JPH10122770A - Plate type heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To avoid freezing water in a heat exchanger even when the heat exchanger is used as a supercooled water generating heat exchanger by improving the distribution mode of the fluid flowing inside a plate-type heat exchanger. SOLUTION: A plate-type heat exchanger is applied as a supercooled water generating heat exchanger to be used as an ice thermal storage device to generate ice by the supercooling canceling operation of the supercooled water. A plurality of corrugated heat transfer plates 54, 55, 56, 57 are stacked, and contact parts are brazed to form a refrigerant flow passages A, A and a water flow passage B between the plates. The quantity of the brazing filler metal C of a part facing the water flow passage B is larger than that on a part facing the refrigerant flow passages A, A. A corner part of the water flow passage B is closed by the brazing filler metal C projected from the brazed part facing the water flow passage B to prevent water from flowing in the corner part.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a plate type heat exchanger, and more particularly, to an improvement in a fluid flow form in a fluid passage formed between heat transfer plates.

[0002]

2. Description of the Related Art Conventionally, as an example of an ice heat storage device provided in an ice heat storage type air conditioner or the like, as disclosed in Japanese Patent Application Laid-Open No. 4-251177, for example, a compressor and a condenser are disclosed. A refrigerant circulation circuit formed by sequentially connecting an expansion mechanism and a refrigerant heat exchange unit by a refrigerant pipe, and a heat storage tank,
There is known an apparatus provided with a water circulation circuit formed by sequentially connecting a heat storage medium heat exchange section capable of exchanging heat with the refrigerant heat exchange section and a supercooling elimination section by a water pipe.

[0003] In the ice making operation of this type of ice heat storage device, water (heat storage medium) taken out from a heat storage tank to a water pipe is heat-exchanged with a refrigerant in a refrigerant heat exchange unit in a heat storage medium heat exchange unit. Cooling is performed to a cooling state, and the supercooled state is eliminated in the supercooling elimination section to generate slurry ice. Then, the ice is supplied to and stored in the heat storage tank.

[0004] The heat storage medium heat exchange section and the refrigerant heat exchange section are generally integrally formed by a shell and tube type heat exchanger.

By the way, as a heat exchanger other than this type of heat exchanger, a large heat transfer area can be secured while reducing the overall size as compared with a shell and tube type heat exchanger, and the number of stacked heat transfer plates can be reduced. A plate-type heat exchanger in which the heat transfer area can be easily increased or decreased by changing the plate heat exchanger is generally known. Therefore, the inventors of the present invention have considered the use of the plate heat exchanger as a heat exchanger for generating supercooled water.

[0006] Further, when a heat transfer plate composed of a herringbone type corrugated plate, which is generally known, is used as it is as a supercooled water generating heat exchanger, the supercooled water is in a state of large turbulence. There is a possibility that the supercooling elimination operation due to the flow may occur inside the heat exchanger. For this reason, the inventors of the present invention make the water flow with little turbulence. The configuration of the heat exchanger considered by the present inventors will be specifically described. As shown in FIG. 27, a plurality of heat transfer plates (a, a,
..) Are joined to form a water flow path (b) and a refrigerant flow path (c) alternately between the heat transfer plates (a, a,...). And each of these flow paths (b, c)
Has a uniform cross-sectional shape from the upstream side to the downstream side. Thereby, water is cooled in each water flow path (b) by the refrigerant evaporated in each refrigerant flow path (c), and supercooled water is obtained.

[0007]

However, when the heat exchanger having such a configuration is used for generating supercooled water, the following problems remain.

[0008] The water flowing through each water flow path (b) is
Stagnation in the corners. That is, in the region x in FIG. 27, the flow velocity of the water is low, and the water flowing through this corner (x) always flows through the corner (x) from the upstream end to the downstream end of the water flow path (b). Will be. For this reason,
Cooling of the water at this corner (x) proceeds, and the degree of supercooling is significantly increased only at this portion. As a result, the supercooled state of the water is eliminated at the corner (x), and ice may be generated inside the heat exchanger. In such a situation, ice will be generated in parts other than the supercooling elimination part, and not only will the ice making operation not be performed stably, but also this ice will adhere to the heat transfer plate and grow. This causes inconveniences such as an inability to make an ice-making operation and a plastic deformation of the plate.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and an object of the present invention is to improve the flow form of a fluid flowing inside a plate-type heat exchanger so that the heat exchanger can be supercooled. An object of the present invention is to prevent a problem caused by freezing inside the heat exchanger even when the heat exchanger is used as a heat exchanger.

[0010]

In order to achieve the above object, the present invention improves the flow of water in a water flow path so that water with a high degree of supercooling flows at the corners of the water flow path. Such a situation can be avoided.

More specifically, the means implemented by the first aspect of the present invention is that a plurality of heat transfer plates (53-58) are overlapped and a fluid passage (A, A) is provided between the heat transfer plates (53-58). B) is formed, and it is assumed that a plate-type heat exchanger in which fluids flowing in fluid passages (A, B) adjacent to each other exchange heat via heat transfer plates (53 to 58). Then, the cross-sectional shape of the fluid passage (B) through which at least one of the fluid passages (A, B) through which the fluids performing the heat exchange flow is a non-circular cross-section having a corner portion. Further, at the corner of the fluid passage (B), a blocking means (40) for closing the corner to prevent the flow of the fluid at the corner is provided.

According to this specific matter, for example, the present invention is used as a heat exchanger for performing heat exchange between water and a refrigerant to make the water in a supercooled state, and is provided at the corner of the water passage (B). When the corners are closed, there is no portion in the water passage (B) where the degree of supercooling is significantly increased. For this reason, a situation in which supercooling is eliminated inside the heat exchanger and ice is generated can be avoided.

According to a second aspect of the present invention, in the plate type heat exchanger of the first aspect, the heat transfer plates (53 to 5) are provided.
8) is a wave obtained by alternately forming a first curved portion (81) curved to bulge in one direction in the thickness direction and a second curved portion (82) curved to bulge in the other direction. Form into a mold. Further, the first curved portions of the heat transfer plates (53 to 58) adjacent to each other are formed.
(81,81,...) And the second curved portion (82,82,...) Are brought into contact with each other,
The fluid passages (A, B) are formed between 3 and 58). Further, the first fluid and the second fluid flow through the fluid passages (A, B) adjacent to each other, and the second fluid is cooled to a supercooled state by heat exchange between the two. Then, the first bending portion (81, 8
) And the second curved portion (82, 82,...), The portion facing the second fluid passage (B) is connected to the first fluid passage (A).
It is configured to be brazed with a larger amount of brazing material than the part facing the.

According to this specific matter, the first curved portion (81,81,
…) And the second curved portion (82, 82,…)
At the portion facing the fluid passage (B), the brazing filler metal protrudes greatly. In other words, this brazing material is the passage of the second fluid
(B) is provided with the corner portion closed. Therefore, the means for joining the heat transfer plates (53-58) and the means for closing the corners can be used together.

According to a third aspect of the present invention, in the plate type heat exchanger of the first aspect, the blocking means (40) is formed by a spacer (90) fitted into a corner of the fluid passage (B). The configuration is as follows.

