JP6947314B2 - Plate heat exchanger and heat pump device - Google Patents

Description

The present invention relates to a plate heat exchanger that exchanges heat between a first fluid and a second fluid, and a heat pump device including the plate heat exchanger.

The plate heat exchanger is a heat exchanger configured by stacking a plurality of substantially rectangular heat transfer plates, forming a flow path between adjacent heat transfer plates, and connecting the first fluid to the flow path. Heat exchange is performed between the first fluid and the second fluid by alternately flowing the second fluid in the stacking direction. In this plate type heat exchanger, in the prior art, the temperature of the second fluid circulating in the refrigeration cycle is measured by a temperature sensor provided on the side surface of the heat transfer plate (see, for example, Patent Document 1).

Japanese Unexamined Patent Publication No. 2013-124836

However, the above-mentioned plate heat exchanger has a configuration in which the contact area of the first fluid and the contact area of the second fluid are substantially the same on the side surface of the plate heat exchanger. Therefore, even if the temperature sensor is provided at a position on the side surface facing the second fluid, there is a problem that the temperature sensor is easily affected by the temperature of the first fluid and the detection accuracy of the second fluid is deteriorated.

The present invention has been made to solve the above-mentioned problems, and to obtain a plate heat exchanger and a heat pump device capable of improving the temperature detection accuracy of the second fluid in the plate heat exchanger. The purpose.

The plate-type heat exchanger according to the present invention alternately has a heat transfer plate having a rectangular plate-shaped main plate portion and a wall portion protruding from the edge of the main plate portion to one side of the plate-shaped surface. A plurality of layers are laminated by reversing 180 degrees with respect to an axis extending vertically from the center of the plate-like surface of the portion, and a first flow path through which the first fluid flows and a second flow path through which the second fluid flows between the heat transfer plates. In a plate-type heat exchanger in which , The main plate portion is formed intermittently or continuously along one long side of the main plate portion, and abuts on the wall portion of the heat transfer plate facing the side on which the convex portion protrudes. Is provided with a long portion so as to be in contact with the other long side, and with the long portion of the heat transfer plate as a reference, the transfer facing the side next to the side where the wall portion protrudes from the long portion. The distance of the heat plate to the convex portion is configured to be smaller than the distance from the long portion to the convex portion of the heat transfer plate facing the side on which the convex portion protrudes. ..

The plate-type heat exchanger according to the present invention alternately has a heat transfer plate having a rectangular plate-shaped main plate portion and a wall portion protruding from the edge of the main plate portion to one side of the plate-shaped surface. A plurality of layers are laminated by reversing 180 degrees with respect to an axis extending vertically from the center of the plate-like surface of the portion, and a first flow path through which the first fluid flows and a second flow path through which the second fluid flows between the heat transfer plates. In a plate-type heat exchanger in which the above-mentioned heat transfer plates are alternately formed in the stacking direction, the four sides formed by the plurality of wall portions at positions corresponding to the four sides of the main plate portion by laminating the plurality of heat transfer plates. The side portion of at least one of the four side portions is configured such that the contact area of the second fluid is larger than the contact area of the first fluid.

Further, the heat pump device according to the present invention alternately has a heat transfer plate having a rectangular plate-shaped main plate portion and a wall portion protruding from the edge of the main plate portion to one side of the plate-shaped surface. A plurality of layers are laminated by reversing 180 degrees with respect to an axis extending vertically from the center of the plate-like surface of the heat transfer plate, and a first flow path through which the first fluid flows and a second flow path through which the second fluid flows are formed between the heat transfer plates. In a plate-type heat exchanger formed alternately in the stacking direction, the main plate portion is provided with a convex portion protruding from a plate-shaped surface opposite to the surface on which the wall portion protrudes, and the convex portion is provided with a convex portion. The main plate portion is formed intermittently or continuously along one long side of the main plate portion, and abuts on the wall portion of the heat transfer plate facing the side on which the convex portion protrudes, and the main plate portion is formed. A long portion is provided so as to be in contact with the other long side, and the heat transfer is opposed to the side where the wall portion protrudes from the long portion with reference to the long portion of the heat transfer plate. The distance of the plate to the convex portion is configured to be smaller than the distance from the long portion to the convex portion of the heat transfer plate facing the side where the convex portion protrudes, and is formed on the wall portion. A temperature detecting means installation portion for installing a temperature detecting means for detecting the temperature of the second fluid is provided in a portion facing the second fluid, and a compressor for compressing the second fluid, air, and the above. The second fluid, which includes an air heat exchanger that exchanges heat with the second fluid, an expansion valve that lowers the pressure of the second fluid, and a pressure container that holds the surplus second fluid, circulates. It includes a second fluid circuit and a temperature detecting means installed in the temperature detecting means installation portion.

The plate heat exchanger of the present invention can improve the detection accuracy when detecting the temperature of the second fluid from the side surface of the plate heat exchanger.
Further, the plate heat exchanger of the present invention can improve the detection accuracy when detecting the temperature of the second fluid from the side portion of the plate heat exchanger.
In the heat pump device of the present invention, the temperature detection accuracy of the second fluid can be improved by installing the temperature detection means in the temperature detection means installation portion.

It is a refrigerant circuit diagram which shows Embodiment 1 of this invention. It is an outline drawing of the housing of the outdoor unit which shows Embodiment 1 of this invention. It is the schematic inside the housing of the outdoor unit which shows Embodiment 1 of this invention. It is an exploded perspective view of the plate type heat exchanger used in Embodiment 1 of this invention. It is a perspective view of the plate type heat exchanger used in Embodiment 1 of this invention. It is a front view of the heat transfer plate used in Embodiment 1 of this invention. It is an enlarged view of the heat transfer plate used in Embodiment 1 of this invention. It is sectional drawing of the heat transfer plate used in Embodiment 1 of this invention. It is sectional drawing of the plate type heat exchanger used in Embodiment 1 of this invention. It is sectional drawing of the plate type heat exchanger used in Embodiment 1 of this invention. It is a front view of the heat transfer plate used in Embodiment 2 of this invention. It is an enlarged view of the heat transfer plate used in Embodiment 2 of this invention. It is sectional drawing of the heat transfer plate used in Embodiment 2 of this invention. It is sectional drawing of the plate type heat exchanger used in Embodiment 2 of this invention. It is sectional drawing of the plate type heat exchanger used in Embodiment 2 of this invention. It is sectional drawing of the plate type heat exchanger used in Embodiment 2 of this invention. It is sectional drawing of the plate type heat exchanger used in Embodiment 2 of this invention. It is a front view of the heat transfer plate used in Embodiment 3 of this invention. It is sectional drawing of the heat transfer plate used in Embodiment 3 of this invention. It is sectional drawing of the plate type heat exchanger used in Embodiment 3 of this invention. It is sectional drawing of the plate type heat exchanger used in Embodiment 3 of this invention. It is sectional drawing of the plate type heat exchanger used in Embodiment 4 of this invention. It is sectional drawing of the plate type heat exchanger used in Embodiment 5 of this invention. It is sectional drawing of the plate type heat exchanger used in Embodiment 5 of this invention. It is sectional drawing of the plate type heat exchanger used in Embodiment 6 of this invention.

Embodiment 1.
The heat pump device provided with the plate heat exchanger of the present invention will be described with reference to FIGS. 1 to 10. FIG. 1 is a refrigerant circuit diagram, FIG. 2 is an external view of the housing 20 of the outdoor unit 1, and FIG. 3 is a schematic view of the inside of the housing 20 of the outdoor unit 1 as viewed from above.
In the present embodiment, the lateral direction of the rectangular main plate portion 70a, which will be described later, is defined as the “minor direction”, and the longitudinal direction of the main plate portion 70a is defined as the “longitudinal direction”.

As shown in FIG. 1, the outdoor unit 1 as a heat pump device includes a refrigerant circuit 2a as a second fluid circuit. The refrigerant circuit 2a includes a plate heat exchanger 3, a compressor 4 having a muffler 4a, a four-way valve 5, an air heat exchanger 6, a pressure vessel 7, an electronic expansion valve 8a, an electronic expansion valve 8b, and a refrigerant pipe connecting them. It is composed of 10.
The plate heat exchanger 3 is a heat exchanger configured by stacking a plurality of substantially rectangular heat transfer plates, forming a flow path between adjacent heat transfer plates, and connecting the first fluid to the flow path. Heat exchange is performed between the first fluid and the second fluid by alternately flowing the second fluid in the stacking direction. In the present embodiment, the water W that transfers heat energy to the outside of the outdoor unit 1 will be described as the first fluid, and the refrigerant R that circulates in the refrigerant circuit 2a will be described as the second fluid.
In this embodiment, water is used as the first fluid, but a liquid heat medium may be used. Examples of the liquid heat medium include an aqueous solution of calcium oxide, an aqueous solution of ethylene glycol, and alcohol. Further, although R32 is used as the refrigerant R as the second fluid, a refrigerant such as R410A, CO2, or HC may be used.

The plate heat exchanger 3 includes a water pipe connection port 3a, a water pipe connection port 3b, a refrigerant pipe connection port 3c, and a refrigerant pipe connection port 3d. The water pipe connection port 3a and the water pipe connection port 3b are connected to a water circuit 2b (first fluid circuit) in which water W circulates. A device (not shown) that uses water for a radiator such as a water heater, a radiator, a floor heater, a panel heater, and a falcon vector is connected to the water circuit 2b.
The compressor 4 compresses the refrigerant R, and the four-way valve 5 switches the flow of the refrigerant R. The air heat exchanger 6 exchanges heat between the air and the refrigerant R, and the pressure vessel 7 stores the refrigerant R. The electronic expansion valve 8a and the electronic expansion valve 8b are used as a pressure reducing device for reducing the pressure of the refrigerant R.

