiment does not have a portion corresponding to the cut-and-raised portion of the conventional structure, and corresponds to a structure in which only the first opening 26 is provided. Therefore, in the inner fin of the first embodiment, the first fluid flowing in the first flow path 6 can be prevented from colliding with the cut-and-raised portion, and the pressure loss in the flow direction of the first fluid can be reduced.

Also, at the first openings 26 of the contact surface 25 , the first fluid directly contacts the first heat transfer plate 1 or the second heat transfer plate 2 without passing through the inner fins 4 . Therefore, the heat exchange performance is also enhanced. In addition, in the first embodiment, the width W of the contact surface 25 is made larger than the height H of the side surface 24, so that the area of the contact surface 25 is expanded compared to a configuration smaller than the height H of the side surface 24. Therefore, a large first opening 26 provided in the contact surface 25 can be ensured. Since the inner wall surface of the first opening 26 serves as a heat transfer surface, by ensuring a large first opening 26, the heat transfer area can be increased, and the heat transfer performance can be improved to enhance the heat exchange performance. can.

FIG. 11 shows the results of calculating changes in the pressure loss ratio and the heat transfer performance ratio when the width W of the contact surface 25 is increased and when the contact surface 25 is provided with openings.

FIG. 11 is a diagram showing calculation results of the pressure loss ratio and the heat transfer performance ratio of the inner fins of the plate heat exchanger 100 of the first embodiment. In FIG. 11, the pressure loss ratio [%] is indicated by a bar graph, and the heat transfer performance ratio [%] is indicated by a line graph. In FIG. 11, "base" is the case where the width W of the contact surface 25 of the inner fin 4 is set to a certain width. "Medium fin width" is the case where the width W of the "base" is increased to 133% with the width W being 100%. "Large fin width" is the case where the width W of the "base" is increased to 189% with the width W being 100%. “Large fin width (with opening)” is the case where the width W of the contact surface 25 is “large fin width” and the contact surface 25 is provided with the first opening 26 .

It can be seen from FIG. 11 that increasing the width W of the contact surface 25 reduces the pressure loss ratio. Also, although it is difficult to understand in FIG. 11 , the “large fin width (with openings)” has a pressure loss ratio that is substantially the same as or slightly improved compared to the “large fin width” in which the first openings 26 are not provided. ing. Further, the heat transfer performance ratio is also improved in the "large fin width (with openings)" compared to the "large fin width" in which the first openings 26 are not provided. 11, by increasing the width W of the contact surface 25 of the inner fin 4 and providing the first opening 26 in the increased contact surface, the heat transfer performance ratio is improved while reducing the pressure loss ratio. I know you can.

Although the configuration using the offset fins is shown here as the inner fins 4, the inner fins 4 are not limited to the offset fins. The inner fins 4 may be one of flat fin type, wavy fin type, louver type, and corrugated fin type, or a combination thereof. In either type, the inner fin of the first embodiment has a contact surface 25 having a width W larger than the height H of the side surface 24 and a length L in the second direction equal to or greater than the height H of the side surface 24 . Any configuration in which the first opening 26 is formed.

Further, although the inner fins 4 have been described here, the inner fins 5 may be configured as described above. Also, both the inner fins 4 and the inner fins 5 may be configured as described above. When both the inner fins 4 and the inner fins 5 are configured as described above, the heat transfer properties of both the first flow path 6 and the second flow path 7 can be further improved, and as a result, the performance of the plate heat exchanger 100 can be improved. can be improved.

As described above, Embodiment 1 is a plate-type heat exchanger in which flow paths are formed by spaces between a plurality of stacked heat transfer plates, and inner fins are arranged in the flow paths, The flow direction of the fluid in the flow channel is defined as the first direction, the direction orthogonal to the first direction is defined as the second direction, and the direction orthogonal to the first direction and the second direction is defined as the third direction. When the inner fin has a side surface extending in the third direction and a contact surface 25 joined to the heat transfer plate, the width W of the contact surface 25 in two directions is greater than the height H of the side surface in the third direction. The contact surface 25 is provided with a first opening whose length L in the second direction is equal to or greater than the height H of the side surface in the third direction.