According to a fourth aspect of the present invention, there is provided the plate type heat exchanger according to the third aspect, wherein the plate arrangement has the same structure as that of the second aspect, and the spacer (90)
, The first curved portion (81, 81, ...) and the second curved portion (82, 82, ...)
Of the fluid facing the second fluid passage (B) of the portion facing the second fluid.

A fifth aspect of the present invention is based on the premise of the first aspect of the present invention, wherein a fluid passage through which at least one of the fluid passages (A, B) through which fluids performing heat exchange flow with each other flows. (B) has a substantially circular cross section.

According to a sixth aspect of the present invention, in the plate type heat exchanger of the fifth aspect, each of the heat transfer plates (53 to 58) is provided.
The heat transfer plates (53-58) are provided with a swelling portion (92) swelling in a substantially semicircular cross section toward the back surface side, and the heat transfer plates (53-58) are brought into contact with each other to swell. Department (92,92)
A fluid passage (B) having a circular cross section is formed between the surface sides.

By these specific items, a configuration for preventing the fluid from flowing to the corner of the fluid passage is embodied. In particular, according to the fifth and sixth aspects of the present invention, the corners can be eliminated only by improving the shape of the heat transfer plates (53 to 58), and no separate means is required.

According to a seventh aspect of the present invention, instead of the blocking means (40) in the first aspect of the present invention, the fluid flowing through the corner of the fluid passage (B) and the other portion flow. The configuration is such that a replacement means (41) for replacing the fluid is provided.

According to this specific matter, even when the one according to the present invention is used as a heat exchanger for supercooling one of the fluids, the fluid flowing through the corner is exchanged. At this corner, the degree of supercooling does not significantly increase. For this reason, a situation in which supercooling is eliminated inside the heat exchanger and ice is generated can be avoided.

According to an eighth aspect of the present invention, in the plate heat exchanger according to the seventh aspect, the exchange means (41) is provided with a swirling flow generating member (95, 96, 97, 98)
It consists of.

According to this particular matter, the fluid is swirled by the swirling flow generating members (95, 96, 97, 98) at the inlet of the fluid passage (B). Due to this swirling flow, the fluid flowing through the corner of the fluid passage (B) is exchanged with the fluid flowing through other portions. That is, it is possible to avoid a situation where the fluid flowing in the corner always flows through the corner.

According to a ninth aspect of the present invention, in the plate-type heat exchanger according to the eighth aspect, the swirl flow generating member is provided with a plurality of blades (95a) around a rotation axis (95a) extending in a streamline direction of the fluid. 95b, 95b…) are provided, and these wings (95b, 95b…)
Are configured with rotating blades (95) that rotate around a rotation axis (95a) to generate a swirling flow in the fluid.

According to a tenth aspect of the present invention, in the plate heat exchanger according to the eighth aspect, the swirling flow generating member is
Multiple blades around the axis (96a) extending in the fluid streamline direction
(96b, 96b...) Are provided, and these blades (96b, 96b...) Are constituted by swirling flow generating blades (96) that are curved in the circumferential direction toward the downstream side in the streamline direction.

According to an eleventh aspect of the present invention, in the plate type heat exchanger according to the eighth aspect, the swirling flow generating member is
It is constituted by plate members (97, 98) inserted through the fluid passage (B) and twisted in the streamline direction.

With these specific items, a specific configuration for generating a swirling flow inside the fluid passage (B) can be obtained.

According to a twelfth aspect of the present invention, in the plate heat exchanger according to the seventh aspect, the exchange means is constituted by partially bending the fluid passage (B).

According to this specific matter, the fluid at the corner portion flows toward the center of the fluid passage (B) due to the secondary flow generated at the bent portion. This also makes it possible to exchange the fluid flowing through the corners of the fluid passage (B) with the fluid flowing through other portions.

According to a thirteenth aspect of the present invention, in the plate type heat exchanger according to the seventh aspect, the exchange means is constituted by twisting the fluid passage (B).

The fourteenth aspect of the present invention relates to the thirteenth aspect.
3. The plate type heat exchanger according to claim 1, wherein
Use the same plate layout structure as described, with each plate
(53-58) are integrally superposed, and the whole is twisted in the streamline direction.

According to a fifteenth aspect of the present invention, in the plate heat exchanger according to the seventh aspect, a plate arrangement similar to that of the second aspect is provided, and a fluid passage (B) for each second fluid is provided. The cross-sectional shape is changed along the streamline direction, and the cross-sectional shape in which corners are formed at both ends in the plate thickness direction, and the corners are formed at both ends in a direction orthogonal to the plate thickness direction. The cross-sectional shape to be formed is alternately repeated in the streamline direction.

According to these specific items, each plate (53-
Only by improving the configuration of (58), it is possible to exchange the fluid between the corner and the other part.

[0034]

Embodiments of the present invention will be described below with reference to the drawings.

-Embodiment in which water does not flow into corners of water flow path- The following first to third embodiments are embodiments in which corners of water flow paths in which water easily stays do not exist. . Hereinafter, each embodiment will be described.

(First Embodiment) Hereinafter, a first embodiment of the present invention will be described with reference to the drawings.

First, a regenerative air conditioner (10) using the heat exchanger (50) of the present invention will be described.

As shown in FIG. 1, the regenerative air conditioner (1
0) includes a refrigerant circuit (20) for circulating a refrigerant and a water circuit (30) for circulating water. First, the refrigerant circuit (20) and the water circuit (30) will be described in order.

-Refrigerant circuit (20)-The refrigerant circuit (20) comprises a compressor (21) and a four-way switching valve (22).
The outdoor heat exchanger (23), the outdoor electric expansion valve (EV-1) and the indoor electric expansion valve (EV-2), the indoor heat exchanger (24), and the accumulator (25) are connected to the refrigerant pipe ( A main refrigerant circuit (27), which is connected in order by 26) and is capable of reversible operation, is provided. And the indoor heat exchanger (24) and the indoor electric expansion valve (EV-2)
Is provided in the indoor unit, while other component devices such as the compressor (21) are provided in the outdoor unit.

Further, the refrigerant circulation circuit (20) is provided with a heat storage refrigerant circuit (2a), an ice core circuit (2b), and a hot gas passage (2c). The heat storage refrigerant circuit (2a) is a circuit in which the refrigerant circulates during a cold storage operation or a cooling operation using cold storage, and has one end having an outdoor heat exchanger (23) and an outdoor electric expansion valve (EV-
The other end is between the four-way switching valve (22) and the accumulator (2).
5), a first solenoid valve (SV-1), a preheater (11), a heat storage electric expansion valve (EV-3) as an expansion mechanism,
The supercooling heat exchanger (50) and the second solenoid valve (SV-2) are sequentially connected.

The ice core circuit (2b) includes a water circulation circuit described later.
A circuit for generating ice nuclei in (30), one end of which is between the heat storage electric expansion valve (EV-3) and the supercooling heat exchanger (50) in the heat storage refrigerant circuit (2a), and the other end. Is a subcooling heat exchanger (50)
And a second solenoid valve (SV-2), and a capillary tube (CP) and an ice nucleus generator (13) are connected in order.

The hot gas passage (2c) is used to cool the refrigerant discharged from the compressor (21) during a cooling operation utilizing cold storage heat, etc.
(50), one end of which is on the discharge side of the compressor (21), and the other end of which is the second solenoid valve (SV-) in the heat storage refrigerant circuit (2a).
A third solenoid valve connected between 2) and the subcooling heat exchanger (50)
(SV-3).