The four-way valve 5 is configured so that the flow path of the refrigerant can be switched between the heating mode and the cooling mode.
When the refrigerant circuit 2a is set to the heating mode, the refrigerant R that has become high temperature and high pressure in the compressor 4 is subjected to the plate heat exchanger 3 (from the refrigerant pipe connection port 3c to the refrigerant pipe connection port 3d) and electrons. A closed circuit is configured so as to circulate in the order of the expansion valve 8b, the pressure vessel 7, the electronic expansion valve 8a, the air heat exchanger 6, the muffler 4a, and the compressor 4.
On the other hand, when the refrigerant circuit 2a is set to the cooling mode, the refrigerant R that has become high temperature and high pressure in the compressor 4 is used in the air heat exchanger 6, the electronic expansion valve 8a, the pressure vessel 7, and the electronic expansion valve 8b. , The plate heat exchanger 3 (refrigerant pipe connection port 3d to refrigerant pipe connection port 3c), the muffler 4a, and the compressor 4 are configured to circulate in this order.

Temperature sensors 11, 12, 13, and 14 are attached to the side surfaces of the refrigerant pipe 10 and the plate heat exchanger 3, respectively, and detect the temperature of the refrigerant R flowing through the refrigerant circuit 2a, respectively. In addition to the refrigerant circuit 2a, the outdoor unit 1 includes a control device 15, a storage device 16, and an arithmetic unit 17 for controlling the operation of each part.
The temperature sensor 11 is for detecting the temperature of the refrigerant pipe 10 on the outlet side of the compressor 4, and is fixed to the refrigerant pipe 10 on the outlet side of the compressor 4. The temperature sensor 12 is for detecting the temperature of the air heat exchanger 6, and is fixed to the refrigerant pipe 10 in the vicinity of the air heat exchanger 6. The temperature sensor 13 is for detecting the temperature of the refrigerant pipe 10 connecting the plate heat exchanger 3 and the electronic expansion valve 8b, and is fixed to the refrigerant pipe 10. The temperature sensor 14 is for detecting the temperature of the refrigerant R flowing in the plate heat exchanger 3, and is fixed to the side surface of the plate heat exchanger 3.

The temperature sensors 11, 12, 13, and 14 are connected so that the detected values can be transmitted to the control device 15. The control device 15 is connected so that the switching operation of the four-way valve 5 and the opening degrees of the electronic expansion valves 8a and 8b can be adjusted.
The control device 15 is composed of, for example, a microcomputer, reads temperature data detected by the temperature sensors 11, 12, 13, and 14, and stores the temperature data in the storage device 16. The calculation device 17 reads the temperature data of the temperature sensor 14 from the storage device 16, calculates the pressure saturation temperature of the refrigerant R based on the temperature data, and stores the calculated pressure saturation temperature of the refrigerant R as the pressure saturation temperature data. Store in device 16. Further, the control device 15 reads the temperature data and the pressure saturation temperature data from the storage device 16 and controls the electronic expansion valves 8a and 8b based on the temperature and the pressure.

As shown in FIG. 2, the housing 20 of the outdoor unit 1 includes a grill 20a from which air is blown out. As shown in FIG. 3, the outdoor unit 1 has a blower room 21 and a machine room 22, and the blower room 21 and the machine room 22 are separated by a separator 23. Although not shown, the outdoor unit 1 is provided with an electric component box for storing electric parts on the machine room 22.
An air heat exchanger 6, a fan 24, and the like are arranged in the blower chamber 21, and the outside air is blown to the air heat exchanger 6 by the operation of the fan 24.

Further, in the machine room 22, a compressor 4, a pressure vessel 7, a four-way valve 5 (not shown in FIG. 3), a plate heat exchanger 3, electronic expansion valves 8a, 8b (not shown in FIG. 3) and the like are arranged. Has been done.

Next, the configuration of the plate heat exchanger 3 will be described with reference to FIGS. 4 to 10.
FIG. 4 is an exploded perspective view of the plate heat exchanger 3, FIG. 5 is a perspective view of the plate heat exchanger 3, and FIG. 6 is a front view of the heat transfer plates 40 and 41. FIG. 7 is an enlarged view of the heat transfer plates 40 and 41. FIG. 8A is a cross-sectional view of the heat transfer plates 40 and 41 viewed from the positions AA in FIG. 6, and FIG. 8B is a cross-sectional view of the heat transfer plates 40 and 41 taken from FIG. 6BB. It is a cross-sectional view seen from the position, (c) is a cross-sectional view of the heat transfer plates 40 and 41 seen from the position CC of FIG. 6, and (d) is a cross-sectional view of the heat transfer plates 40 and 41. It is sectional drawing seen from the position of DD of 6. FIG. 9 is a cross-sectional view of the plate heat exchanger 3 viewed from the position BB of FIG. 6, and FIG. 10 is a cross-sectional view of the plate heat exchanger 3 viewed from the position CC of FIG. It is a figure.

As shown in FIG. 4, the plate heat exchanger 3 includes heat transfer plates 40 and 41, outer plates 42 and 43, and reinforcing plates 44 and 45. In the plate heat exchanger 3, from the front side to the back side, the reinforcing plate 44, the outer plate 42, the heat transfer plates 40, 41, 40, 41, 40, 41, 40, 41, 40, the outer plate 43, The reinforcing plates 45 are laminated in this order.
In the present embodiment, as shown in FIGS. 4 and 5, the side of the plate heat exchanger 3 where the reinforcing plate 44 is provided is the front side, and the side where the reinforcing plate 45 is provided is the back side. It is defined.

As shown in FIG. 4, the reinforcing plate 44 is formed in a substantially rectangular plate shape, and the water pipe connection port 1a, the water pipe connection port 1b, the refrigerant pipe connection port 1c, and the refrigerant pipe connection port 1d are provided at the four corners of the substantially rectangular shape. It is formed.
The outer plate 42 is for sealing the leakage of the refrigerant R and the water W, is formed in a substantially rectangular plate shape like the reinforcing plate 44, and has the first opening 46 and the second opening 47 at the four corners. , The third opening 48 and the fourth opening 49 are formed. The outer plate 43 is formed in a substantially rectangular plate shape like the outer plate 42 and the like. The outer plate 43 is not provided with the first opening 46, the second opening 47, the third opening 48, and the fourth opening 49 like the outer plate 42.

In the plate heat exchanger 3, substantially rectangular heat transfer plates 40 and 41 are alternately laminated, and the refrigerant R and water W are alternately circulated between the heat transfer plates 40 and 41 to exchange heat. be. In FIGS. 4 to 10, for convenience of explanation, five heat transfer plates 40 and four heat transfer plates 41 are described. Further, the heat transfer plate 40 and the heat transfer plate 41 have the same shape and are rotated 180 degrees with respect to the axis Z extending vertically from the center of the plate-shaped surfaces of the main plate portions 70a and 70b.

Each heat transfer plate 40 is formed in a substantially rectangular plate shape, and a first opening 50, a second opening 51, a third opening 52, and a fourth opening 53 are formed at four corners. Each heat transfer plate 41 is formed in a substantially rectangular plate shape, and a first opening 54, a second opening 55, a third opening 56, and a fourth opening 57 are formed at four corners. Further, a plurality of convex portions 61 and 62 are formed on the heat transfer plates 40 and 41, respectively. The convex portions 61 and 62 are formed in a substantially V shape when viewed from the front surface side. Here, the plate-type heat exchanger 3 has a configuration in which the heat transfer plate 40 and the heat transfer plate 41 are laminated by rotating the heat transfer plate 40 and the heat transfer plate 41 by 180 degrees with reference to the axis Z extending vertically from the center of the plate-like surfaces of the main plate portions 70a and 70b. Therefore, in the laminated state, the convex portion 61 formed on the heat transfer plate 40 and the convex portion 62 formed on the heat transfer plate 41 are configured so that the directions in a substantially V shape are opposite to each other. There is.
In this way, by forming the substantially V-shaped convex portions 61 and 62 having different directions so as to overlap each other, a flow path that causes a complicated flow is formed between the heat transfer plate 40 and the heat transfer plate 41.

In the plate type heat exchanger 3, the water pipe connection port 1a, the first opening 46, the first opening 50, and the first opening 54 overlap in the stacking direction, and the water pipe connection port 1b, the second opening 47, The second opening 51 and the second opening 55 overlap in the stacking direction, and the refrigerant pipe connection port 1c, the third opening 48, the third opening 52, and the third opening 56 overlap in the stacking direction, and the refrigerant pipe The connection port 1d, the fourth opening 49, the fourth opening 53, and the fourth opening 57 overlap in the stacking direction.
Then, the heat transfer plates 40, 41, the outer plates 42, 43, and the outer peripheral wall portions of the reinforcing plates 44, 45 are laminated so as to overlap each other, and are joined by brazing.

As a result, the first flow path 63 from which the water W flowing in from the water pipe connection port 1a flows out from the water pipe connection port 1b is formed between the back surface of the heat transfer plate 40 and the front surface of the heat transfer plate 41. Similarly, a second flow path 64 in which the refrigerant R flowing in from the refrigerant pipe connection port 1c flows out from the refrigerant pipe connection port 1d is formed between the back surface of the heat transfer plate 41 and the front surface of the heat transfer plate 40.

The water W that has flowed into the water pipe connection port 1a from the outside flows through the passage holes formed by the overlapping of the first openings 50 and 54 of the heat transfer plates 40 and 41, and flows into each of the first flow paths 63. It is configured in. The water W that has flowed into the first flow path 63 is configured to gradually spread in the lateral direction, flow in the longitudinal direction, and flow out from the second openings 51 and 55. The water W flowing out from the openings 51 and 55 flows through the passage hole formed by the overlapping of the openings 51 and 55, and is configured to flow out from the water pipe connection port 1b to the outside.
Similarly, the refrigerant R that has flowed into the refrigerant pipe connection port 1c from the outside flows through the passage holes formed by overlapping the third openings 52 and 56 of the heat transfer plates 40 and 41, and flows through the passage holes formed by overlapping the third openings 52 and 56 of the heat transfer plates 40 and 41. It is configured to flow into. The refrigerant R that has flowed into the second flow path 64 is configured to gradually spread in the lateral direction, flow in the longitudinal direction, and flow out from the fourth openings 53 and 57. The refrigerant R flowing out from the fourth openings 53 and 57 flows through the passage holes formed by the overlapping of the fourth openings 53 and 57, and is configured to flow out from the refrigerant pipe connection port 1d to the outside.