In this way, the width W of the contact surface 25 in two directions is made larger than the height H of the side surface in the third direction, and the contact surface 25 has a length L in the second direction of the side surface in the third direction. By providing the first opening having the height H or more, the heat transfer performance can be improved while reducing the pressure loss. Further, in the first embodiment, the existing components are structurally modified, and no additional parts are required. By improving the performance, the high performance of the plate heat exchanger 100 can be realized.

In the first embodiment, the first opening 26 is provided at the center of the contact surface 25 in the second direction, and the width W of the contact surface 25 is two to five times the height H of the side surface. and the length L of the first opening 26 in the second direction satisfies H≦WL≦3H.

Thereby, joint surfaces having a width of 0.5 to 1.5H can be formed on both sides of the first opening 26 in the second direction. Therefore, the bonding strength between the contact surface 25 and the heat transfer plate is maintained, and heat exchange between the inner fins 4 and the heat transfer plate can be sufficiently performed at the contact surface.

Embodiment 2.
The second embodiment will be described below, but the description of the parts that overlap with the first embodiment will be omitted, and the same reference numerals will be given to the parts that are the same as or correspond to those of the first embodiment.

FIG. 12 is a perspective view of part of the inner fins 4 of the plate heat exchanger 100 according to Embodiment 2. FIG. FIG. 13 is a front view of part of the inner fins 4 of the plate heat exchanger 100 according to Embodiment 2. FIG. 14 is a cross-sectional view taken along line AA of FIG. 13. FIG. FIG. 15 is a cross-sectional view of a portion of the plate heat exchanger 100 according to Embodiment 2, in which the inner fins 4 are joined between the first heat transfer plate 1 and the second heat transfer plate 2. FIG. .

The inner fins 4 of the plate-type heat exchanger 100 according to the second embodiment have a configuration in which protrusions 27a and 27b extending in the third direction are formed at both ends of the first opening 26 in the second direction. have. The protruding portion 27a and the protruding portion 27b are parallel to the side surface 24 of the inner fin 4. As shown in FIG. The protrusions 27a and 27b may be formed by any method, but may be formed by cutting and raising from the contact surface 25, for example.

By providing the protrusions 27a and 27b on the inner fins 4 in this manner, the heat transfer area can be increased, and the heat transfer performance can be improved. Moreover, since each of the protrusions 27a and 27b is formed parallel to the side surface 24 of the inner fin 4, it is possible to suppress an increase in pressure loss of the first fluid.

As shown in FIGS. 14 and 15, when the height of the projecting portion 27a is H ₁ and the height of the projecting portion 27b is H ₂ , H ₁ =H ₂ . Further, when the thickness of the inner fin 4 is T, H ₁ +T=H ₂ +T=H. 2 is in contact with the heat transfer plate 2; In this way, the protruding portion 27a and the tip portion 28 of each of the protruding portions 27a are in contact with the first heat transfer plate 1 or the second heat transfer plate 2, so that the inner fins 4 are more stable than when they are not in contact with each other. and the thermal resistance between the heat transfer plates can be reduced. The contact portions between the protrusions 27a and the tip portions 28 of the protrusions 27a and the heat transfer plate may or may not be joined.

FIG. 16 is a diagram showing calculation results of the pressure loss ratio and the heat transfer performance ratio of the inner fins of the plate heat exchanger 100 according to the second embodiment. In FIG. 16, the pressure loss ratio [%] is indicated by a bar graph, and the heat transfer performance ratio [%] is indicated by a line graph.
The “base” in FIG. 16 is the same as the “base” in FIG. 11, and “large fin width (with first opening)” in FIG. 16 is “large fin width (with first opening)” in FIG. is similar to 16, "large fin width (with first opening)", "large fin width (medium number of protrusions)", and "large fin width (large number of It is constant at 189% of the "wide" or "base". The medium number of protrusions means a configuration in which the protrusions 27 a and 27 b are provided in about half of all the first openings 26 of the inner fin 4 . A large number of protrusions means a configuration in which all the first openings 26 of the inner fin 4 are provided with the protrusions 27a and 27b.