-Water circulation circuit (30)-The water circulation circuit (30) is, as shown in FIG.
, A pump (32), a preheater (11), a mixer (33), a subcooling heat exchanger (50), and a subcooling elimination unit (34) by a water pipe (35) as a heat storage medium. A certain water circulation (see the arrow in FIG. 2) is connected in order so as to be possible.

And, the supercooling heat exchanger according to the present invention
(50) is a plate-type heat exchanger, as will be described later, which allows heat exchange between the refrigerant flowing through the refrigerant circulation circuit (20) and the water flowing through the water circulation circuit (30) to perform a cold heat storage operation. Sometimes it is configured to cool the water to a supercooled state.

The preheater (11) is a double-pipe heat exchanger, in which refrigerant flows outside the inner pipe, water flows inside the inner pipe, and ice water flowing from the heat storage tank (31) is removed. Heating and water plumbing
It is configured to melt ice flowing through (35).

The ice nucleus generator (13) is provided with a subcooling heat exchanger (5).
0) is attached to the water pipe (35) at the downstream side, and a part of the water flowing through the water pipe (35) is cooled and iced by the refrigerant in the refrigerant circuit (20), and it is supercooled as ice nuclei. It is configured to supply the solution to the cancellation section (34).

The mixer (33) and the subcooling eliminating section (34)
Each is constituted by a hollow cylindrical container, and is configured such that water introduced in a tangential direction forms a swirling flow. And
The mixer (33) stirs the water and ice heated by the preheater (11) to promote the melting of the ice, while the supercooling elimination unit (34)
Is the ice nucleus generated by the ice nucleator (13) and the supercooled heat exchanger
The supercooling water generated in (50) is stirred to eliminate supercooling.

-Supercooling heat exchanger (50)-Next, the supercooling heat exchanger (50) will be described.

As shown in FIG. 3 (exploded perspective view of the heat exchanger), the subcooling heat exchanger (50) is of a plate type. More specifically, a plurality of heat transfer plates (53 to 58) are overlapped between two frames (51, 52) to form fluid passages (A, B) between the heat transfer plates (53 to 58). doing.

The shapes of the heat transfer plates (53-58) and the flow paths (A, B) formed by the heat transfer plates (53-58) will be described below with reference to FIGS. I do.

As shown in FIG. 4, the heat transfer plates (53 to 58) are formed by pressing a metal flat plate into a corrugated shape by press working. That is, each of the heat transfer plates (53 to 58) swells in one direction (upward in FIG. 5) and the first curved portion (81) which is curved so as to swell in the other direction (downward in FIG. 5). The heat transfer plates adjacent to each other are formed in a corrugated shape in which second curved portions (82) are alternately formed.
The first curved portion (81) and the second curved portion (82) of (53 to 58) are opposed to each other. This allows each heat transfer plate (5
A plurality of fluid passages (A, B) extending vertically are formed between 3 and 58).

As shown in FIG. 3, the plates (53 to 58) have openings (61 to 64) at four corners for forming a fluid flow path. . These openings (61-64) are located at the lower left in FIG.
An opening (61), a second opening (62) located at the upper right, a third opening (63) located at the lower right, and a fourth opening (64) located at the upper left.

The arrangement of the heat transfer plates (53 to 58) will be described below. In FIG. 3, the first plate (53) located closest to the front side has a seal portion (71) formed so as to surround the periphery of each of the openings (61 to 64). This seal (7
1) is such that the periphery of each opening (61 to 64) protrudes toward the frame (51), and a seal portion (71) formed by this protruding portion is formed.
Abuts on the frame (51) so that each of these openings (61 to 6
4) The area around is sealed. Also, this first plate
(53) is an outer peripheral seal portion protruding toward the frame (51).
(70) is provided over the entire periphery.

Also, between the first plate (53) and the second plate (54) located second from the front in FIG. 3, the periphery of the first opening (61) and the second opening (62) is provided. A seal portion (72) is formed so as to surround it. That is, between the first plate (53) and the second plate (54), the third opening (63) and the fourth opening (64) communicate with the water flow path (B), and the two openings (63). 6
3,64), water as the second fluid can be circulated. The first plate (53) and the second plate (5
An outer peripheral seal portion (70) is also formed on the peripheral portion of 4).

On the other hand, between the second plate (54) and the third plate (55) adjacent to the back side of FIG. 3 around the third opening (63) and the fourth opening (64). Around the seal (7
3) is formed. That is, between the second plate (54) and the third plate (55), the first opening (61) and the second opening (62) communicate with the flow path (A) of the refrigerant, and 61,62)
The refrigerant as the first fluid can be circulated between them. The second plate (54) and the third plate (55)
An outer peripheral seal portion (70) is also formed at the peripheral edge of the.

In this manner, each heat transfer plate (53 to 53) is set so that different fluids (water, refrigerant) flow in the flow paths adjacent to each other.
58) are superimposed alternately, and these are
1,72,…). Specifically, as this brazing operation, each heat transfer plate (53 to
58) It is performed by sandwiching a plate-like brazing material between them and vacuum brazing it in a furnace.

Further, one of the frames (5 in FIG. 3)
In (1), pipes (75 to 7) corresponding to the above openings (61 to 64)
8) is connected. Piping (7) corresponding to the first opening (61)
5) is a refrigerant introduction pipe, a pipe (76) corresponding to the second opening (62) is a refrigerant outlet pipe, a pipe (77) corresponding to the third opening (63) is a water introduction pipe, and a fourth opening (64). The corresponding pipe (78) is a water outlet pipe.

With such a configuration, the fluid passages (A, B) formed between the heat transfer plates (53 to 58) are formed.
Has a refrigerant flow path (A) and a water flow path (B) formed alternately. That is, as shown by a solid line arrow in FIG.
Through the refrigerant introduction pipe (75), the refrigerant flows through the refrigerant flow paths (A, A) from the first openings (61, 61,...), And then flows into the second openings (62, 62,...)
Through the refrigerant outlet pipe (76). Similarly, the water flows through each of the third openings (63, 63,...) Through the water introduction pipe (77), as indicated by the dashed arrows in FIG.
(B), and thereafter, the water is led out from the water outlet pipe (78) through each of the fourth openings (64, 64,...). In this way, the refrigerant and the water exchange heat through the heat transfer plates (53 to 58).

The feature of this embodiment is that the first curved portion (81) and the second curved portion (8) of each heat transfer plate (53 to 58) are provided.
2) in the brazing part. In detail, the brazing part consists of the brazing part facing the coolant flow path (A) and the water flow path (B).
There is a brazing part facing. The brazing portion facing the coolant flow path (A) is brazed with a small amount of brazing material (which hardly appears in FIGS. 4 and 5) as in the conventional case. On the other hand, the brazing portion facing the water flow path (B) has a higher brazing material than the brazing portion facing the refrigerant flow path (A).
(C) is present in large amounts. In other words, in this part,
The brazing material (C) protrudes largely laterally from the contact portion between the first curved portion (81) and the second curved portion (82).
That is, a part (corner) of the water flow path (B) is closed by the brazing material (C). That is, the configuration is such that water does not flow to this corner. This constitutes the blocking means (40) according to the present invention. Further, as the brazing material used in the present embodiment, a material suitable for its viscosity and wettability is selected so that the brazing material can easily flow into the corners during the vacuum brazing operation.