Next, the detailed configuration of the heat transfer plate 40 will be described.
As shown in FIGS. 6 and 8, the heat transfer plate 40 includes a main plate portion 70a having a substantially rectangular plate shape, wall portions 71a, 72a, 73a, 74a provided around the main plate portion 70a, and a plurality of wall portions 71a, 72a, 73a, 74a. The convex portion 61 is provided. The main plate portion 70a is formed with a first opening 50, a second opening 51, a third opening 52, a fourth opening 53, and a plurality of convex portions 61. The wall portions 71a, 72a, 73a, and 74a are formed so as to project from the edges of each side of the main plate portion 70a to one side of the plate-like surface. That is, the wall portions 71a, 72a, 73a, and 74a are formed so as to project from the peripheral edge of the main plate portion 70a to one side of the plate-shaped surface.
The wall portion in the present invention is formed so as to project toward the back surface side in the stacking direction.

The wall portions 71a and 72a are formed continuously on the long side of the main plate portion 70a, and the wall portion 71a and the wall portion 72a are formed so that the distance between the wall portions 71a and the wall portion 72a increases as the distance from the main plate portion 70a increases. That is, the wall portion 71a and the wall portion 72a are formed in a tapered shape.
The wall portions 73a and 74a are continuously formed on the short side of the main plate portion 70a, and the wall portion 73a and the wall portion 74a are formed so that the distance between the wall portion 73a and the wall portion 74a increases as the distance from the main plate portion 70a increases. That is, the wall portion 73a and the wall portion 74a are formed in a tapered shape.

A first opening 50, a second opening 51, a third opening 52, and a fourth opening 53 are formed at the four corners of the main plate portion 70a.
The first opening 50 is formed at the corner of the main plate 70a formed by the wall 71a and the wall 74a, and the second opening 51 is formed at the corner of the main plate 70a formed by the wall 71a and the wall 73a. The third opening 52 is formed at the corner of the main plate 70a formed by the wall 72a and the wall 73a, and the fourth opening 53 is formed at the corner of the main plate 70a formed by the wall 72a and the wall 74a. It is formed in.
The main plate portion 70a is formed with a high portion 75a in which the peripheral portion of the first opening 50 protrudes in the direction opposite to the direction in which the wall portions 71a, 72a, 73a, 74a protrude. The high portion 75a has a trapezoidal bulge when viewed from the front side.
Similarly, the main plate portion 70a is formed with a high portion 76a in which the peripheral portion of the second opening 51 protrudes in the direction opposite to the direction in which the wall portions 71a, 72a, 73a, 74a protrude. The high portion 76a has a trapezoidal bulge when viewed from the front side.

As shown in FIG. 8, the protruding length L1 of the wall portion 71a from the main plate portion 70a is formed to be longer than the protruding length L2 of the wall portion 72a from the main plate portion 70a. In the present embodiment, the protrusion length L1 is 6 mm and the protrusion length L2 is 4.7 mm.
By making the wall portion 71a longer than the wall portion 72a in this way, the tip of the wall portion 71a of the heat transfer plate 40 is shown in FIG. 9 in the laminated state of the heat transfer plate 40 and the heat transfer plate 41. E1 is configured so that the tip E2 of the wall portion 72b (the wall portion 72b will be described later) of the heat transfer plate 41 located on the back surface of the heat transfer plate 40 is aligned. As described above, since the tip E1 of the wall portion 71a and the tip E2 of the wall portion 72b are aligned with each other, the wall portion H1 has a double structure and the strength of the side surface of the plate heat exchanger 3 is increased. be able to. The side portion H1 referred to here is composed of a plurality of wall portions 71a and a plurality of wall portions 72b. Further, since the tip E3 of the wall portion 71b and the tip E4 of the wall portion 72a are configured to be aligned with each other, the wall portion H2 also has a double structure to increase the strength of the side surface of the plate heat exchanger 3. Can be enhanced. The side portion H2 is composed of a plurality of wall portions 71b and a plurality of wall portions 72a. The side portion H1 is also a part of the side surface of the plate heat exchanger 3, and similarly, the side portion H2 is also a part of the side surface of the plate heat exchanger 3.

In the present embodiment, the tip E1 of the wall portion 71a and the tip E2 of the wall portion 72b are aligned with each other, but the protruding length of the wall portion 71a is increased to form a double structure of the wall portion. If possible, the same effect as described above can be obtained, and it is not necessary to configure the tips E1 and E2 to be aligned with each other. The tip E1 of the wall portion 71a may be formed at least up to the position of the front surface portion of the wall portion 72b. According to such a configuration, the side surface of the second flow path 64 can be doubly covered by the wall portion 71a and the wall portion 72b on the back side thereof, and the strength of the side surface of the second flow path 64 can be increased. When the tip E1 of the wall portion 71a is formed up to the position of the tip E2 of the wall portion 72b, the side surface of the first flow path 63 is the wall portion 71a, the wall portion 72b on the back side thereof, and the wall portion on the back side thereof. It can be triple-covered with 71a, and the strength of the side surface of the first flow path 63 can be increased. The relationship between the tip E3 and the tip E4 may be changed in the same manner.
Main plate portion 70a, wall portions 71a, 72a, 73a, 74a, first opening 50, second opening 51, third opening 52, fourth opening 53, a plurality of convex portions 61, and high portions 75a, 76a. Is formed by pressing a plate material.

As shown in FIG. 6, convex portions 61 are formed in the main plate portion 70a except for the high portions 75a and 76a in a state where the convex portions 61 are arranged along the longitudinal direction of the main plate portion 70a (hereinafter, simply referred to as the longitudinal direction). Has been done. The convex portion 61 is a V-shaped protrusion when viewed from the front side, and is formed so that the valley portion in the middle of the V-shape faces the wall portion 73a and both ends of the V-shape face the wall portion 74a. ing. That is, the convex portion 61 is formed so that the valley portion in the middle of the V-shape faces one end in the longitudinal direction of the main plate portion 70a, and both ends of the V-shape face the other end in the longitudinal direction of the main plate portion 70a. ..
The protruding height of the convex portion 61 from the main plate portion 70a is formed so as to be the same as the protruding height of the high portions 75a and 76a from the main plate portion 70a. The height of the convex portion 61 protruding from the main plate portion 70a may be made smaller than the height of the high portions 75a and 76a protruding from the main plate portion 70a.

That is, one end of both ends of the V-shape of the protrusion 61 is close to the wall portion 72a, and the other end is formed at a position at a predetermined distance from the long side of the wall portion 71a. With such a configuration, the distance from the one end to the wall portion 72a is smaller than the distance from the other end to the wall portion 71a.
Each convex portion 61 is formed from the long side of the main plate portion 70a on the wall portion 72a side to a position at a predetermined distance from the long side of the wall portion 71a.
The long side on the wall portion 72a side corresponds to one long side according to the claim of the present application, and the long side on the wall portion 71a side corresponds to the other long side according to the claim of the present application.

Since the plurality of convex portions 61 are formed from the long side of the main plate portion 70a on the wall portion 71a side to a position at a predetermined interval, the main plate portion 70a is formed on the wall portion 71a side of the plurality of convex portions 61. A long portion Fa that does not have a protruding shape is formed. That is, the wall of the main plate portion 70a is formed by arranging a plurality of convex portions 61 formed at predetermined intervals from the long side of the main plate portion 70a on the wall portion 71a side along the longitudinal direction of the main plate portion 70a. On the long side of the portion 71a side, a long portion Fa which is a part of the main plate portion 70a and a region in which the convex portion 61 is not formed is formed. The constituent requirements of the main plate portion 70a do not include the convex portion 61.

That is, the convex portion 61 is formed intermittently along the long side of the main plate portion 70a on the wall portion 72a side as shown by being surrounded by the alternate long and short dash line in FIG. 7, and the long portion Fa is formed. As shown by being surrounded by the alternate long and short dash line on the left side of FIG. 7, it is formed so as to be in contact with the long side of the main plate portion 70a on the wall portion 71a side.

In the present embodiment, the length of the long portion Fa in the lateral direction is 1.75 mm, and the length of the main plate portion 70a in the lateral direction is 93 mm. The ratio of the length in the lateral direction of the long portion Fa to the length in the lateral direction of the main plate portion 70a is preferably "1.2: 100 to 4: 100", and in the present embodiment, it is "2: 100". .. By setting the ratio of the length of the long portion Fa in the lateral direction to the length of the main plate portion 70a in the lateral direction to be "1.2: 100 to 4: 100", the long portion Fa and the convex portion 62 on the back surface side thereof. It is possible to suitably maintain the contact state with the main plate portion 70a, and to minimize the area forming the long portion Fa on the main plate portion 70a. Further, by setting the ratio of the length of the long portion Fa in the lateral direction to the length of the main plate portion 70a in the lateral direction to be "2: 100", the long portion Fa and the convex portion 62 on the back side thereof come into contact with each other. The state can be maintained more favorably, and the area forming the long portion Fa on the main plate portion 70a can be reduced as much as possible.

Next, the detailed configuration of the heat transfer plate 41 will be described.
As shown in FIGS. 6 and 8, the heat transfer plate 41 has the same shape as the heat transfer plate 40, and the reference numerals shown in parentheses correspond to the configurations of each part of the heat transfer plate 41.
That is, the first opening 54, the second opening 55, the third opening 56, the fourth opening 57, the convex portion 62, the main plate portion 70b, the wall portions 71b, 72b, 73b, 74b, and the height of the heat transfer plate 41. Each of the portions 75b and 76b and the long portion Fb has a first opening 50, a second opening 51, a third opening 52, a fourth opening 53, a convex portion 61, and a main plate portion 70a in the heat transfer plate 40. It corresponds to the wall portions 71a, 72a, 73a, 74a, the high portions 75a, 76a, and the long portion Fa, respectively. Therefore, the description of each part of the heat transfer plate 41 will be omitted. The constituent requirements of the main plate portion 70b do not include the convex portion 62.