It can be seen from FIG. 16 that the heat transfer performance ratio can be greatly improved by increasing the number of protrusions 27a and 27b, although the pressure loss ratio increases. In addition, when comparing the "base" and the "large fin width (large number of protrusions)", the "large width fin (large number of protrusions)" can reduce the pressure loss ratio to about 80%, and the heat transfer performance ratio is reduced to about 80%. It can be seen that a 25% improvement can be achieved.

Although the structure in which the inner fin 4 is provided with the protruding portion 27a and the protruding portion 27b has been described here, it may be provided in the inner fin 5, or may be provided in both the inner fin 4 and the inner fin 5. good.

According to the second embodiment, similarly to the first embodiment, the pressure loss of the fluid can be reduced by increasing the width W of the contact surface 25 in the second direction. In the second embodiment, the heat transfer performance is further improved by providing a protrusion 27a and a protrusion 27b extending parallel to the side surface 24 at both ends of the first opening 26 in the second direction. can be planned. Further, the tip portions 28 of the projecting portions 27a and 27b are joined to the first heat transfer plate 1 or the second heat transfer plate 2, thereby reducing the thermal resistance between the inner fins and the heat transfer plate. be able to.

Embodiment 3.
The third embodiment will be described below, but the description of the parts that overlap with the first and second embodiments will be omitted, and the same or corresponding parts will be given the same reference numerals.

FIG. 17 is a cross-sectional view of a portion of the plate heat exchanger 100 according to Embodiment 3, in which the inner fins 4 are joined between the first heat transfer plate 1 and the second heat transfer plate 2. FIG. . 18 is a cross-sectional view taken along the line AA of FIG. 17. FIG. 19 is a cross-sectional view taken along the line BB of FIG. 17. FIG.

In the second embodiment, the heights of the projections 27a and 27b are the same, but in the third embodiment, the height _H1 of the projection 27a and the height _H2 of the projection 27b are different. different. In this example, the height _H1 of the projection 27a is shorter than the height _H2 of the projection 27b, but the reverse is also possible. With such a structure in which the heights of the projections are varied, the uneven flow in the flow path can be improved.

Also, as shown in FIGS. 17 and 18, the tip end portion 28 of the protruding portion 27b is in contact with the first heat transfer plate 1 and the second heat transfer plate 2, so that the inner fin 4 is more stable than when they are not in contact with each other. and the thermal resistance of the first heat transfer plate 1 can be reduced.

On the other hand, as shown in FIG. 19, the tip portion 28 of the projecting portion 27a is not in contact with the first heat transfer plate 1 and the second heat transfer plate 2 . Therefore, thermal resistance increases compared to the case of contact. However, the heat transfer performance can be improved by increasing the heat transfer area as described below. That is, since the tip portion 28 of the protruding portion 27a is not in contact with the heat transfer plate facing the tip portion 28, a gap is formed between the tip portion 28 and the heat transfer plate. passes through. Therefore, the heat transfer area between the first fluid and the inner fins 4 and the heat transfer area between the first fluid and the heat transfer plate increase by the area of the tip portion 28 of the projecting portion 27a. By increasing the heat transfer area in this way, the heat transfer performance can be improved.

FIG. 20 is a flow distribution diagram of fluid when the inner fins are not provided with protrusions as a comparative example. FIG. 21 is a flow distribution diagram of fluid in the plate heat exchanger 100 according to the third embodiment.

In FIG. 20 and FIG. 21, the dark portions indicate the portions where the flow velocity is fast, and the light portions indicate the portions where the flow velocity is slow. As is clear from a comparison of FIGS. 20 and 21, FIG. 21, in which the projections 27a and 27b are provided, reduces variations in the flow velocity distribution and improves drift compared to FIG. I understand.