-Operation- Next, the operation of the above-described regenerative air conditioner (10) will be described. First, a cold storage operation using the supercooling heat exchanger (50) will be described.

-Cold heat storage operation- In this operation mode, as shown in FIG.
2) is switched to the solid line side, and while the heat storage electric expansion valve (EV-3) is adjusted to the predetermined opening, the other electric expansion valves (EV-1, EV-
2) Close. Also, the first and second solenoid valves (SV-1, SV-
2) is open, and the third solenoid valve (SV-3) is closed.

In this state, in the refrigerant circulation circuit (20), the refrigerant discharged from the compressor (21) exchanges heat with the outside air in the outdoor heat exchanger (23) as shown by arrows in FIG. I do. After that, this refrigerant is decompressed by the heat storage electric expansion valve (EV-3), and then exchanges heat with water in the supercooling heat exchanger (50) to evaporate.
The water is cooled to a supercooled state (eg -2 ° C). Thereafter, the refrigerant passes through the accumulator (25) and the compressor (21)
Inhaled.

In this operation, a part of the refrigerant is
After being diverted from the downstream side of the heat storage electric expansion valve (EV-3) to the ice nucleus circuit (2b), the pressure was reduced by the capillary tube (CP), and then evaporated by the ice nucleus generator (13), and the accumulator (25) was removed. Via compressor
Inhaled in (21). In this ice nucleus generator (13), the refrigerant exchanges heat with the water flowing through the water pipe (35), and the ice blocks are removed from the water pipe (3).
Generated on the inner wall of 5).

On the other hand, in the water circulation circuit (30), water is circulated by driving the pump (32). The water flowing out of the heat storage tank (31) is heated by a preheater (11) via a pump (32), and then stirred by a mixer (33). After that, the water is cooled by exchanging heat with the refrigerant in the subcooling heat exchanger (50), enters a predetermined supercooling state, and flows out of the supercooling heat exchanger (50).
And the supercooled water flowing out of the heat exchanger (50)
Further cooled in the ice nucleus generator (13),
Generated on the inner wall of 5). After that, ice nuclei are generated around the ice block, and the supercooled water containing the ice nuclei is
(34). Then, the ice nuclei and the supercooled water are stirred in the supercooling elimination section (34), and slurry-like ice for heat storage is generated and collected and stored in the heat storage tank (31).

At the time of the main operation, a relatively high-temperature refrigerant flows through the preheater (11), and even if ice flows through the water pipe (35), the preheater (1) may be used.
In step (1), the mixture is heated and melted, and ice is prevented from entering the supercooled heat exchanger (50).

At this time, the flow of water in the supercooling heat exchanger (50) is, as described above, since the corner of the water flow path (B) is closed by the brazing material (C). Flows through portions other than the corners. In other words, the water does not flow particularly to the corners where the flow velocity of the water tends to be slow, so that the water is extremely cooled in this portion and the degree of supercooling does not increase only in this portion. . Therefore, the operation of eliminating the supercooling at the corner can be prevented, and the water flows out of the heat exchanger (50) in the supercooled state and flows out of the supercooling eliminating section.
It will flow toward (34).

As described above, the cold storage operation using the supercooling heat exchanger (50) is performed.

Next, another operation of the regenerative air conditioner (10) will be schematically described.

-Normal Cooling Operation- In this operation mode, only the refrigerant circuit (20) is operated, and the water circuit (30) is not operated.

In this operation mode, the four-way switching valve (22) is switched to the solid line side in FIG. 1, the indoor electric expansion valve (EV-2) is superheated, and the outdoor electric expansion valve (EV-1) is operated. The heat storage electric expansion valve (EV-3) is controlled to a fully closed state and to a fully closed state. On the other hand, each solenoid valve (SV-1, SV-2, SV-3) is closed.

In this state, the refrigerant discharged from the compressor (21) exchanges heat with the outside air in the outdoor heat exchanger (23) and condenses. After that, the refrigerant is decompressed by the indoor electric expansion valve (EV-2), and then evaporates in the indoor heat exchanger (24) to produce an accumulator.
Through (25), it is sucked into the compressor (21). By this circulation operation, the regenerative air conditioner (10) cools the room.

-Cooling operation utilizing cold storage- In this operation mode, as shown in FIG.
2) is switched to the solid line side, the indoor electric expansion valve (EV-2) is controlled to a predetermined opening, and the other electric expansion valves (EV-1, EV-3) are fully opened. Further, the first and third solenoid valves (SV-1 and SV-3) are opened, and the second solenoid valve (SV-2) is closed.

In this state, in the water circulation circuit (30),
The pump (32) is driven to circulate cold water. The cold water in the heat storage tank (31) passes through the pump (32), the preheater (11), and the mixer (33) in this order, and then flows into the supercooling heat exchanger (50). Then, the cold water flowing into the subcooling heat exchanger (50) exchanges heat with the refrigerant and is heated. Thereafter, the heated water flows out of the subcooling heat exchanger (50), and returns to the heat storage tank (31) via the subcooling elimination section (34). The heated water exchanges heat with ice stored in the heat storage tank (31) to be cooled, becomes cold water, flows out of the heat storage tank (31) again, and circulates in the water circulation circuit.

On the other hand, in the refrigerant circuit (20), a part of the refrigerant discharged from the compressor (21) passes through the four-way switching valve (22) as shown by the arrow in FIG. Heat exchanger (2
It flows to 3) and exchanges heat with the outside air in the outdoor heat exchanger (23) to condense. Further, the other discharged refrigerant flows into the supercooling heat exchanger (50) through the hot gas passage (2c), and exchanges heat with cold water circulating in the water circulation circuit (30) to condense. Then, the refrigerant condensed in the outdoor heat exchanger (23) and the subcooling heat exchanger (50) are merged and decompressed by the indoor electric expansion valve (EV-2), and then the indoor heat exchanger (24) After evaporating and cooling the room air, the air is sucked into the compressor (21) through the accumulator (25).

With the above operation, the indoor cooling operation using the cold heat of the ice stored in the heat storage tank (31) is performed.

-Normal Heating Operation- In this operation mode, the water circulation circuit (30) is not operated, and only the refrigerant circulation circuit (20) is operated.

In this operation mode, the four-way switching valve (22) is switched to the broken line side in FIG. 1, the outdoor electric expansion valve (EV-1) is controlled to a predetermined opening, and the indoor electric expansion valve (EV-2) is controlled. Is fully opened, and the heat storage electric expansion valve (EV-3) is controlled to be fully closed. On the other hand, each solenoid valve (SV-1, SV-2, SV-3) is closed.

In this state, the refrigerant discharged from the compressor (21) flows into the indoor heat exchanger (24), exchanges heat with the indoor air, condenses, and heats the indoor air. After that, this refrigerant is decompressed by the outdoor electric expansion valve (EV-1),
In (23), heat exchange with the outside air evaporates. Thereafter, the refrigerant is sucked into the compressor (21) via the accumulator (25). The room is heated by such a circulation operation of the refrigerant.

The operation of the regenerative air conditioner (10) has been described above.