Next, the contact state between the heat transfer plate 40 and the heat transfer plate 41 will be described.
The plate-type heat exchanger 3 has a configuration in which a heat transfer plate 40 and a heat transfer plate 41 are laminated by being rotated 180 degrees with respect to a shaft Z extending vertically from the center of the plate-like surfaces of the main plate portions 70a and 70b. Therefore, in the laminated state, the wall portion 71a and the wall portion 72b, the wall portion 72a and the wall portion 71b, the wall portion 73a and the wall portion 74b, and the wall portion 74a and the wall portion 73b overlap, respectively. It is configured as follows.

As shown in FIG. 9, the long portion Fa of the main plate portion 70a of the heat transfer plate 40 is configured to be separated from the main plate portion 70b of the heat transfer plate 41 located on the back surface side. This distant distance is shown as the distance K1 in FIG. Further, the long portion Fa of the main plate portion 70a of the heat transfer plate 40 is configured to be separated from the main plate portion 70b of the heat transfer plate 41 located on the front surface side. This distant distance is shown as the distance K2 in FIG. The plate heat exchanger 3 is configured such that the distance K1 and the distance K2 are substantially the same.

As shown in FIG. 9, the long portion Fb of the main plate portion 70b of the heat transfer plate 41 is configured to be separated from the main plate portion 70a of the heat transfer plate 40 located on the back surface side. This distant distance is shown as the distance K3 in FIG. Further, the long portion Fb of the main plate portion 70b of the heat transfer plate 41 is configured to be separated from the main plate portion 70a of the heat transfer plate 40 located on the front surface side. This distant distance is shown as the distance K4 in FIG. The plate heat exchanger 3 is configured such that the distance K3 and the distance K4 are substantially the same.

As shown in FIG. 10, the convex portion 61 of the heat transfer plate 40 is configured to abut the wall portion 71b and the long portion Fb of the heat transfer plate 41. Therefore, in the cross-sectional position of FIG. 10, only the water W comes into contact with the side portion H2 composed of the wall portions 71b and 72a without the refrigerant R coming into contact with the side portion H2. That is, the convex portion 61 of the heat transfer plate 40 is in contact with the wall portion 71b of the heat transfer plate 41 facing the convex portion 61 next to the projecting side. Further, the long portion Fb of the main plate portion 70b of the heat transfer plate 41 is in contact with the convex portion 61 of the heat transfer plate 40 located next to the side on which the wall portions 71b, 72b, 73b, 74b protrude.

On the other hand, the long portion Fb of the main plate portion 70b of the heat transfer plate 41 is configured to be separated from the convex portion 61 of the heat transfer plate 40 located on the front surface side.
That is, the distance from the long portion Fb to the convex portion 61 of the heat transfer plate 40 facing the wall portions 71b, 72b, 73b, 74b next to the protruding side is based on the long portion Fb of the heat transfer plate 41. The distance from the long portion Fb to the convex portion 61 of the heat transfer plate 40 facing the convex portion 62 next to the protruding side is smaller than the distance.

As shown in FIG. 10, the convex portion 62 of the heat transfer plate 41 is configured to abut the wall portion 71a and the long portion Fa of the heat transfer plate 40. Therefore, in the cross-sectional position of FIG. 10, only the refrigerant R comes into contact with the side portion H1 composed of the wall portions 71a and 72b without the water W coming into contact with the side portion H1. That is, the convex portion 62 of the heat transfer plate 41 is in contact with the wall portion 71a of the heat transfer plate 40 facing the convex portion 62 next to the projecting side. Further, the long portion Fa of the main plate portion 70a of the heat transfer plate 40 is in contact with the convex portion 62 of the heat transfer plate 41 located next to the side on which the wall portions 71a, 72a, 73a, 74a protrude.

On the other hand, the long portion Fa of the main plate portion 70a of the heat transfer plate 40 is configured to be separated from the convex portion 62 of the heat transfer plate 41 located on the front surface side.
That is, the distance from the long portion Fa to the convex portion 62 of the heat transfer plate 41 facing the wall portions 71a, 72a, 73a, 74a next to the protruding side is based on the long portion Fa of the heat transfer plate 40. The distance from the long portion Fa to the convex portion 62 of the heat transfer plate 41 facing the convex portion 61 next to the protruding side is smaller than the distance.
Since the heat transfer plate 41 is laminated by rotating the heat transfer plate 40 by 180 degrees with respect to the axis Z extending vertically from the center of the plate-like surfaces of the main plate portions 70a and 70b, the heat transfer plate 40 and the heat transfer plate 41 are laminated. And abut as described above.

In the cross-sectional position of FIG. 9, the convex portion 61 is not in contact with the main plate portion 70b of the heat transfer plate 41 located on the front surface side thereof, but is configured to be in contact with the main plate portion 70b depending on the cross-sectional position. Similarly, at the cross-sectional position of FIG. 9, the convex portion 62 is not in contact with the main plate portion 70a of the heat transfer plate 40 located on the front surface side thereof, but is configured to be in contact with the main plate portion 70a depending on the cross-sectional position. .. Although not shown, the high portions 75a and 76a are configured to abut against the main plate portion 70b of the heat transfer plate 41 located on the front surface side thereof, and the high portions 75b and 76b are located on the front surface side thereof. It is configured to come into contact with the main plate portion 70a of the heat transfer plate 40.

In the plate heat exchanger 3, the heat transfer plates 40 and the heat transfer plates 41 having the same shape are laminated in a state of being rotated 180 degrees with respect to the axis Z extending vertically from the center of the plate-like surfaces of the main plate portions 70a and 70b. Therefore, in the laminated state, the wall portion 71a and the wall portion 72b are in contact with each other, and the wall portion 72a and the wall portion 71b are in contact with each other.

As shown in FIG. 6, the temperature sensor 14 is provided at a position corresponding to the long portion Fa in the longitudinal direction, and is joined to the wall portion 71a of the heat transfer plate 40 by a wax. Further, the temperature sensor 14 is attached to the wall portion 71a where the area facing the refrigerant R is larger than the area facing the water W. As shown in FIG. 9, the width S1 to which the temperature sensor 14 can be joined to the wall portion 71a in the stacking direction is configured to be about twice the width S2 in the stacking direction of the second flow path 64 of the refrigerant R. ing. Therefore, since a temperature sensor having a width of one side having a length of width S1 can be attached to the wall portion 71a, a temperature sensor smaller than this temperature sensor (for example, a temperature having a width of one side having a length of width S2) can be attached. Temperature detection can be performed at a lower cost than when a sensor) is used.

In the present embodiment, the width S1 is set to 4 mm, but this may be set in the range of, for example, 3 mm to 7 mm. By making the protruding length of the wall portion 71a longer than that of the wall portion 72b in this way, a temperature sensor having a side width of 4 mm can be attached to the wall portion 71a, so that the temperature sensor is smaller than this temperature sensor. Temperature detection can be performed at a lower cost than when a temperature sensor is used.
In the present embodiment, the temperature sensor 14 is joined so as to correspond to the width S2, but it may be joined so as to straddle a plurality of wall portions 71a.
The temperature sensor 14 corresponds to the temperature detecting means according to the claim of the present application, and the wall portion 71a corresponds to the temperature detecting means installing portion according to the claim of the present application.

Next, the operation of the outdoor unit 1 configured in this way will be described.
When the water W is heated by the plate heat exchanger 3, as shown in FIG. 1, the refrigerant R is compressed by the compressor 4 to obtain a high-pressure and high-temperature gas refrigerant, and the plate-type heat is generated via the four-way valve 5. It is supplied to one of the refrigerant pipe connection ports 3c of the exchanger 3. In the plate heat exchanger 3, the refrigerant R and the water W become countercurrents, heat exchange is performed between the refrigerant R and the water W, and the water W is heated. The liquid refrigerant exiting the other refrigerant pipe connection port 3d of the plate heat exchanger 3 is supercooled (with a subcool) by the electronic expansion valve 8b and enters the pressure vessel 7. Further, the pressure is reduced by the electronic expansion valve 8a to become a two-phase refrigerant, which evaporates by the air heat exchanger 6 to become a low-pressure gas refrigerant, and returns from the suction muffler 4a to the compressor 4 via the four-way valve 5. The high-temperature water heated by the plate heat exchanger 3 is supplied to a hot water supply tank, a fan coil unit, etc. (not shown).

Further, when the water W is cooled by the plate heat exchanger 3, the four-way valve 5 is switched so that the flow of the refrigerant R is in the opposite direction to that of FIG. 1. The refrigerant R is compressed by the compressor 4 to obtain a high-pressure and high-temperature gas refrigerant, which is supplied to the air heat exchanger 6 via the four-way valve 5. The liquid refrigerant leaving the air heat exchanger 6 is supercooled by the electronic expansion valve 8a and enters the pressure vessel 7. Further, the pressure is reduced by the electronic expansion valve 8b to become a two-phase refrigerant, which is supplied to the refrigerant pipe connection port 3d and evaporates by the plate heat exchanger 3 to become a low-pressure gas refrigerant. In the plate heat exchanger 3, the refrigerant R and the water W become countercurrents, heat exchange is performed between the refrigerant R and the water W, and the water W is cooled. The low-pressure gas refrigerant discharged from the refrigerant pipe connection port 3c of the plate heat exchanger 3 returns from the suction muffler 4a to the compressor 4 via the four-way valve 5. The water W cooled by the plate heat exchanger 3 is supplied to, for example, a fan coil unit and used for cooling or the like.