According to the third embodiment, effects similar to those of the first and second embodiments can be obtained. Further, in the third embodiment, as in the second embodiment, the protrusions 27a and 27b extending in the third direction are provided at both ends of the first opening 26 in the second direction. It is possible to improve the heat transfer performance. Further, in the third embodiment, the uneven flow can be improved by differentiating the heights of the projections 27a and 27b.

Further, in the third embodiment, the tip portion 28 of the projecting portion 27b is configured to contact the heat transfer plate facing the tip portion 28, thereby reducing the thermal resistance between the inner fin 4 and the heat transfer plate. can be done. In addition, in the third embodiment, the tip portion 28 of the protruding portion 27a is configured so as not to contact the heat transfer plate facing the tip portion 28, so that the heat transfer area can be increased, and the heat transfer performance is improved. can improve. As described above, the heat exchange performance of the plate heat exchanger 100 can be improved.

Although the inner fin 4 has been described here, the inner fin 5 may be configured as described above, or both the inner fin 4 and the inner fin 5 may be configured as described above.

Embodiment 4.
The fourth embodiment will be described below, but the description of the parts that overlap with the first to third embodiments will be omitted, and the same or corresponding parts will be given the same reference numerals.

FIG. 22 is a cross-sectional view of a portion of the plate heat exchanger 100 according to Embodiment 4, in which the inner fins 4 are joined between the first heat transfer plate 1 and the second heat transfer plate 2. FIG. . 23 is a cross-sectional view taken along the line AA of FIG. 22. FIG. 24 is a cross-sectional view taken along the line BB of FIG. 22. FIG.

In the second embodiment, the heights of the protrusions 27a and 27b are the same, but in the fourth embodiment, the height _H1 of the protrusion 27a and the height _H2 of the protrusion 27b are different. different. In the fourth embodiment, the tip portions 28 of both protrusions are not in contact with the heat transfer plate.

According to the fourth embodiment, effects similar to those of the first and second embodiments can be obtained. Further, in the fourth embodiment, as in the second embodiment, the protrusions 27a and 27b extending in the third direction are provided at both ends of the first opening 26 in the second direction. It is possible to improve the heat transfer performance. Further, in the fourth embodiment, the uneven flow can be improved by making the protrusions 27a and the protrusions 27b different in height.

Further, in the fourth embodiment, the tip portions 28 of both the protruding portion 27a and the protruding portion 27b are not in contact with the heat transfer plate. As a result, each of the heat transfer area between the first fluid and the inner fins 4 and the heat transfer area between the first fluid and the heat transfer plate is equal to the area of the tip portions 28 of both the projecting portion 27a and the projecting portion 27b. ,To increase. By increasing the heat transfer area in this way, the heat transfer performance can be improved. As described above, the heat exchange performance of the plate heat exchanger 100 can be improved.

Although the inner fin 4 has been described here, the inner fin 5 may be configured as described above, or both the inner fin 4 and the inner fin 5 may be configured as described above.

Embodiment 5.
The fifth embodiment will be described below, but descriptions of the same parts as in the first to fourth embodiments will be omitted, and the same or corresponding parts will be given the same reference numerals.

FIG. 25 is a cross section of a portion of the component where the inner fins 4 are joined between the first heat transfer plate 1 and the second heat transfer plate 2 of the plate heat exchanger 100 of pattern 1 according to the fifth embodiment. It is a diagram. FIG. 26 is a cross section of a portion of the component where the inner fins 4 are joined between the first heat transfer plate 1 and the second heat transfer plate 2 of the plate heat exchanger 100 of pattern 2 according to the fifth embodiment. It is a diagram.

Embodiment 5 corresponds to a form in which the inner fins of Embodiments 1 to 4 are applied to a double-wall heat exchanger. Here, a mode in which the inner fins of the fourth embodiment shown in FIGS. 22 to 24 are applied to a double wall plate heat exchanger will be described.