As described above, according to the configuration of the present embodiment, the corners of the water flow path (B) are formed by the heat transfer plates (53 to 5).
8) It was closed by the brazing material (C) for joining the two, and water was not allowed to flow into this part. For this reason, a portion where the water flow velocity is extremely low does not occur in the water flow path (B), and it is possible to prevent the degree of supercooling from being increased in this portion and the generation of ice. As a result, the ice making operation can be performed stably, freezing of the heat exchanger can be avoided, and reliability can be improved.

(Second Embodiment) Next, a second embodiment of the present invention will be described. This embodiment is a modification of the blocking means (40) for closing the corner of the water flow path (B), and the other configuration is the same as that of the above-described first embodiment. Therefore, here, only the configuration for closing the corner of the water flow path (B) will be described.

In the first embodiment described above, the corner of the water flow path (B) is closed by the brazing material (C), but in the present embodiment, another member is interposed instead. Specifically, a spacer (90) made of silicon rubber is interposed.

As shown in FIGS. 8 and 9, the upper and lower surfaces of this spacer (90) have respective heat transfer plates (53).
Curved surfaces (90a, 90b) approximately matching the curved portions (81, 82)
It has become. The vertical surfaces (90c, 90d) connecting the edges of the curved surfaces (90a, 90b) are flat surfaces.

The curved portions of the heat transfer plates (55, 56) are arranged so that the spacer (90) thus configured faces the water flow path (B).
(81,82) are interposed between each other. Also, the refrigerant flow path
The contact portions of the heat transfer plates (54, 55) and (56, 57) facing (A) are brazed as in the first embodiment described above.

With such a configuration, the first
As in the case of the embodiment, the corner of the water flow path (B) is closed, and water does not flow in this part. Therefore, the formation of ice at this corner is prevented, the ice making operation is stabilized, and the heat exchanger is
The reliability can be improved by avoiding freezing in (50). Further, if the spacer (90) is made of an elastic material as in the present embodiment, the spacer (90) is sandwiched between the curved portions (81, 82) of the heat transfer plates (55, 56), so that the transfer is performed. Heat plate (55,5
6) The spacer (90) can be brought into close contact with the spacer (90). Therefore, in this case, the curved portion (92) of the spacer (90)
This does not require a high dimensional accuracy in the shape of the heat transfer plate, and can prevent generation of a water retention portion between the heat transfer plates (55, 56) and the spacer (90).

In this embodiment, each curved surface of the spacer (90) is used.
(90a, 90b) to the curved part (81, 8) of each heat transfer plate (53-58).
It is not always necessary to adhere to 2), and a configuration may be adopted in which the spacer (90) is simply sandwiched between the heat transfer plates (53 to 58).

The material of the spacer (90) is not limited to silicon rubber, and other resin materials and the like can be applied.

(Third Embodiment) Next, a third embodiment of the present invention will be described. This embodiment is for avoiding adverse effects caused by water staying at the corners of the water flow path (B), as in the first and second embodiments described above.

In this embodiment, the shape of each heat transfer plate (53-58) is different from that of each of the above-described embodiments. FIG.
As shown in FIG. 0, each of the heat transfer plates (54 to 57) is formed so that the cross-sectional shape of the water flow path (B) formed by overlapping each other is circular. In other words, each heat transfer plate (5
4 to 57) each have a curved portion (92) having a substantially semicircular cross section,
Flat portions (93) connecting the edges of the curved portions (92, 92) are formed alternately. The heat transfer plates (54 to 57) adjacent to each other are turned upside down so that the front surface and the back surface are joined to each other and are integrally laminated. That is, the curved part (9) of each heat transfer plate (53-56)
2,92) and the flat portions (93,93) face each other, and the respective contact portions are integrally joined by brazing.

With such a configuration, each of the curved portions (9
2,92), a water flow path (B) having a circular cross section is formed. That is, no corner is formed in the water flow path (B).

Therefore, the water flow path (B) of the present embodiment has no water stagnation, and there is no extremely low flow velocity of the water flow path (B). For this reason, even in the configuration of the present embodiment, the generation of ice in the water flow path (B) is prevented, the ice making operation is stabilized, and the reliability is improved by avoiding freezing of the heat exchanger (50). .

In this embodiment, the cross section of the water flow path (B) is set to be circular, but it may be, for example, elliptical as long as it has no corner.

Embodiment provided with a mechanism for generating a swirling flow In the following fourth to seventh embodiments, a swirling flow is generated in the water flow path (B) as the exchange means (41) according to the present invention. This is an embodiment in which a mechanism is provided so that water does not stay at corners. Hereinafter, each embodiment will be described.

(Fourth Embodiment) In this embodiment, a rotating blade (95) for generating a swirling flow in each water flow path (B) is provided at the inlet of the water flow path (B). That is,
Rotating blades (95) are inserted and arranged at the upstream end of a plurality of water channels (B, B,...) Formed between the heat transfer plates (53 to 58) (water channel (B) (The phantom lines in FIG. 11 show the heat transfer plates (53, 54) constituting the above). Hereinafter, the rotating blade (95) will be described.

The rotating blade (95) is, as shown in FIG.
Rotation axis (95) extending parallel to the streamline direction in water flow path (B)
A plurality of blades (95b, 95b, ...) are radially arranged around a). Each wing body (95b, 95b, ...) is approximately 1/4
It is made of a circular flat plate, and for example, 12
The sheets are arranged at equal angular intervals.

The rotating blade (95) is provided with a rotating shaft (95a).
Are rotatably supported by a bearing member (not shown) provided at an inlet portion of the water flow path (B), and further, a driving force of a driving source such as a motor is transmitted to the rotating shaft (95a). It has a configuration. Thus, the exchange means (41) according to the present invention is constituted.

Therefore, when the supercooled water is generated, the driving force from the driving source is transmitted to the rotating shaft (95a), and the rotating blade (95) rotates together with the rotating shaft (95a). Thereby, the water flowing toward each of the water flow paths (B, B,...) Becomes a swirling flow. Therefore, the water at the corner of the water flow path (B) flows from the corner to the center of the water flow path (B) due to the swirling flow, and is replaced with the water at the center. In this way, a situation in which the water at the corners constantly flows through the corners due to the swirling flow in the water flow path (B) is avoided, and the degree of supercooling locally does not increase.

(Fifth Embodiment) In this embodiment, fixed vanes (96) for generating a swirling flow in each water flow path (B) are provided at the inlet of the water flow path (B) as replacement means (41). It is provided. That is, the fixed blade (96) is inserted and arranged at the upstream end of the plurality of water flow paths (B, B,...) Formed between the heat transfer plates (53 to 58) (the water flow path).
The heat transfer plates (53, 54) constituting (B) are shown by phantom lines in FIG. 12). Hereinafter, the fixed blade (96) will be described.

The fixed blade (96) is, as shown in FIG.
A plurality of blades (96b, 96b,...) Are fixed non-rotatably at the inlet of each water flow path (B) around a central axis (96a) extending parallel to the streamline direction in the water flow path (B). ) Is arranged. Each of the blades (96b, 96b,...) Is a substantially triangular flat plate, and is slightly curved in the circumferential direction so that water flowing along the flat plate has a swirling flow. Such a wing body
(96b, 96b,...) Are arranged at equal angular intervals around the central axis (96a), for example.