Next, the operation of the plate heat exchanger 3 will be described.
In the side portion H1 composed of the wall portions 71a and 72b, at the cross-sectional position shown in FIG. 10, the wall portion 71a and the long portion Fa of the heat transfer plate 40 and the convex portion 62 of the heat transfer plate 41 on the back surface side thereof are formed. Since the long portion Fa of the heat transfer plate 40 and the convex portion 62 of the heat transfer plate 41 on the front surface side thereof are separated from each other, the temperature is transmitted only from the refrigerant R.
On the other hand, in the side portion H1 composed of the wall portions 71a and 72b, at the cross-sectional position shown in FIG. 9, the long portion Fa of the heat transfer plate 40 and the main plate portion 70b of the heat transfer plate 41 on the back side thereof are at a distance K1. Since the structure is such that the long portion Fa of the heat transfer plate 40 and the main plate portion 70b of the heat transfer plate 41 on the front side thereof are separated by a distance K2 (K1≈K2). The temperatures of the refrigerant R and the water W are transmitted at almost the same ratio.
Considering the states of FIGS. 9 and 10 comprehensively, the side portion H1 composed of the wall portions 71a and 72b has a larger contact area with the refrigerant R than the contact area with the water W.

In this embodiment, as shown in FIGS. 6, 9 and 10, the temperature sensor 14 is attached to the wall portion 71a. Therefore, the temperature sensor 14 joined to the wall portion 71a can detect the temperature of the refrigerant R while suppressing the influence of the water W.
The control device 15 reads the temperature data detected by the temperature sensor 14, and the arithmetic unit 17 calculates the temperature of the refrigerant R flowing in the plate heat exchanger 3 based on the temperature data.

As described above, in the temperature transmission to the side surface of the plate type heat exchanger 3 on the side where the temperature sensor 14 is joined, the temperature transmission between the water W and the refrigerant R is not the same ratio, and the refrigerant R is more than the water W. Since the ratio of temperature transmission increases, the temperature sensor 14 can improve the accuracy of detecting the temperature of the refrigerant R.
In addition, as the temperature sensor 14 increases the accuracy of detecting the temperature of the refrigerant R, the outdoor unit 1 increases the accuracy of calculating the pressure saturation temperature data by the control device 15, and improves the control accuracy of the electronic expansion valves 8a and 8b. Can be enhanced.

Further, as shown in FIG. 8, the wall portion 71a is formed so that the protruding length L1 from the main plate portion 70a is longer than the protruding length L2 of the wall portion 72a from the main plate portion 70a. As shown in 9, the joinable width S1 of the temperature sensor 14 is configured to be about twice the width S2 of the second flow path 64 of the refrigerant R in the stacking direction. Therefore, it is not necessary to use a small temperature sensor corresponding to the width S2, and the temperature sensor 14 having a size corresponding to the width S1 can be used, so that the temperature can be detected at low cost.

The heat transfer plate 40 is formed so that the protruding height of the convex portion 61 from the main plate portion 70a is the same as the protruding height of the high portions 75a and 76a from the main plate portion 70a. Therefore, both the convex portion 61 of the heat transfer plate 40 and the high portions 75a and 76a come into contact with the main plate portion 70b of the heat transfer plate 41 located on the front surface side of the heat transfer plate 40, so that the plate type heat is generated. The strength of the exchanger 3 can be increased.
Further, in the heat transfer plate 41, the protruding height of the convex portion 62 from the main plate portion 70b is formed to be the same as the protruding height of the high portions 75b and 76b from the main plate portion 70b. Therefore, both the convex portion 62 of the heat transfer plate 41 and the high portions 75b and 76b come into contact with the main plate portion 70a of the heat transfer plate 40 located on the front surface side of the heat transfer plate 41, so that the plate type heat is generated. The strength of the exchanger 3 can be increased.

Further, as shown in FIG. 9, in the plate type heat exchanger 3, the total number of heat transfer plates 40 and heat transfer plates 41 is an odd number. The flow path closest to the outer plate 42 includes a first flow path 63 through which water W flows, and the water W is between the outer plate 43 and the heat transfer plate 40 adjacent to the outer plate 43. Is configured to flow. Therefore, in the plate heat exchanger 3, the heat (cold air) of the refrigerant R is exchanged through the reinforcing plates 44 and 45 by interposing the water W between the refrigerant R and the reinforcing plates 44 and 45. It is possible to suppress the release to the outside of the vessel 3 and suppress the energy loss.

Embodiment 2.
The outdoor unit provided with the plate heat exchanger 80 according to the second embodiment of the present invention will be described with reference to FIGS. 11 to 17. In FIGS. 11 to 17, the same reference numerals as those in FIGS. 1 to 10 indicate the same or corresponding parts. The outdoor unit provided with the plate heat exchanger 80 of the second embodiment is a modification of the convex portions 61 and 62 of the heat transfer plates 40 and 41 of the first embodiment.

FIG. 11 is a front view of the heat transfer plates 81 and 82. FIG. 12 is an enlarged view of the heat transfer plates 81 and 82. FIG. 13A is a cross-sectional view of the heat transfer plates 81 and 82 viewed from the positions EE of FIG. 11, and FIG. 13B is a cross-sectional view of the heat transfer plates 81 and 82 of FIG. It is a cross-sectional view seen from the position, (c) is a cross-sectional view of the heat transfer plates 81 and 82 seen from the position of JJ in FIG. 11, and (d) is a cross-sectional view of the heat transfer plates 81 and 82. 11 is a cross-sectional view seen from the position of HH. FIG. 14 is a cross-sectional view of the plate heat exchanger 80 viewed from the position FF of FIG. 11, and FIG. 15 is a cross-sectional view of the plate heat exchanger 80 viewed from the position GG of FIG. It is a figure. FIG. 16 is a cross-sectional view of the plate heat exchanger 80 viewed from the position I-I in FIG. 11, and FIG. 17 is a cross-sectional view of the plate heat exchanger 80 viewed from the position JJ of FIG. It is a figure.
The plate heat exchanger 80 of the present embodiment (see FIGS. 14 and 15) includes heat transfer plates 81 and 82 as shown in FIGS. 11 and 13.

First, the detailed configuration of the heat transfer plate 81 will be described.
The heat transfer plate 81 includes a plurality of protrusions 83 and a plurality of protrusions 84. The convex portion 83 and the convex portion 84 are formed in a substantially V shape when viewed from the front surface side.
The plurality of convex portions 83 are formed at the central positions of the main plate portion 70a in the longitudinal direction. Each convex portion 83 is formed from the long side of the main plate portion 70a on the wall portion 72a side to a position at a predetermined distance from the long side of the wall portion 71a.

Since the plurality of convex portions 83 are formed from the long side of the main plate portion 70a on the wall portion 71a side to a position at a predetermined interval, the main plate portion 70a is formed on the wall portion 71a side of the plurality of convex portions 83. A long portion Fc having no protruding shape is formed. That is, the wall of the main plate portion 70a is formed by arranging a plurality of convex portions 83 formed at predetermined intervals from the long side of the main plate portion 70a on the wall portion 71a side along the longitudinal direction of the main plate portion 70a. On the long side of the portion 71a side, a long portion Fc, which is a part of the main plate portion 70a and a region in which the convex portion 83 is not formed, is formed.

That is, the convex portion 83 is formed intermittently along the long side of the main plate portion 70a on the wall portion 72a side as shown by being surrounded by the alternate long and short dash line in FIG. 12, and the long portion Fc is formed. As shown by being surrounded by the alternate long and short dash line on the left side of FIG. 12, it is formed so as to be in contact with the long side of the wall portion 71a side of the main plate portion 70a.

A plurality of ridges 84 are formed on the main plate portion 70a at positions on both sides in the longitudinal direction of the long portion Fc. Each ridge portion 84 is formed from the long side of the main plate portion 70a on the wall portion 72a side to the long side of the wall portion 71a. The constituent requirements of the main plate portion 70a do not include the convex portion 83 and the convex portion 84.

As shown in FIGS. 11, 14, and 15, the temperature sensor 14 is provided at a position corresponding to the long portion Fc in the longitudinal direction, and is joined to the wall portion 71a of the heat transfer plate 81 by brazing. Has been done. Further, the temperature sensor 14 is attached to the portion of the wall portion 71a facing the refrigerant R.

Next, the detailed configuration of the heat transfer plate 82 will be described.
As shown in FIGS. 11 and 13, the heat transfer plate 82 has the same shape as the heat transfer plate 81, and the reference numerals shown in parentheses correspond to the configurations of each part of the heat transfer plate 82.
That is, in the heat transfer plate 82, the first opening 54, the second opening 55, the third opening 56, the fourth opening 57, the convex portion 85, the convex portion 86, the main plate portion 70b, the wall portions 71b, 72b, 73b, 74b, high portion 75b, 76b, and long portion Fd, respectively, have a first opening 50, a second opening 51, a third opening 52, a fourth opening 53, and a convex portion 83 in the heat transfer plate 81. , Convex portion 84, main plate portion 70a, wall portions 71a, 72a, 73a, 74a, high portions 75a, 76a, and long portions Fc, respectively. Therefore, the description of each part of the heat transfer plate 82 will be omitted. The constituent requirements of the main plate portion 70b do not include the convex portion 85 and the convex portion 86.

Next, the contact state between the heat transfer plate 81 and the heat transfer plate 82 will be described.
As shown in FIG. 14, the long portion Fc of the main plate portion 70a of the heat transfer plate 81 is configured to be separated from the main plate portion 70b of the heat transfer plate 82 located on the back surface side. This distant distance is shown as the distance K5 in FIG. Further, the long portion Fc of the main plate portion 70a of the heat transfer plate 81 is configured to be separated from the main plate portion 70b of the heat transfer plate 82 located on the front surface side. This distant distance is shown as the distance K6 in FIG. The plate heat exchanger 80 is configured such that the distance K5 and the distance K6 are substantially the same.

As shown in FIG. 14, the long portion Fd of the main plate portion 70b of the heat transfer plate 82 is configured to be separated from the main plate portion 70a of the heat transfer plate 81 located on the back surface side. This distant distance is shown as the distance K7 in FIG. Further, the long portion Fd of the main plate portion 70b of the heat transfer plate 82 is configured to be separated from the main plate portion 70a of the heat transfer plate 81 located on the front surface side. This distant distance is shown as the distance K8 in FIG. The plate heat exchanger 80 is configured such that the distance K7 and the distance K8 are substantially the same.