In Embodiment 5, at least some of the plurality of heat transfer plates are composed of double plates obtained by partially joining two plates. Here, one or both of the first heat transfer plate 1 and the second heat transfer plate 2 have a configuration in which two plates are partially joined. Specifically, FIG. 25 shows a configuration in which only the first heat transfer plate 1 is partially joined with two plates. In FIG. 25, the first heat transfer plate 1 has a structure in which a plate 1a and a plate 1b are partially joined. Moreover, FIG. 26 shows a configuration in which two plates of both the first heat transfer plate 1 and the second heat transfer plate 2 are partially joined. In FIG. 26, the first heat transfer plate 1 has a structure in which plates 1a and 1b are partially joined, and the second heat transfer plate 2 has a structure in which plates 2a and 2b are partially joined. 25 and 26, black-painted portions 29 between plates are joint portions. A fine channel is formed between the two plates, and this fine channel is configured to communicate with the outside.

With this configuration, when a defect occurs in the heat transfer plate, for example, when a defect occurs in the plate 1a of FIG. From the defect point, it flows into the fine flow channel between the two plates 1a and 1b and does not flow into the second flow channel 7 through which the second fluid flows. Therefore, mixing of the first fluid and the second fluid can be avoided. Therefore, the double-wall plate heat exchanger of Embodiment 5 is effective for a mode of use in which it is desired to avoid mixing two kinds of fluids, for example, a mode in which a combustible refrigerant is used as the fluid. Note that the first fluid that has flowed into the microchannel leaks out through the microchannel. Thereby, it is possible to inform the outside that a defect has occurred in the heat transfer plate.

According to the fifth embodiment, the same effects as those of the first to fourth embodiments can be obtained. Mixing can be prevented.

Embodiment 6.
The sixth embodiment will be described below, but the description of the parts that overlap with the first to fifth embodiments will be omitted, and the same or corresponding parts will be given the same reference numerals.

FIG. 27 is a cross-sectional view of a portion of the plate heat exchanger 100 according to Embodiment 6, in which the inner fins 4 are joined between the first heat transfer plate 1 and the second heat transfer plate 2. FIG. . FIG. 28 is a perspective view of part of the inner fins 4 of the plate heat exchanger 100 according to Embodiment 6. FIG. FIG. 29 is a front view of inner fins 4 of plate heat exchanger 100 according to Embodiment 6. FIG. 30 is a cross-sectional view taken along the line AA of FIG. 29. FIG. 31 is a cross-sectional view taken along the line BB of FIG. 29. FIG.

The plate heat exchanger 100 of Embodiment 6 uses water as a fluid, and even if the water freezes in the plate heat exchanger 100 and the heat transfer plates are damaged, the first fluid and the second fluid and are not mixed with each other.

The first heat transfer plate 1 is a double plate formed by partially joining a plate 1a and a plate 1b.

The inner fin 4 of Embodiment 6 is an offset fin as shown in FIGS. 28 and 29. FIG. 28, 30 and 31, the inner fin 4 has a first contact surface 25a on the side joined to the first heat transfer plate 1 and a second contact surface 25a on the side joined to the second heat transfer plate 2. and a contact surface 25b. As shown in FIG. 29, the inner fin 4 has a shape in which the width of the second contact surface 25b is increased from the width W in the second direction to the width _W1 periodically in the first direction. there is For better understanding of this shape, the contact surface portion enlarged to width _W1 (hereinafter referred to as the enlarged contact surface) is shaded with thin dots in FIGS.

By enlarging a portion of the contact surface portion of the inner fin 4 in this way, the enlarged contact surface and the second contact surface 25b ( 29) are combined to form a T-shaped continuous enlarged surface 30. As shown in FIG.

A space surrounded by the continuous enlarged surface 30 and the first heat transfer plate 1 facing the continuous enlarged surface 30 with the first flow path 6 interposed therebetween has a larger volume than other portions. For this reason, the continuously enlarged surface 30 and the portion of the first heat transfer plate 1 facing the continuously enlarged surface 30 are subject to force in the third direction due to the expansion caused by the freezing of the water, and are likely to be damaged. Here, the strength of the plate 1a of the first heat transfer plate 1 is set lower than that of the plate 1b and the second heat transfer plate 2. As shown in FIG. Therefore, when the plate 1a is damaged by freezing, the plate 1a is damaged first. Therefore, even if damage occurs, mixing of the first fluid and the second fluid can be prevented.