Therefore, in the present embodiment, when the supercooled water is generated, water is supplied to each blade (96) at the inlet of the water flow path (B).
(b, 96b,...) (see arrows in FIG. 12), whereby the water flowing through each water flow path (B) becomes a swirling flow. For this reason, even in the present embodiment, the water at the corner of the water flow path (B) flows from the corner to the water flow path (B) due to the swirling flow.
Flows to the center of the river and is replaced by the water on the center. In this way, a situation in which the water at the corners constantly flows through the corners due to the swirling flow in the water flow path (B) is avoided, and the degree of supercooling locally does not increase.

(Sixth Embodiment) This embodiment has a configuration in which a torsion tape (97) formed by twisting a metal flat plate along its longitudinal direction is inserted into the water flow path (B). It is. The torsion tape (97) has a width dimension corresponding to an interval dimension (dimension t1 in FIG. 13) between the curved portions (81, 82) of the heat transfer plates (53, 54) indicated by phantom lines in FIG. Have been matched. In other words, the torsion tape (97) has a plurality of end portions abutting against the curved portions (81, 82) of the heat transfer plates (53, 54), and the abutting portions are joined by, for example, brazing. Have been.

Therefore, in the present embodiment, in the water flow path (B), water flows along the shape of the torsion tape (97), and this water becomes a swirling flow, and at the corner of the water flow path (B). Water stagnation disappears.

(Seventh Embodiment) This embodiment also has a configuration in which a torsion tape (98) is inserted into the inside of the water flow path (B). This torsion tape (98) has a heat transfer plate (5
3,54). In other words, the width dimension of the torsion tape (98) is equal to the distance between the corners (dimension t2 in FIG. 14) at the portions entering the respective corners (both ends in the left-right direction in FIG. 14). Each heat transfer plate
In the portion of the (53, 54) that comes into contact with the curved portion (81, 82), the width dimension is different in the longitudinal direction so as to match the distance between the curved portions (dimension t1 in FIG. 14). . In other words, in the lower part of FIG. 14 (a view as seen from the streamline direction), the horizontal part of the twisting tape (98) has a large width dimension and the vertical part has a small width dimension. The entire edge of the torsion tape (98) is joined to the wall surfaces of the heat transfer plates (53, 54) by, for example, brazing.

According to this configuration, the whole of the water flowing through the water flow path (B) can be made to flow as a swirling flow, so that the stagnation of water at the corners can be avoided more reliably.

-Embodiment for Changing Shape of Water Flow Path- In the following eighth to twelfth embodiments, by changing the shape of the water flow path (B) as the exchange means (41) in the present invention, This is an embodiment in which water does not stay at the corners. Hereinafter, each embodiment will be described.

(Eighth Embodiment) As shown in FIG. 15, in the present embodiment, the heat transfer plates (53, 54) are changed to have a shape waving in the thickness direction. In other words, each water channel
(B) meanders vertically in FIG. In this configuration, the water flow velocity in each part of the water flow path (B) changes. That is, a secondary flow is generated due to the effect of the centrifugal force at each curved portion of the water flow path (B). This secondary flow is formed by a pair of circulating flows that face the outside of the bend at the center in the cross section perpendicular to the streamline of the water flow path (B), and go inside the bend near the wall of the water flow path (B). (FIG. 15)
Arrow indicates the direction of the secondary flow at the portion bent to bulge downward). Accordingly, the water at the corners flows along the circulating flow toward the center of the water flow path (B).

As described above, even in the present embodiment, a situation in which the water in the corners constantly flows through the corners is avoided, and the degree of supercooling locally does not increase.

(Ninth Embodiment) As shown in FIG. 16, in the present embodiment, the water flow path (B) is changed to have a shape waving in the width direction of the heat transfer plates (53, 54). That is, each water flow path (B) is configured to meander in the left-right direction in FIG. Also in this configuration, as in the case of the above-described eighth embodiment, a secondary flow occurs at each bent portion (the arrow in FIG. 16 indicates a secondary flow at a portion bent to swell rightward). This causes the water at the corners to flow toward the center of the water flow path.

As described above, even in the present embodiment, a situation in which the water in the corners constantly flows through the corners is avoided, and the degree of supercooling locally does not increase.

(Tenth Embodiment) This embodiment is a composite of the configurations of the eighth and ninth embodiments described above. FIG. 17 shows the shape of one water channel (B) in the present embodiment. As described above, the water flow path (B) of the present embodiment has a configuration in which the direction of water flow is changed by the plurality of bent portions (B-1 to B-6). Specifically, an upward bent portion (B-B) extends from the upstream side (front side in FIG. 17) to the downstream side (back side in FIG. 17).
1) Bend to the right (B-2), 2 bends to the left (B-3, B-4), Bend down (B-5), Bend in the horizontal direction The portion (B-6) is formed continuously.

The flow of water in the cross section at each bent portion (B-1 to B-6) will be described below with reference to FIG. In FIG. 18, the water located at the right corner at the upstream end of the water flow path (B) is moved to any position by the secondary flow generated at each bent portion (B-1 to B-6). The position where the water flows is indicated by a circle so that the user can easily understand whether the water has moved. First, in the cross section aa in FIG. 17, water located at the corner of FIG. 18 (a) flows from the corner to the water flow path (B) from the corner due to the secondary flow of the upward bent portion (B-1). Move to the center side (see FIG. 18B). Then, bend to the right (B-2)
Then, the secondary flow here moves further along the wall surface of the water flow path (B) to the center side of the water flow path (B) (FIGS. 18C and 18D).
reference). Hereinafter, similarly, water is exchanged between the corner and the center of the water flow path (B) by the secondary flow at each bent portion (B-1 to B-6). As described above, even in the present embodiment, a situation in which the water in the corners constantly flows through the corners is avoided, and the degree of supercooling locally does not increase.

(Eleventh Embodiment) As shown in FIG.
In this embodiment, the water flow path (B) is spirally twisted, whereby the water flowing through the water flow path (B) is turned into a swirling flow. That is, FIG. 19 (b) shows the shape of the water flow path (B) having the AA cross section in FIG. 19 (a), and FIG. 19 (c) shows the shape of the water flow path (B) having the BB cross section in FIG. 19 (a). Is shown.

FIG. 20 is a diagram embodying the configuration of the present embodiment, in which several heat transfer plates (53 to 56) superimposed on each other are twisted over the entirety in the streamline direction. FIG. 5 is a diagram in which the cross-sectional shapes of the water and refrigerant flow paths (A, B) in the case of the above are continuously arranged at predetermined intervals in the streamline direction. Thus, the entire heat exchanger (50) is formed in a spiral shape, whereby a swirling flow is generated in each water flow path (B).

With such a configuration, it is possible to avoid a situation where the water in the corner always keeps flowing through the corner.

(Twelfth Embodiment) As shown in FIG.
In this embodiment, the cross-sectional shape of the water flow path (B) gradually changes in the streamline direction. In other words, FIG.
FIG. 21 shows the shape of the water flow path (B) in AA cross section in (a).
(c) shows the shape of the water flow path (B) of the BB cross section in FIG. 21 (a), respectively.

FIGS. 22 to 26 show the water flow path (B) as described above.
7 shows a state of change in the cross-sectional shape of the water flow path (B) and the refrigerant flow path (A) when the cross-sectional shape gradually changes in the streamline direction. That is, the cross-sectional shape of each flow path (B, A) on the downstream side in the flow direction of water and the refrigerant is shown from FIG. 22 to FIG.

