JP3209115B2 - Heat storage device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to, for example, a method in which a heat storage medium such as water or an aqueous solution is cooled to a supercooled state by a refrigerant, and the supercooled state is eliminated to produce slurry-like ice. The present invention relates to a heat storage device for storing heat as a cold heat source or heating a heat storage medium with a refrigerant and storing hot water as a heat source, and more particularly to an improvement in a heat exchange portion in this type of device.

[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.

In order to cool the room by utilizing the cold heat of the ice stored in the heat storage tank, the cold water cooled by the ice is circulated through a water circulation circuit, and the refrigerant discharged from the compressor is cooled, for example. Heat is exchanged with cold water inside the supercooling heat exchanger to condense. Then, after reducing the pressure of the condensed refrigerant, the refrigerant is evaporated in a heat exchanger installed in the room to cool the room air.

The heat storage medium heat exchange section and the refrigerant heat exchange section are generally integrally formed by a shell-and-tube heat exchanger. That is, for example, a plurality of heat transfer tubes are accommodated in a cylindrical shell, and water is flowed inside the heat transfer tubes and a coolant is flown outside, thereby performing heat exchange between the two. In this type of heat exchanger, the thickness of the heat transfer tube is set to be large in order to prevent the heat transfer tube from being damaged by volume expansion when ice is generated in the heat transfer tube. Alternatively, a deformable resinous rod is inserted into the inside of the rod so that the volume expansion can be absorbed by the deformation of the rod.

The water pipe on the outlet side of the heat storage tank has:
A preheater is provided in order to prevent the ice from flowing into the heat exchanger when the ice flows out of the heat storage tank and causing freezing. This preheater is a heat exchanger having a double-tube structure, in which water containing ice is exchanged with high-temperature refrigerant to give heat to the water to melt the ice.

[0007]

However, an ice storage device having a heat exchange section such as a supercooled water generating heat exchanger or a preheater as described above has a problem in that the entire device is required for the following reasons. It was difficult to reduce the size.

That is, when a shell-and-tube type heat exchanger is used for generating supercooled water, as described above, the thickness of the heat transfer tube is set large, or a rod is inserted into the inside thereof. Therefore, in order to set the cooling performance to be high while securing a sufficient flow rate of water, it is necessary to increase the size of the heat exchanger, which leads to an increase in the size of the entire apparatus.

Further, in the preheater, the ice cannot be reliably melted by simply heating the water. Therefore, a stirring vessel for stirring the heated water and ice is provided downstream of the preheater. Needed. That is, a preheater and a stirring vessel are required on the outlet side of the heat storage tank, and a space for disposing the preheater and the stirring vessel is required. Therefore, it has been difficult to reduce the size of the apparatus.

As described above, it is difficult to reduce the size of the entire heat exchange device used in the conventional ice heat storage device. It was necessary to improve the replacement part.

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 heat exchange portion of a heat storage device to achieve a compact configuration while maintaining sufficient performance. An object of the present invention is to reduce the size of the entire apparatus.

[0012]

In order to achieve the above object, the present invention relates to a heat exchange portion of a heat storage device for performing heat exchange between a heat storage medium such as water and a refrigerant to store heat in the heat storage medium. On the other hand, by adopting a plate-type heat exchanger, a compact configuration can be realized while maintaining sufficient performance.

Specifically, the means of the invention according to claim 1 includes a heat storage circuit (30) that includes a heat storage tank (31) and circulates a heat storage medium, and a refrigerant circuit (20) that circulates a refrigerant. Prepared,
It is premised on a heat storage device that cools or heats the heat storage medium with the above-described refrigerant and then stores the heat storage medium in the heat storage tank (31) to store heat.

A heat exchange means (50) for exchanging heat between the heat storage medium and the refrigerant is provided, and the heat exchange means (50) comprises:
A plurality of heat transfer plates (53-58) are overlapped to form a heat storage medium flow path (B) and a refrigerant flow path (A) between the heat transfer plates (53-58). The heat storage medium and the refrigerant flowing through the passages (A, B) are constituted by a plate-type heat exchanger that exchanges heat via heat transfer plates (53 to 58).

According to this specific matter, the heat exchange portion of the heat storage device can be made compact while maintaining high heat exchange performance. Therefore, downsizing can be achieved while maintaining the performance of the entire apparatus.

Further , the invention according to claim 1 is characterized in that the heat exchange means (50) is a subcooling heat exchanger that cools the heat storage medium to a supercooled state by evaporating refrigerant,
The ice making is performed by eliminating the supercooled state of the heat storage medium supercooled in step 0).

That is, according to the present invention, the supercooling heat exchanger (50) of the ice heat storage device for performing ice making by the supercooling elimination operation and thereby storing the cold heat is configured according to the first aspect of the present invention. And high ice making efficiency can be realized.