In this way, by providing the continuously enlarged surface 30, the location of the freeze damage is set in the inner fin 4, and by using a double plate as the heat transfer plate at the location of the freeze damage, the first fluid and the second fluid are mixed. can be prevented. However, since the number of side surfaces 24 is reduced by providing the continuous enlarged surface 30, the contact area between the inner fins 4 and the first fluid is reduced, and there is a possibility that the heat transfer property of the entire first flow path 6 is reduced. .

Therefore, by providing the second opening portion 30a larger than the first opening portion 26 in the continuous enlarged surface 30, the deterioration of heat transferability is suppressed. As shown in FIG. 29, the length _L1 of the second opening 30a in the second direction is greater than the length L of the first opening 26 in the second direction, and the length L of the second opening 30a in the first direction is _D1 is greater than the length D of the first opening 26 in the first direction.

By providing the second openings 30 a in the continuously enlarged surface 30 in this manner, the first fluid directly contacts the second heat transfer plate 2 without passing through the inner fins 4 at the second openings 30 a. Therefore, deterioration of heat transfer performance can be suppressed. In addition, by providing the second opening 30a, the heat transfer area can be increased by the inner wall surface of the second opening 30a, and from this point, the deterioration of the heat transfer performance can be suppressed.

Here, an example in which the second opening 30a is provided in the continuous enlarged surface 30 larger than the enlarged contact surface is shown, but a configuration in which the second opening 30a is provided in the enlarged contact surface is also possible.

In addition, the provision of the continuous enlarged surface 30 reduces the number of side surfaces 24, which may cause drift. Therefore, although not shown here, the protrusions 27a and 27b of the second to fourth embodiments may be applied to the inner fin 4. FIG. Thereby, the drift in the first flow path 6 can be suppressed.

According to the sixth embodiment, effects similar to those of the first to fifth embodiments can be obtained. In the sixth embodiment, the inner fins are offset fins, and the wavy portions formed by alternately connecting the side surfaces 24 and the contact surfaces 25 in the second direction are shifted by half a wave to form the first fins. It has a configuration in which a plurality of them are arranged side by side in a direction and are alternately formed. The contact surface 25 has a first contact surface 25a joined to one of the two heat transfer plates facing each other across the inner fin, and a second contact surface 25b joined to the other. The inner fin has a shape in which a portion with an enlarged width of the second contact surface 25b is provided periodically in the first direction. , a second opening 30a larger than the first opening 26 is provided. The other heat transfer plate that contacts the second contact surface 25b is a double plate having two plates.

In this way, the portion where the width of the second contact surface 25b is expanded becomes the location of freezing damage, and by using the double plate for the portion serving as the location of freezing damage, even if damage occurs to the heat transfer plate due to freezing, the first fluid and the second fluid can be prevented from being mixed. Therefore, a highly reliable plate heat exchanger can be realized. In addition, by providing the second opening 30a larger than the first opening 26 in the enlarged contact surface, the heat transfer area can be increased, and the deterioration in heat transfer performance caused by the provision of the enlarged contact surface can be prevented. can be suppressed.

In the sixth embodiment, a continuous enlarged surface 30 is formed by combining the enlarged surface with the second contact surface 25b in one wave portion continuous on both sides of the enlarged contact surface in the first direction. In the continuous enlarged surface 30, the length _D1 in the first direction is greater than or equal to the length D of the first opening in the first direction, and the length _L1 in the second direction is the length of the first opening in the second direction. A second opening having a length L or greater is provided.

As a result, the heat transfer area can be increased, and the deterioration of the heat transfer performance can be further suppressed.

Although the inner fin 4 has been described here, the inner fin 5 may be configured as described above, or both the inner fin 4 and the inner fin 5 may be configured as described above.