As described above, the water flow path (B) has a horizontal dimension longer than the vertical dimension (reference numeral B ′ in FIG. 22), and conversely, the water flow path (B) has a vertical dimension longer than the horizontal dimension (B ′). Reference symbol B ″ in FIG. 22)
Are next to each other. Of these water passages, those having a longer horizontal dimension (B ') are configured such that the vertical dimension gradually becomes longer than the horizontal dimension toward the downstream side, and conversely, the vertical dimension The longer one (B '') has a configuration in which the horizontal dimension gradually becomes longer than the vertical dimension toward the downstream side (see FIGS. 25 and 26). Such a water channel
The state of change in the cross-sectional shape of (B) is alternately repeated over the entire water flow path (B).

Because of such a configuration, for example, in the water flow path (B) having a longer horizontal dimension, corners are formed at both left and right ends, whereas a vertical dimension located downstream thereof is formed. In the longer water flow path (B), corners are formed at both upper and lower ends. Thus, in each water flow path (B), the formation position of the corner is switched over the streamline direction, and the corner is continuously formed over the streamline direction as in the conventional case. Local cooling of the water compared to what would be formed would be avoided.

With such a configuration, it is possible to prevent the degree of supercooling of water from being locally increased due to stagnation of water at the corners, and to prevent freezing of the heat exchanger.

In each of the above-described embodiments, the periphery of the opening (61-64) through which the refrigerant and water in each heat transfer plate (53-58) are circulated and the periphery of the plate are sealed by brazing. However, the present invention may be applied to a device sealed by welding or a gasket.

Further, the plate type heat exchanger (5
0) is not limited to generation of supercooled water for ice making,
It is applicable as a heat exchanger used for various applications.

[0122]

As described above, according to the present invention, the following effects are exhibited. According to the first aspect of the present invention, the sectional shape of the fluid passage through which at least one of the fluid passages through which the fluids performing heat exchange flow with each other is different from that of the plate type heat exchanger with respect to the plate heat exchanger. A circular cross section was formed, and by closing the corner, the flow of fluid at the corner was prevented. For this reason, even when a heat exchanger is used to cool the fluid to a supercooled state, there is no portion in the fluid passage where the degree of supercooling is significantly increased. Therefore, a situation in which supercooling is eliminated inside the heat exchanger and ice is generated can be avoided. As a result, freezing of the heat exchanger is avoided. Particularly, when the plate-type heat exchanger is applied to an apparatus that performs an ice making operation using a supercooling elimination operation, this plate type The ice making operation can be favorably performed while maintaining the original advantage of the mold heat exchanger, that is, maintaining compactness and high efficiency.

According to the second aspect of the present invention, since the corners of the fluid passages are closed by the brazing material for joining the heat transfer plates, the means for joining the heat transfer plates and the corners are used. It can also serve as a closing means, and can realize a configuration that has a simple configuration and does not cause fluid to flow to the corners without increasing the number of parts.

According to the third and fourth aspects of the present invention, the corner is closed by fitting a spacer into the corner of the fluid passage. In the fifth and sixth aspects of the present invention, the fluid passage has a circular cross section so that no corners are present. Thereby, a configuration for preventing the fluid from flowing to the corners of the fluid passage can be embodied. In particular, according to the fifth and sixth aspects of the present invention, it is possible to eliminate corner portions only by improving the shape of the heat transfer plate, and to obtain a highly practical configuration without requiring individual means. Can be

According to the seventh aspect of the present invention, by providing a switching means for switching the fluid flowing in the corner of the fluid passage with the fluid flowing in the other portion, the fluid is brought into a supercooled state. Even when a heat exchanger is used for cooling, the degree of supercooling at the corner is prevented from becoming extremely large. This can also avoid a situation in which supercooling is eliminated inside the heat exchanger and ice is generated, and the reliability of the heat exchanger can be improved.

In the inventions according to the eighth to eleventh aspects, the swirl flow is generated in the fluid, so that the fluid is exchanged between the corner portion of the fluid passage and the other portion. This allows
A situation in which the fluid flowing through the corner of the fluid passage always flows through the corner can be avoided.

According to the twelfth to fifteenth aspects of the present invention, only the structure of each plate is improved, such as twisting the fluid passage or improving the cross-sectional shape, and the gap between the corner and the other part is improved. Fluid can be exchanged, and a situation in which the fluid flowing through the corner of the fluid passage always flows through the corner without using a separate means can be avoided.

[Brief description of the drawings]

FIG. 1 is a diagram showing a refrigerant circulation circuit and a water circulation circuit of a regenerative air conditioner.

FIG. 2 is a diagram showing a water circulation circuit.

FIG. 3 is an exploded perspective view of the plate heat exchanger.

FIG. 4 is a perspective view showing a state in which the heat transfer plates of the first embodiment are overlaid.

FIG. 5 is a diagram illustrating respective flow paths of a refrigerant and water according to the first embodiment.

FIG. 6 is a circuit diagram of a regenerative air conditioner showing a refrigerant circulation operation during a cold heat storage operation.

FIG. 7 is a circuit diagram of the regenerative air conditioner showing a refrigerant circulation operation during a cold storage utilization operation.

FIG. 8 is a perspective view of a spacer according to a second embodiment.

FIG. 9 is a diagram corresponding to FIG. 5 in the second embodiment.

FIG. 10 is a diagram corresponding to FIG. 4 in a third embodiment.

FIG. 11 is a perspective view of a rotating blade according to a fourth embodiment.

FIG. 12 is a perspective view of a fixed blade according to a fifth embodiment.

FIG. 13 is a diagram illustrating a twisted tape according to a sixth embodiment.

FIG. 14 is a diagram illustrating a twisted tape according to a seventh embodiment.

FIG. 15 is a diagram illustrating a shape of a heat transfer plate according to an eighth embodiment.

FIG. 16 is a diagram illustrating a shape of a heat transfer plate according to a ninth embodiment.

FIG. 17 is a perspective view showing the shape of a heat transfer plate according to the tenth embodiment.

FIG. 18 is a diagram for explaining a secondary flow generation state at each cross-section in FIG. 17;

FIG. 19 is a view showing a shape of a heat transfer plate according to the eleventh embodiment.

FIG. 20 is a diagram for explaining a change state of each flow channel in the eleventh embodiment.

FIG. 21 is a view showing a shape of a heat transfer plate according to a twelfth embodiment.

FIG. 22 is a diagram showing a cross-sectional shape at an upstream end portion of each flow channel in the twelfth embodiment.

FIG. 23 is a diagram showing a cross-sectional shape of each flow path in the twelfth embodiment on the downstream side of the position shown in FIG. 22;

FIG. 24 is a view showing a cross-sectional shape of each flow path in the twelfth embodiment on the downstream side of the position shown in FIG. 23;

FIG. 25 is a diagram showing a cross-sectional shape of each flow path in the twelfth embodiment on the downstream side of the position shown in FIG. 24;

FIG. 26 is a diagram showing a cross-sectional shape of each flow path in the twelfth embodiment on the downstream side of the position shown in FIG. 25.

FIG. 27 is a diagram for explaining a flow state of water at a corner of a water flow path.