As shown in FIG. 15, the convex portion 83 of the heat transfer plate 81 is configured to abut the wall portion 71b and the long portion Fd of the heat transfer plate 82. Therefore, in the cross-sectional position of FIG. 15, only the water W comes into contact with the side portion H2 composed of the wall portions 71b and 72a without the refrigerant R coming into contact with the side portion H2. That is, the convex portion 83 of the heat transfer plate 81 is in contact with the wall portion 71b of the heat transfer plate 82 facing the convex portion 83 next to the projecting side. Further, the long portion Fd of the main plate portion 70b of the heat transfer plate 82 is in contact with the convex portion 83 of the heat transfer plate 81 located next to the side on which the wall portions 71b, 72b, 73b, 74b protrude.

On the other hand, the long portion Fd of the main plate portion 70b of the heat transfer plate 82 is configured to be separated from the convex portion 83 of the heat transfer plate 81 located on the front surface side.
That is, the distance from the long portion Fd to the convex portion 83 of the heat transfer plate 81 facing the wall portions 71b, 72b, 73b, 74b next to the protruding side is based on the long portion Fd of the heat transfer plate 82. The distance from the long portion Fd to the convex portion 83 of the heat transfer plate 81 facing the convex portion 85 next to the protruding side is smaller than the distance.

As shown in FIG. 15, the convex portion 85 of the heat transfer plate 82 is configured to abut the wall portion 71a and the long portion Fc of the heat transfer plate 81. Therefore, in the cross-sectional position of FIG. 15, only the refrigerant R comes into contact with the side portion H1 composed of the wall portions 71a and 72b without the water W coming into contact with the side portion H1. That is, the convex portion 85 of the heat transfer plate 82 is in contact with the wall portion 71a of the heat transfer plate 81 facing the convex portion 85 next to the projecting side. Further, the long portion Fc of the main plate portion 70a of the heat transfer plate 81 is in contact with the convex portion 85 of the heat transfer plate 82 located next to the side on which the wall portions 71a, 72a, 73a, 74a protrude.

On the other hand, the long portion Fc of the main plate portion 70a of the heat transfer plate 81 is configured to be separated from the convex portion 85 of the heat transfer plate 82 located on the front surface side.
That is, the distance from the long portion Fc to the convex portion 85 of the heat transfer plate 82 facing the wall portions 71a, 72a, 73a, 74a next to the protruding side is based on the long portion Fc of the heat transfer plate 81. , It is configured to be smaller than the distance from the long portion Fc to the convex portion 85 of the heat transfer plate 82 facing the convex portion 83 next to the protruding side.

In the cross-sectional positions of FIGS. 14 and 16, the convex portion 83 and the convex portion 84 do not abut against the main plate portion 70b of the heat transfer plate 82 located on the front surface side thereof, but may abut depending on the cross-sectional position. It is configured in. Similarly, at the cross-sectional positions of FIGS. 14 and 16, the convex portion 85 and the convex portion 86 do not abut against the main plate portion 70a of the heat transfer plate 81 located on the front surface side thereof, but depending on the cross-sectional position. It is configured to abut.
Although not shown, the high portions 75a and 76a are configured to abut against the main plate portion 70a of the heat transfer plate 82 located on the front surface side thereof, and the high portions 75b and 76b are located on the front surface side thereof. It is configured to come into contact with the main plate portion 70a of the heat transfer plate 81.

The outdoor unit provided with the plate heat exchanger 80 configured in this way also performs the same operation as the outdoor unit 1 of the first embodiment.
Further, in the second embodiment, the same effect as that of the first embodiment is obtained, and the following effects are obtained.
At the position where the temperature sensor 14 is not provided in the longitudinal direction, as shown in FIGS. 16 and 17, the ridges 84 and 86 are formed over the entire area in the lateral direction, and therefore heat exchange is performed in this portion. The efficiency can be increased as compared with the convex portions 83 and 85.

Embodiment 3.
The outdoor unit provided with the plate heat exchanger 90 according to the third embodiment of the present invention will be described with reference to FIGS. 18 to 21. In FIGS. 18 to 21, the same reference numerals as those in FIGS. 1 to 10 indicate the same or corresponding parts. The outdoor unit provided with the plate heat exchanger 90 of the third embodiment partially modifies the shapes of the convex portions 61 and 62 of the heat transfer plates 40 and 41 of the first embodiment, and forms the convex portions 93 and 94. It is an added one.

FIG. 18 is a front view of the heat transfer plates 91 and 92. FIG. 19A is a cross-sectional view of the heat transfer plates 91 and 92 viewed from the position KK of FIG. 18, and FIG. 19B is a cross-sectional view of the heat transfer plates 91 and 92 of FIG. It is a cross-sectional view seen from the position, (c) is a cross-sectional view of the heat transfer plates 91 and 92 seen from the position of MM of FIG. 18, and (d) is a cross-sectional view of the heat transfer plates 91 and 92. It is sectional drawing seen from the position of NN of 18. FIG. 20 is a cross-sectional view of the plate heat exchanger 90 viewed from the position LL of FIG. 18, and FIG. 21 is a cross-sectional view of the plate heat exchanger 90 viewed from the position MM of FIG. It is a figure.

The plate heat exchanger 90 (see FIGS. 20 and 21) of the present embodiment includes heat transfer plates 91 and 92 as shown in FIGS. 18 and 19.
First, the detailed configuration of the heat transfer plate 91 will be described.
The heat transfer plate 91 is formed with a convex portion 93 close to the wall portion 72a side of the main plate portion 70a. The convex portion 93 is formed so as to extend along the longitudinal direction. The convex portion 93 is formed so that the tip surface 93a is a flat surface, and the flat surface is formed so as to be at the same height as the apex of the convex portion 61. The convex portion 93 is formed so as to protrude from the main plate portion 70a, and is formed by pressing the plate material.
The plurality of convex portions 61 formed from the long side of the main plate portion 70a on the wall portion 72a side to the long portion Fa are the convex portions continuously formed along the long side of the main plate portion 70a on the wall portion 72a side. It is formed continuously in 93. The constituent requirements of the main plate portion 70a do not include the convex portions 61 and 93.

In the present embodiment, the length of the convex portion 93 in the lateral direction is 1.75 mm. The ratio of the lateral length of the convex portion 93 to the lateral length of the main plate portion 70a is preferably "1.2: 100 to 4: 100", and in the present embodiment, it is "2: 100". By setting the ratio of the lateral length of the convex portion 93 to the lateral length of the main plate portion 70a to be "1.2: 100 to 4: 100", contact with the elongated portion Fb on the front side, which will be described later. The state can be maintained favorably, and the area forming the convex portion 93 on the main plate portion 70a can be reduced as much as possible. Further, by setting the ratio of the lateral length of the convex portion 93 to the lateral length of the main plate portion 70a to "2: 100", the contact state with the elongated portion Fb on the front side, which will be described later, is further improved. It can be maintained favorably, and the area forming the convex portion 93 on the main plate portion 70a can be reduced as much as possible.

Next, the detailed configuration of the heat transfer plate 92 will be described.
As shown in FIGS. 18 and 19, the heat transfer plate 92 has the same shape as the heat transfer plate 91, and the reference numerals shown in parentheses correspond to the configurations of each part of the heat transfer plate 92.
That is, the first opening 54, the second opening 55, the third opening 56, the fourth opening 57, the convex portion 62, the main plate portion 70b, the wall portions 71b, 72b, 73b, 74b, and the height of the heat transfer plate 92. The first opening 50, the second opening 51, the third opening 52, and the fourth opening 53 of the heat transfer plate 91, respectively, of the portions 75b and 76b, the convex portion 94, the tip surface 94a, and the long portion Fb. It corresponds to the convex portion 61, the main plate portion 70a, the wall portions 71a, 72a, 73a, 74a, the high portions 75a, 76a, the convex portion 93, the tip surface 93a, and the long portion Fa, respectively. Therefore, the description of each part of the heat transfer plate 92 will be omitted. The constituent requirements of the main plate portion 70b do not include the convex portions 62 and 94.

Next, the contact state between the heat transfer plate 91 and the heat transfer plate 92 will be described.
As shown in FIGS. 20 and 21, the convex portion 93 of the heat transfer plate 91 is configured to abut the wall portion 71b and the long portion Fb of the heat transfer plate 92. Therefore, in the cross-sectional positions of FIGS. 20 and 21, only the water W comes into contact with the side portion H2 composed of the wall portions 71b and 72a without the refrigerant R coming into contact with the side portion H2. That is, the convex portion 93 of the heat transfer plate 91 is in contact with the wall portion 71b of the heat transfer plate 92 facing the convex portion 93 next to the projecting side. Further, the long portion Fb of the main plate portion 70b of the heat transfer plate 92 is in contact with the convex portion 93 of the heat transfer plate 91 located next to the side on which the wall portions 71b, 72b, 73b, 74b protrude.

On the other hand, the long portion Fb of the main plate portion 70b of the heat transfer plate 92 is configured to be separated from the convex portion 93 of the heat transfer plate 91 located on the front surface side.
That is, the distance from the long portion Fb to the convex portion 93 of the heat transfer plate 91 facing the wall portions 71b, 72b, 73b, 74b next to the protruding side is based on the long portion Fb of the heat transfer plate 92. The distance from the long portion Fb to the convex portion 93 of the heat transfer plate 91 facing the convex portion 94 next to the protruding side is smaller than the distance.

As shown in FIGS. 20 and 21, the convex portion 94 of the heat transfer plate 92 is configured to abut the wall portion 71a and the elongated portion Fa of the heat transfer plate 91. Therefore, in the cross-sectional positions of FIGS. 20 and 21, only the refrigerant R comes into contact with the side portion H1 composed of the wall portions 71a and 72b without the water W coming into contact with the side portion H1. That is, the convex portion 94 of the heat transfer plate 92 is in contact with the wall portion 71a of the heat transfer plate 91 facing the convex portion 93 next to the protruding side. Further, the long portion Fa of the main plate portion 70a of the heat transfer plate 91 is in contact with the convex portion 94 of the heat transfer plate 92 located next to the side on which the wall portions 71a, 72a, 73a, 74a protrude.