Embodiment 7.
Hereinafter, the seventh embodiment will be described, but descriptions of the same parts as those in the first to sixth embodiments will be omitted, and the same reference numerals will be given to the same or corresponding parts.

Embodiment 7 describes a heat pump device equipped with the plate heat exchanger 100 described in Embodiments 1 to 6. FIG. Here, a heat pump heating system using a plate heat exchanger as a condenser will be described as one form of utilization of the heat pump device.

FIG. 32 is a schematic diagram showing the configuration of a heat pump heating system including the plate heat exchanger 100 according to the seventh embodiment.
The heat pump heating system 300 has a heat pump device 400 with a main refrigerant circuit 35 and a heat medium circuit 40 . The main refrigerant circuit 35 is a circuit in which the compressor 31, the second flow path of the heat exchanger 32, the expansion valve 33, and the heat exchanger 34 are sequentially connected, and the refrigerant circulates. The heat medium circuit 40 is a circuit in which the first flow path of the heat exchanger 32, the heat medium utilization device 42, and the pump 41 are connected in order, and the heat medium circulates. Compressor 31 , heat exchanger 32 , expansion valve 33 , and heat exchanger 34 are housed in a housing of heat pump device 400 .

Here, the heat exchanger 32 is the plate heat exchanger described in the above embodiments, and performs heat exchange between the refrigerant flowing through the main refrigerant circuit and the heat medium flowing through the heat medium circuit. A heat medium used in the heat medium circuit 40 is, for example, water or brine. The refrigerant flowing through the main refrigerant circuit 35 is not particularly limited, and for example, the refrigerants described above can be used.

When a combustible refrigerant or the like is used as the refrigerant flowing through the main refrigerant circuit 35 , the double wall plate heat exchanger of the fifth embodiment is used as the heat exchanger 32 . Then, a leak detection sensor 36 for detecting leakage of the first fluid or the second fluid to the outside is installed in the heat pump device 400, and when leakage is detected, it is notified to the outside by sounding a buzzer, etc., thereby improving reliability. A high heat pump type heating system can be realized.

The heat medium utilization device 42 is composed of an indoor heat exchanger of an air conditioner (not shown) that air-conditions the room. The heat medium utilization device 42 heats the room by exchanging heat between the heat medium of the heat medium circuit 70 led into the room and the indoor air.

Since the heat pump heating system of Embodiment 7 includes the plate heat exchangers of Embodiments 1 to 6, the heat exchange efficiency is good, power consumption is suppressed, and CO ₂ emissions can be reduced. A heat pump heating system can be realized.

Here, a heat pump heating system in which heat is exchanged between a refrigerant and a heat medium using a plate heat exchanger has been described, but the present invention is not limited to this. Plate heat exchangers are used in many industrial and household equipment such as heat pump hot water supply systems, heat pump cooling systems using plate heat exchangers as evaporators, chillers for cooling, power generators, and heat sterilization equipment for food. It can be used for equipment, etc.

As an application example of the present disclosure, it can be used in a heat pump device that is easy to manufacture, can improve heat exchange performance, and needs to reduce power consumption.

REFERENCE SIGNS LIST 1 first heat transfer plate 1a plate 1b plate 2 second heat transfer plate 2a plate 2b plate 3 first reinforcing side plate 4 inner fin 5 inner fin 6 first flow path 7 second 2 flow path, 8 second outflow pipe, 9 first inflow pipe, 10 first outflow pipe, 11 second inflow pipe, 12 second reinforcing side plate, 13 first inflow hole, 14 first outflow hole, 15 second 2 inflow hole 16 second outflow hole 17 first inflow hole 18 first outflow hole 19 second inflow hole 20 second outflow hole 21 header portion 22 flat portion 23 outer wall portion 24 side surface 25 contact surface 25a first contact surface 25b second contact surface 26 first opening 27a protrusion 27b protrusion 28 tip 29 black painted portion 30 continuously enlarged surface 30a second opening 31 Compressor 32 Heat Exchanger 33 Expansion Valve 34 Heat Exchanger 35 Main Refrigerant Circuit 36 Detection Sensor 40 Heat Medium Circuit 41 Pump 42 Heat Medium Utilizing Device 70 Heat Medium Circuit 100 Plate Heat Exchanger 200 heat transfer set 300 heat pump heating system 400 heat pump device.