[Explanation of symbols]

 (40) Blocking means (41) Replacement means (50) Subcooling heat exchanger (plate type heat exchanger) (53-58) Heat transfer plate (90) Spacer (92) Curved section (95) Rotating blade (95a ) Rotating shaft (95b) Blade (96) Fixed blade (96a) Shaft (96b) Blade (97,98) Torsion tape (A) Refrigerant passage (B) Water passage

Claims (15)

[Claims] A plurality of heat transfer plates (53-58) are superimposed to form a fluid passage (A, A) between the heat transfer plates (53-58).
B) is formed, and fluids flowing in the fluid passages (A, B) adjacent to each other exchange heat through the heat transfer plates (53 to 58). The cross-sectional shape of the fluid passage (B) in which at least one of the flowing fluid passages (A, B) flows is a non-circular cross-section having a corner, and the fluid passage (B) has a non-circular cross-section. The plate heat exchanger is provided with a blocking means (40) for closing the corner to block the flow of fluid in the corner. 2. The plate type heat exchanger according to claim 1, wherein the heat transfer plates (53 to 58) are provided with a first curved portion (81) curved so as to bulge in one direction in the thickness direction. A second curved portion (82) curved so as to bulge in the other direction is formed in a wave shape alternately formed, and a first curved portion between adjacent heat transfer plates (53 to 58) is formed. (81, 81,...) And the second curved portions (82, 82,...) Abut against each other, and the abutting portion is brazed to provide a fluid passage (A) between the plates (53-58). , B) are formed, the first fluid and the second fluid flow through the fluid passages (A, B) adjacent to each other, and the second fluid is cooled to a supercooled state by heat exchange between the two. , And the first bending portion (81, 81,...) And the second bending portion (82, 82,...)
Of the contact portion facing the second fluid passage (B),
A plate type heat exchanger characterized in that it is brazed with a larger amount of brazing material than a portion facing the passage (A) of the first fluid. 3. The plate type heat exchanger according to claim 1, wherein the blocking means (40) comprises a spacer (90) fitted in a corner of the fluid passage (B). Heat exchanger. 4. The plate type heat exchanger according to claim 3, wherein the heat transfer plates (53 to 58) are provided with a first curved portion (81) curved so as to bulge in one direction in a plate thickness direction. A second curved portion (82) curved so as to bulge in the other direction is formed in a wave shape alternately formed, and a first curved portion between adjacent heat transfer plates (53 to 58) is formed. (81, 81,...) And the second curved portions (82, 82,...) Are opposed to each other, and the fluid passages (A, B) are interposed between the plates (53 to 58).
The first fluid and the second fluid respectively flow through the fluid passages (A, B) adjacent to each other, and the second fluid is cooled to a supercooled state by heat exchange between the two. The spacer (90) comprises a first curved portion (81,81,...) And a second curved portion.
(82, 82,...), Wherein the plate heat exchanger is fitted only in a portion facing the second fluid passage (B). 5. A plurality of heat transfer plates (53-58) are superimposed to form a fluid passage (A, A) between the heat transfer plates (53-58).
B) is formed, and fluids flowing in the fluid passages (A, B) adjacent to each other exchange heat through the heat transfer plates (53 to 58). A plate type heat exchanger wherein at least one of the flowing fluid passages (A, B) has a substantially circular cross-section. 6. The plate heat exchanger according to claim 5, wherein each of the heat transfer plates (53 to 58) has a bulging portion (92) bulging in a substantially semicircular arc shape in cross section toward the back side. Each of the heat transfer plates (53-58) has a fluid passage (B) having a circular cross section between the front sides of the bulging portions (92, 92) with the front and back surfaces abutting each other. A plate-type heat exchanger characterized by forming: 7. A plurality of heat transfer plates (53-58) are superimposed to form a fluid passage (A, A) between the heat transfer plates (53-58).
B) is formed, and fluids flowing in the fluid passages (A, B) adjacent to each other exchange heat through the heat transfer plates (53 to 58). The cross-sectional shape of the fluid passage (B) through which at least one of the flowing fluid passages (A, B) flows is a non-circular cross-section having a corner, and the corner of the fluid passage (B) is A plate-type heat exchanger, comprising: a switching means (41) for switching between a flowing fluid and a fluid flowing in other parts. 8. The plate heat exchanger according to claim 7, wherein the exchange means (41) is constituted by a swirl flow generating member (95, 96, 97, 98) for generating a swirl flow in the fluid. A plate type heat exchanger characterized by the above-mentioned. 9. The plate-type heat exchanger according to claim 8, wherein the swirling flow generating member has a rotating shaft (95) extending in the fluid streamline direction.
a) A plurality of blades (95b, 95b ...) are provided around the rotating blades (95b, 95b ...) which generate a swirling flow in the fluid by rotating around the rotation axis (95a). 95) A plate type heat exchanger characterized by the above-mentioned. 10. The plate type heat exchanger according to claim 8, wherein the swirling flow generating member is provided with a plurality of blades (96b, 96b,...) Around an axis (96a) extending in a streamline direction of the fluid. A plate-type heat exchanger characterized in that these blades (96b, 96b ...) are composed of swirling flow generating blades (96) which are curved in the circumferential direction toward the downstream side in the streamline direction. 11. The plate heat exchanger according to claim 8, wherein the swirling flow generating member is a plate material (97, 98) inserted through the fluid passage (B) and twisted in the streamline direction. A plate type heat exchanger characterized by the above-mentioned. 12. The plate heat exchanger according to claim 7, wherein the replacement means is constituted by partially bending the fluid passage (B). 13. The plate heat exchanger according to claim 7, wherein the exchange means is constituted by twisting the fluid passage (B). 14. The plate type heat exchanger according to claim 13, wherein the heat transfer plates (53-58) are provided with a first curved portion (81) curved so as to bulge in one direction in the thickness direction. A second curved portion (82) curved so as to bulge in the other direction is formed in a wave shape alternately formed, and the first curved portion of the heat transfer plates (53 to 58) adjacent to each other is formed. (81, 81,...) And the second curved portions (82, 82,...) Are brought into contact with each other,
3 to 58), a fluid passage (A, B) is formed, and the first fluid and the second fluid respectively flow through the fluid passages (A, B) adjacent to each other, and heat exchange is performed between the two fluids. , The second fluid is cooled to a supercooled state, and the plates (53 to 58) are twisted in the streamline direction as a whole in a state where the plates (53 to 58) are integrally superposed. A plate type heat exchanger characterized by the above-mentioned. 15. The plate type heat exchanger according to claim 7, wherein the heat transfer plates (53 to 58) are provided with a first curved portion (81) curved so as to bulge in one direction in the thickness direction. A second curved portion (82) curved so as to bulge in the other direction is formed in a wave shape alternately formed, and a first curved portion between adjacent heat transfer plates (53 to 58) is formed. (81, 81,...) And the second curved portions (82, 82,...) Are brought into contact with each other,
The fluid passages (A, B) are formed between the fluid passages (3, 58), and the first fluid and the second fluid respectively flow through the fluid passages (A, B) adjacent to each other. The second fluid is configured to be cooled to a supercooled state, and the fluid passage (B) of each second fluid changes in cross-sectional shape in the streamline direction, and is formed at both ends in the plate thickness direction. A cross-sectional shape in which a corner is formed and a cross-sectional shape in which a corner is formed at both ends in a direction perpendicular to the thickness direction are alternately repeated in the streamline direction. And plate type heat exchanger.