On the other hand, the long portion Fa of the main plate portion 70a of the heat transfer plate 91 is configured to be separated from the convex portion 94 of the heat transfer plate 92 located on the front surface side.
That is, the distance from the long portion Fa to the convex portion 94 of the heat transfer plate 92 facing the wall portions 71a, 72a, 73a, 74a next to the protruding side is based on the long portion Fa of the heat transfer plate 91. The distance from the long portion Fa to the convex portion 94 of the heat transfer plate 92 facing the convex portion 93 next to the protruding side is smaller than the distance to the convex portion 94.

In the cross-sectional positions of FIGS. 20 and 21, the convex portion 61 is not in contact with the main plate portion 70b of the heat transfer plate 92 located on the front surface side thereof, but is configured to be in contact with the main plate portion 70b depending on the cross-sectional position. .. Similarly, at the cross-sectional positions of FIGS. 20 and 21, the convex portion 62 is not in contact with the main plate portion 70a of the heat transfer plate 91 located on the front surface side thereof, but is configured to be in contact with the main plate portion 70a depending on the cross-sectional position. Has been done.

Although not shown, the high portions 75a and 76a are configured to abut against the main plate portion 70b of the heat transfer plate 92 located on the front surface side thereof, and the high portions 75b and 76b are located on the front surface side thereof. It is configured to come into contact with the main plate portion 70a of the heat transfer plate 91.
In addition, in the cross-sectional positions of FIGS. 20 and 21, the convex portion 93 of the heat transfer plate 91 abuts on the long portion Fb of the main plate portion 70b of the heat transfer plate 92 located on the front surface side thereof to transfer heat. The convex portion 94 of the plate 92 is in contact with the long portion Fa of the main plate portion 70a of the heat transfer plate 91 located on the front surface side thereof. Since the heat transfer plate 91 is laminated by rotating the heat transfer plate 92 by 180 degrees with respect to the axis Z extending vertically from the center of the plate-like surfaces of the main plate portions 70a and 70b, the heat transfer plate 91 abuts in this way.

The outdoor unit provided with the plate heat exchanger 90 configured in this way also performs the same operation as the outdoor unit 1 of the first embodiment.
Further, in the third embodiment, the same effect as that of the first embodiment is obtained, and the following effects are obtained.

In the side portion H1 composed of the wall portions 71a and 72b, at the cross-sectional position shown in FIG. 20, the wall portion 71a and the long portion Fa of the heat transfer plate 91 and the convex portion 94 of the heat transfer plate 92 on the back surface side thereof are formed. Since the long portion Fa of the heat transfer plate 91 and the convex portion 94 of the heat transfer plate 92 on the front surface side thereof are separated from each other, the temperature is transmitted only from the refrigerant R.
Similarly, the side portion H1 composed of the wall portions 71a and 72b has a convex portion of the wall portion 71a and the long portion Fa of the heat transfer plate 91 and the heat transfer plate 92 on the back side thereof even at the cross-sectional position shown in FIG. Since the long portion Fa of the heat transfer plate 91 and the convex portion 94 of the heat transfer plate 92 on the front side thereof are separated from each other, the temperature from only the refrigerant R is transmitted. NS.

Considering the states of FIGS. 20 and 21 comprehensively, the temperature detected by the temperature sensor 14 joined to the wall portion 71a is based on the temperature based on the refrigerant R, and is more accurate than the temperature sensor 14 of the first embodiment. The temperature of the refrigerant R flowing in the plate heat exchanger 3 can be detected.
Therefore, the control device 15 of the third embodiment can accurately calculate the temperature of the refrigerant R flowing in the plate heat exchanger 3 as compared with the control device 15 of the first embodiment. can.

Embodiment 4.
The outdoor unit provided with the plate heat exchanger 100 according to the fourth embodiment of the present invention will be described with reference to FIG. In FIG. 22, the same reference numerals as those in FIGS. 1 to 10 indicate the same or corresponding portions. In the outdoor unit provided with the plate heat exchanger 100 of the fourth embodiment, the heights of the convex portions 61 and 62 of the heat transfer plates 40 and 41 of the first embodiment are made lower than those of the first embodiment. ..
As shown in FIG. 22, the convex portion 61 of the heat transfer plate 40 is configured to be in contact with the wall portion 71b of the heat transfer plate 41, and is configured to be spaced from the long portion Fb of the heat transfer plate 41. ing. Further, the convex portion 62 of the heat transfer plate 41 is configured to be in contact with the wall portion 71a of the heat transfer plate 40, and is configured at a distance from the long portion Fa of the heat transfer plate 40.

The distance K9 from the long portion Fa to the convex portion 62 of the heat transfer plate 41 facing the side where the wall portions 71a, 72a, 73a, 74a protrude is the distance K9 from the long portion Fa of the heat transfer plate 40. The distance K10 from the long portion Fa to the convex portion 62 of the heat transfer plate 41 facing the convex portion 61 next to the protruding side is smaller than the distance K10.
Therefore, in the cross-sectional position of FIG. 22, the side portion H1 composed of the wall portions 71a and 72b has a larger contact area with the refrigerant R than the contact area with the water W.
Therefore, in the temperature transmission to the side surface of the plate type heat exchanger 100 on the side where the temperature sensor 14 is joined, the temperature transmission between the water W and the refrigerant R is not the same ratio, and the temperature transmission of the refrigerant R is higher than that of the water W. Therefore, the temperature sensor 14 can improve the accuracy of detecting the temperature of the refrigerant R.

Embodiment 5.
The outdoor unit provided with the plate heat exchanger 110 according to the fifth embodiment of the present invention will be described with reference to FIGS. 23 and 24. In FIGS. 23 and 24, the same reference numerals as those in FIGS. 18 to 21 indicate the same or corresponding parts. The outdoor unit provided with the plate heat exchanger 110 of the fifth embodiment has the heights of the protrusions 61, 62, 93, 94 of the heat transfer plates 91, 92 of the third embodiment lower than those of the third embodiment. It was done.
As shown in FIGS. 23 and 24, the convex portion 93 of the heat transfer plate 91 is configured to abut on the wall portion 71b of the heat transfer plate 92, and is spaced from the long portion Fb of the heat transfer plate 92. It is composed of. The convex portion 94 of the heat transfer plate 92 is configured to be in contact with the wall portion 71a of the heat transfer plate 91, and is configured to be spaced from the long portion Fa of the heat transfer plate 91.

FIG. 23 is a cross-sectional view of the plate heat exchanger 110 corresponding to the position of LL in FIG. The distance K11 from the long portion Fa to the convex portion 94 of the heat transfer plate 92 facing the side on which 72a, 73a, 74a protrudes is the distance K11 of the heat transfer plate 92 facing on the side on which the convex portion 93 protrudes from the long portion Fa. It is configured to be smaller than the distance K12 to the convex portion 94.
Further, FIG. 24 is a cross-sectional view of the plate heat exchanger 110 corresponding to the position of MM in FIG. 18, but the long portion Fa to the wall portion is based on the long portion Fa of the heat transfer plate 91. The distance K13 from the long portion Fa to the convex portion 94 of the heat transfer plate 92 facing the side on which the convex portions 93 protrude from the long portion Fa is the heat transfer plate facing on the side on which the convex portion 93 projects. It is configured to be smaller than the distance K14 to the convex portion 94 of 92.

Therefore, the side portion H1 composed of the wall portions 71a and 72b has a larger contact area with the refrigerant R than the contact area with the water W.
Therefore, in the temperature transmission to the side surface of the plate type heat exchanger 110 on the side where the temperature sensor 14 is joined, the temperature transmission between the water W and the refrigerant R is not the same ratio, and the temperature transmission of the refrigerant R is higher than that of the water W. Therefore, the temperature sensor 14 can improve the accuracy of detecting the temperature of the refrigerant R.

Embodiment 6.
The outdoor unit provided with the plate heat exchanger 120 according to the sixth embodiment of the present invention will be described with reference to FIG. In FIG. 25, the same reference numerals as those in FIGS. 1 to 10 indicate the same or corresponding portions. While the convex portions 61 and 62 of the first embodiment were formed by pressing the heat transfer plates 40 and 41, the outdoor unit provided with the plate heat exchanger 120 of the sixth embodiment is convex. The portions 121 and 122 are formed separately from the heat transfer plates 40 and 41.
As shown in FIG. 25, a plurality of convex portions 121 are attached to the portion of the main plate portion 70a of the heat transfer plate 40 excluding the long portion Fa. Further, a plurality of convex portions 122 are attached to the portion of the main plate portion 70b of the heat transfer plate 41 excluding the long portion Fb. Some of the convex portions 121 of the heat transfer plate 40 are configured to abut the wall portion 71b and the elongated portion Fb of the heat transfer plate 41. Further, some of the convex portions 122 of the heat transfer plate 41 are configured to come into contact with the wall portion 71a and the long portion Fa of the heat transfer plate 40.

Therefore, the side portion H1 composed of the wall portions 71a and 72b has a larger contact area with the refrigerant R than the contact area with the water W.
Therefore, in the temperature transmission to the side surface of the plate type heat exchanger 120 on the side where the temperature sensor 14 is joined, the temperature transmission between the water W and the refrigerant R is not the same ratio, and the temperature transmission of the refrigerant R is higher than that of the water W. Therefore, the temperature sensor 14 can improve the accuracy of detecting the temperature of the refrigerant R.
In the sixth embodiment, the convex portions 121 and 122 are formed separately from the heat transfer plates 40 and 41, but the convex portions 121 are integrated with the heat transfer plate 40 and the convex portions 122 are formed as a heat transfer plate. It may be integrally configured with 41. Even with this configuration, the same effect can be achieved.