Claims (13)

A plate heat exchanger in which a flow path is formed by each space between a plurality of stacked heat transfer plates, and inner fins are arranged in the flow path,
A first direction is a flow direction of the fluid in the flow channel, a second direction is a direction perpendicular to the first direction, and a stacking direction of the heat transfer plates is a direction perpendicular to the first direction and the second direction. Assuming the third direction,
The inner fin has a side surface extending in the third direction and a contact surface joined to the heat transfer plate, and the width W of the contact surface in the second direction is the height of the side surface in the third direction. The contact surface is provided with a first opening having a length L in the second direction equal to or greater than the height H of the side surface in the third direction ,
A plate-type heat exchanger , wherein protrusions protruding parallel to the side surfaces are formed at both ends of the first opening in the second direction. The first opening is provided at the center of the contact surface in the second direction, and the width W of the contact surface is in the range of 2 to 5 times the height H of the side surface, 2. The plate heat exchanger according to claim 1, wherein the length L of said first opening in said second direction satisfies H≦WL≦3H. The contact surface has a rectangular shape elongated in the second direction, and the first opening has a slit shape in which the length L is greater than the length D of the first opening in the first direction. A plate heat exchanger according to claim 1 or claim 2. 4. The heat transfer plate according to any one of claims 1 to 3, wherein the height of the two protrusions is the same, and the tip of each of the two protrusions is in contact with the heat transfer plate facing the tip. A plate heat exchanger according to any one of the preceding paragraphs . The plate heat exchanger according to any one of claims 1 to 3, wherein the heights of the two protrusions are different from each other. 6. The plate heat exchanger according to claim 5 , wherein one tip of said two protrusions is in contact with said heat transfer plate. 6. The plate heat exchanger according to claim 5 , wherein the tips of both of the two protrusions are not in contact with the heat transfer plate. The plate heat exchanger according to any one of claims 1 to 7, wherein at least some of the plurality of heat transfer plates are double plates in which two plates are joined. The inner fins are offset fins, and the side surfaces and the contact surfaces are alternately connected in the second direction, and the wavy portions are alternately arranged in the first direction with a half-wave shift. having a configuration formed in
The contact surface has a first contact surface that contacts one of the two heat transfer plates that face each other with the inner fin interposed therebetween, and a second contact surface that contacts the other,
The inner fin has a shape in which a portion with an enlarged width of the second contact surface is provided periodically in the first direction, and the enlarged contact surface is a portion with an enlarged width of the second contact surface. is provided with a second opening larger than the first opening,
The plate heat exchanger according to any one of claims 3 to 7 , wherein the other heat transfer plate that contacts the second contact surface is composed of a double plate having two plates. A continuously enlarged surface is formed by combining the second contact surface of one of the waveform portions continuous on both sides of the enlarged contact surface in the first direction and the enlarged contact surface, and On the surface, the length _D1 in the first direction is equal to or greater than the length D of the first opening in the first direction, and the length L1 in the second direction is the length _L1 in the second direction of the first opening. 10. The plate heat exchanger according to claim 9 , wherein the second opening is provided with a length L or more in the direction. 1 to 4, wherein the first opening has one shape or a combination of a plurality of shapes of a quadrangle, a circle, a triangle, a polygon, a D shape, and an arrow shape when viewed from the third direction. 11. A plate heat exchanger according to any one of claims 10 to 14. A heat pump comprising a main refrigerant circuit in which a compressor, a plate heat exchanger according to any one of claims 1 to 11 , an expansion valve, and a heat exchanger are sequentially connected, and in which a refrigerant circulates. Device. 13. A heat pump heating system comprising a heat medium circuit in which the heat pump device according to claim 12 , the plate heat exchanger, the heat medium utilization device, and the pump are sequentially connected, and a heat medium circulates.

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