Further, the invention according to claim 1 is characterized in that the supercooling heat exchanger (50) has a turbulence such that the supercooled heat storage medium positioned downstream of the heat storage medium in the flow direction does not eliminate the supercooling. A heat exchange section (F) for flowing the heat storage medium in a small state, and a heat exchange section for flowing the heat storage medium in a state of being more turbulent than the heat exchange section (F) and located upstream of the heat exchange section (F). (E).

According to this specific matter, the heat storage medium is rapidly cooled in the heat exchange section (E) in which the heat storage medium flows in a state of large turbulence, while the heat exchange section (F) in which the heat storage medium flows in the state of small turbulence. The heat storage medium is gradually cooled, and even if the heat storage medium is in a supercooled state, it does not disappear. That is, by reducing the turbulence of the flow of the heat storage medium in the supercooled state, the elimination of the supercooling due to the stirring action is suppressed.

[0020] According to a second aspect of the invention, the heat storage device according to the first aspect, projecting the heat transfer plates (53-58), and in the other direction first protrusion protruding in one direction in the thickness direction The second protrusions are formed in a wave shape alternately formed, and flow paths (A, B) are formed between the plates (53 to 58). Further, the flow path (B) of the heat storage medium formed between the respective plates (53 to 58)
In addition, a heat exchange section (E) for flowing the heat storage medium in a state of large turbulence and a heat exchange section (F) for flowing the heat storage medium in a state of small turbulence are provided continuously. In the heat transfer plate (53-58), where the heat exchange medium (E) for flowing the heat storage medium in a state of large turbulence is formed, the extending direction of each protruding portion is the heat transfer plate (53-58).
To form a herringbone-shaped projection extending in a direction at a predetermined angle with respect to the longitudinal direction. On the other hand, in a portion where the heat exchange medium (F) through which the heat storage medium flows with little turbulence is formed, the extending direction of each protruding portion is extended along the longitudinal direction of the heat transfer plates (53 to 58).

According to this specific matter, it is possible to obtain a specific configuration for forming the flow path (B) and a portion in which the flow is disturbed in the flow path (B).

The third aspect of the present invention is directed to the first aspect.
3. The heat storage device according to 2, wherein the heat storage circuit (30) includes a heat storage tank (31) for storing the heat storage medium, a circulating means (32) for pumping the heat storage medium, and a supercooling heat exchanger capable of supercooling the heat storage medium. Table (50)
Are connected by a circulation pipe (35). Also, heat storage tank
After the heat storage medium taken out of (31) is brought into a supercooled state by the supercooled heat exchanger (50), the supercooled state is eliminated and ice is generated. And a preheating heat exchange section (D) through which a high-temperature refrigerant for heating the heat storage medium taken out of the heat storage tank (31) flows into the supercooling heat exchanger (50), and this preheating heat exchange section
And a cooling heat exchange section (C) through which a low-temperature refrigerant flows to cool the heat storage medium heated by the refrigerant of (D) to a supercooled state.

According to this specific matter, when ice is mixed in the heat storage medium taken out of the heat storage tank (31), this heat storage medium first flows through the preheating heat exchange section (D) of the refrigerant flow path (A). Heated by the hot refrigerant, which causes the ice to melt. Thereafter, the refrigerant is cooled to a supercooled state by a low-temperature refrigerant flowing through the cooling heat exchange section (C). Therefore, a situation in which ice present inside the heat storage medium in a supercooled state serves as a nucleus for eliminating supercooling and causes the heat exchanger to freeze can be avoided.

According to a fourth aspect of the present invention, in the heat storage device of the third aspect , a preheat heat exchange section (D) and a cooling heat exchange section are provided.
(C) is connected by a pressure reducing pipe (79), and the pressure reducing pipe (7
In 9), a pressure reducing mechanism (EV-3) for reducing the pressure of the refrigerant derived from the preheating heat exchange section (D) will be provided. Then, after the refrigerant that has exchanged heat with the heat storage medium in the preheat heat exchanger (D) is depressurized by the decompression mechanism (EV-3), the refrigerant exchanges heat with the heat storage medium in the cooling heat exchange section (C) to evaporate. ing.

According to this specific matter, the refrigerant that has contributed to the melting of ice in the heat storage medium in the preheat heat exchange section (D) can be used for supercooling generation in the cooling heat exchange section (C), and the refrigerant can be effectively used. Becomes

[0026]

BEST MODE FOR CARRYING OUT THE INVENTION (First Embodiment) A first embodiment of the present invention in which a heat exchanger for generating supercooled water is improved will be described below with reference to the drawings.

-Regenerative air conditioner (10)-First, the regenerative air conditioner (10) will be described.

As shown in FIG. 1, a 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), and a supercooling heat exchanger.
(50) and the second solenoid valve (SV-2) are connected in order.