In addition, the convex portions 93 and 94 of the third embodiment may be provided with respect to the second embodiment. With this configuration, at the position where the temperature sensor 14 is not provided in the longitudinal direction, the ridges 84 and 86 are formed over the entire area in the lateral direction, so that the heat exchange efficiency in this portion is convex. It can be increased as compared with the portions 83 and 85. In addition, the temperature detected by the temperature sensor 14 joined to the wall portion 71a is based on the temperature based on the refrigerant R, and the refrigerant R flowing in the plate heat exchanger 3 is more accurate than the temperature sensor 14 of the first embodiment. Temperature can be detected.

The convex portions 83 and 85 of the second embodiment may be configured to have a lower height as in the plate heat exchanger 100 of the fourth embodiment. Even with this configuration, the side portion H1 composed of the wall portions 71a and 72b has a larger contact area with the refrigerant R than the contact area with the water W, and the temperature sensor 14 determines that the refrigerant R has a contact area. The temperature detection accuracy can be improved.

The convex portions 121 and 122 of the sixth embodiment may be configured to have a lower height as in the plate heat exchanger 100 of the fourth embodiment. Even with this configuration, the side portion H1 composed of the wall portions 71a and 72b has a larger contact area with the refrigerant R than the contact area with the water W, and the temperature sensor 14 determines that the refrigerant R has a contact area. The temperature detection accuracy can be improved.

In the refrigerant circuit 2a of each of the above embodiments, a four-way valve 5 is provided to switch the flow of the refrigerant R so that the mode can be switched between the heating mode and the cooling mode, but the configuration is not limited to this. For example, the four-way valve 5 may be omitted from the refrigerant circuit 2a, and the refrigerant circuit 2a may be configured so that only one of the heating mode and the cooling mode is performed.

1 Outdoor unit 2a Refrigerant circuit 2b Water circuit 3, 80, 90, 100, 110, 120 Plate heat exchanger 3a, 3b Water pipe connection port 3c, 3d Refrigerant pipe connection port 4 Compressor 4a Muffler 5 Four-way valve 6 Air heat Exchanger 7 Pressure vessel 8a, 8b Electronic expansion valve 10 Refrigerant piping 11, 12, 13, 14 Temperature sensor 15 Control device 16 Storage device 17 Computing device 20 Housing 20a Grill 21 Blower room 22 Machine room 23 Separator 24 Fan 40, 41 , 81, 82, 91, 92 Heat transfer plates 42, 43 Outer plates 44, 45 Reinforcing plates 46, 50, 54 First openings 47, 51, 55 Second openings 48, 52, 56 Third openings 49, 53, 57 Fourth openings 61, 62, 83, 85, 121, 122 Convex parts 84, 86 Convex parts 63 First flow path 64 Second flow path 70a, 70b Main plate part,
71a, 71b, 72a, 72b, 73a, 73b, 74a, 74b Wall part 75a, 75b, 76a, 76b High part 93, 94 Convex part 93a, 94a Tip surface E1, E2, E3, E4 Tip Fa, Fb, Fc, Fd long part H1, H2 side part K1, K2, K3, K4, K5, K6, K7, K8, K9, K10, K11, K12, K13, K14 distance L1, L2 length S1, S2 width R refrigerant W water Z axis

Claims (18)

A heat transfer plate having a rectangular plate-shaped main plate portion and a wall portion protruding from the edge of the main plate portion to one side of the plate-shaped surface alternately extends vertically from the center of the plate-shaped surface of the main plate portion. Plate-type heat that is inverted 180 degrees with respect to the axis and laminated, and the first flow path through which the first fluid flows and the second flow path through which the second fluid flows are alternately formed in the stacking direction between the heat transfer plates. In the exchanger
The main plate portion is provided with a convex portion protruding from a plate-shaped surface opposite to the surface on which the wall portion protrudes.
The convex portions, the main plate portion one is formed continuous manner along the long sides of, and in the wall of the heat transfer plate convex section faces next to the side where the projecting contact,
The main plate portion is provided with a long portion so as to be in contact with the other long side.
With reference to the long portion of the heat transfer plate, the distance from the long portion to the convex portion of the heat transfer plate facing next to the side where the wall portion protrudes is from the long portion to the convex portion. A plate-type heat exchanger configured to be smaller than the distance to the convex portion of the heat transfer plate facing the side on which the portion protrudes. The plate heat exchanger according to claim 1, wherein the convex portion is in contact with the long portion of the heat transfer plate facing the side on which the convex portion protrudes. The plate heat exchanger according to claim 1 or 2, wherein the convex portion is formed so as to extend from one long side of the main plate portion to the long portion. The convex portion formed along one long side of the main plate portion is continuously formed.
The plate heat exchanger according to any one of claims 1 to 3, wherein a plurality of convex portions formed from one long side of the main plate portion to the long portion are formed. The main plate portion is provided with ridges formed from one long side of the main plate portion to the other long side of the main plate portion at positions on both sides of the long portion in the longitudinal direction of the main plate portion. The plate heat exchanger according to any one of claims 1 to 4. The wall portion corresponding to the other long side and the wall portion corresponding to the one long side are formed so that the distance between them increases as the distance from the main plate portion increases.
The protruding length of the wall portion corresponding to the other long side from the main plate portion is configured to be longer than the protruding length of the wall portion corresponding to the one long side from the main plate portion. The plate heat exchanger according to any one of claims 1 to 5. The tip of the wall portion corresponding to the one long side of the heat transfer plate is configured to be aligned with the tip of the wall portion corresponding to the other long side of the adjacent heat transfer plate in the stacking direction. The plate heat exchanger according to claim 6. Any of claims 1 to 7, wherein a temperature detecting means installation portion for installing a temperature detecting means for detecting the temperature of the second fluid is provided on a portion of the wall portion facing the second fluid. The plate heat exchanger according to the first paragraph. The plate heat exchanger according to claim 8, the compressor for compressing the second fluid, the air heat exchanger for heat exchange between air and the second fluid, and the pressure of the second fluid. A second fluid circuit in which the second fluid circulates, including an expansion valve for lowering and a pressure vessel for holding the excess second fluid.
The temperature detecting means installed in the temperature detecting means installation unit and
Heat pump device equipped with. A heat transfer plate having a rectangular plate-shaped main plate portion and a wall portion protruding from the edge of the main plate portion to one side of the plate-shaped surface alternately extends vertically from the center of the plate-shaped surface of the main plate portion. Plate-type heat that is inverted 180 degrees with respect to the axis and laminated, and the first flow path through which the first fluid flows and the second flow path through which the second fluid flows are alternately formed in the stacking direction between the heat transfer plates. In the exchanger
The main plate portion is provided with a convex portion protruding from a plate-shaped surface opposite to the surface on which the wall portion protrudes.
The convex portion is formed intermittently or continuously along one long side of the main plate portion, and abuts on the wall portion of the heat transfer plate facing the side on which the convex portion protrudes. ,
The main plate portion is provided with a long portion so as to be in contact with the other long side.
With reference to the long portion of the heat transfer plate, the distance from the long portion to the convex portion of the heat transfer plate facing next to the side where the wall portion protrudes is from the long portion to the convex portion. The heat transfer plate is configured to be smaller than the distance to the convex portion of the heat transfer plate facing the side on which the portion protrudes.
The main plate portion is provided with ridges formed from one long side of the main plate portion to the other long side of the main plate portion at positions on both sides of the long portion in the longitudinal direction of the main plate portion.
Plate heat exchanger. The plate heat exchanger according to claim 10, wherein the convex portion is in contact with the long portion of the heat transfer plate facing the side on which the convex portion protrudes. The convex portion is formed so as to extend from the one long side of the main plate portion to the long portion.
The plate heat exchanger according to claim 10 or 11. The convex portion formed along one long side of the main plate portion is continuously formed.
A plurality of convex portions formed from one long side of the main plate portion to the long portion are formed.
The plate heat exchanger according to any one of claims 10 to 12. The wall portion corresponding to the other long side and the wall portion corresponding to the one long side are formed so that the distance between them increases as the distance from the main plate portion increases.
The protruding length of the wall portion corresponding to the other long side from the main plate portion is configured to be longer than the protruding length of the wall portion corresponding to the one long side from the main plate portion. Are
The plate heat exchanger according to any one of claims 10 to 13. It is configured so that the tip of the wall portion corresponding to the one long side of the heat transfer plate and the tip of the wall portion corresponding to the other long side of the adjacent heat transfer plate in the stacking direction are aligned. ing
The plate heat exchanger according to claim 14. Any of claims 10 to 15, wherein a temperature detecting means installation portion for installing a temperature detecting means for detecting the temperature of the second fluid is provided on a portion of the wall portion facing the second fluid. The plate heat exchanger according to the first paragraph. The plate heat exchanger according to claim 16, the compressor for compressing the second fluid, the air heat exchanger for heat exchange between air and the second fluid, and the pressure of the second fluid. A second fluid circuit in which the second fluid circulates, including an expansion valve for lowering and a pressure vessel for holding the excess second fluid.
The temperature detecting means installed in the temperature detecting means installation unit and
Heat pump device equipped with. A heat transfer plate having a rectangular plate-shaped main plate portion and a wall portion protruding from the edge of the main plate portion to one side of the plate-shaped surface alternately extends vertically from the center of the plate-shaped surface of the main plate portion. Plate-type heat that is inverted 180 degrees with respect to the axis and laminated, and the first flow path through which the first fluid flows and the second flow path through which the second fluid flows are alternately formed in the stacking direction between the heat transfer plates. In the exchanger
By stacking the plurality of heat transfer plates, four side portions composed of the plurality of wall portions are provided at positions corresponding to the four sides of the main plate portion.
At least one of the four side portions is configured such that the contact area of the second fluid is larger than the contact area of the first fluid.
A temperature detecting means for detecting the temperature of the second fluid at a portion of the side portion facing the second fluid, which is configured so that the contact area of the second fluid is larger than the contact area of the first fluid. A plate-type heat exchanger provided with a temperature detecting means installation unit for installation.

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