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 heat storage, 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) has a heat storage tank (31) 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 above-mentioned 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 supercooling heat exchanger (50) is of a plate type. More specifically, a plurality of heat transfer plates (53-58) are overlapped between two frames (51, 52) to form fluid passages (A, B) between the heat transfer plates (53-58). are 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.

Each of the heat transfer plates (53 to 58) is formed by pressing a metal flat plate into a corrugated plate by press working. These heat transfer plates (53-58) are composed of a first type plate (53,55,57) and a second type plate (54,5
6,58) are alternately superimposed, and these are integrally joined by brazing. FIG. 4 shows a state in which the heat transfer plates (53 to 58) are overlapped in a state where the first type plate (53) is located on the front side, and FIG. 5 shows a state in which the second type plate (54) is placed. Are shown respectively.

First, the first type plate (53) will be described. As shown in FIG. 4, the plate (53) has openings (61 to 6) for forming a fluid flow path at four corners.
4) is formed, and the other parts are formed in a corrugated plate shape. As the wave shape, peaks (bold line portions in FIG. 4) as first protrusions and valleys (thin line portions in FIG. 4) as second protrusions are alternately formed. I have. The wave shape will be described in detail. An upwardly inclined portion (53a) disposed so that the extension direction of the peak and the valley is inclined upward toward the right in FIG. 4, and is inclined downward. The so-called herringbone shape in which the lower inclined portions (53b) arranged as described above are alternately formed.

On the other hand, as shown in FIG. 5, the second type plate (54) is similar to the first type plate (53),
At the four corners, openings (61 to
64) are formed, and the other portions are formed in a corrugated plate shape. And this second type plate (5
4) is different from the first type in the wave shape.

More specifically, the second type plate (54) is also formed in a herringbone shape, but the extending direction of the peaks and valleys is different from that of the first type. That is, the first type plate (53) described above
As shown in FIG. 5, a herringbone shape is formed in the order of an upper inclined portion (53a) and a lower inclined portion (53b) from the left end, while the second type plate (54) is as shown in FIG. Further, from the left end, a herringbone shape is formed in the order of the lower inclined portion (54b) and the upper inclined portion (54a).

Next, the arrangement of the heat transfer plates (53 to 58) will be described. In FIG. 3, the first plate (53) as the first type plate 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). The seal portion (71) is configured such that the periphery of each opening (61 to 64) protrudes toward the frame (51), and the seal portion (71) formed of the protruding portion contacts the frame (51). Thus, the periphery of each of the openings (61 to 64) is sealed.

Further, between the first plate (53) and the second plate (54) as the second type plate located second from the front in FIG. 3, the first plate located at the lower left in FIG. The second opening (6) located at the upper right and around the opening (61)
A seal portion (72) is formed so as to surround the periphery of 2). That is, the first plate (53) and the second plate (54)
The third opening (63) located at the lower right in FIG.
Fluid (water) is allowed to flow between the first opening (64) and the fourth opening (64) located at the upper left. On the other hand, the second plate (54)
And a third plate (55) adjacent to the back side in FIG. 3 so as to surround the periphery of the third opening (63) and the periphery of the fourth opening (64). Are formed. That is, between the second plate (54) and the third plate (55), the first plate
Fluid (refrigerant) can flow between the opening (61) and the second opening (62). In this way, the first type heat transfer plates (53, 55, 57) and the second type heat transfer plates (54, 56, 58) allow different fluids (water, refrigerant) to flow in adjacent flow paths.
Are alternately superimposed, and these are integrally brazed. This brazed portion is at least a peripheral portion of each of the seal portions (71, 72, 73) and each of the heat transfer plates (53 to 58).

FIG. 6 shows an overlapping state of the heat transfer plates (53 to 57). The flow state of the fluid in the overlapping state will be described. For example, in the flow path formed between the first plate (53) and the second plate (54), the first plate (53 The fluid flowing in the region (upper region in FIG. 6) near the peak of the second plate (54) flows along the direction in which the peak of the first plate (53) extends. On the other hand, the second
The fluid flowing in the area near the plate (54) (the lower area in FIG. 6) passes over the valley (projecting downward) of the first plate (53), and the peak of the second plate (54). It flows along the extension direction of the part. That is, in each of the flow paths (A, B), the fluid flows in a state of large turbulence (for example, a turbulent state), and heat exchange is performed with a high heat transmission coefficient.

Further, one of the frames (5)
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.

Due to such a configuration, the flow paths (A, B) formed between the heat transfer plates (53 to 58) are formed by the refrigerant flow path (A) and the water flow path (B). Are formed alternately. That is, the refrigerant flows from the first openings (61, 61,...) Through the refrigerant introduction pipe (75) through the refrigerant flow path, as indicated by solid arrows in FIG.
(A, A), and then through the second openings (62, 62,...) Through the refrigerant outlet pipe (76). Similarly, the water flows through the water inlet pipe (77) through each of the third openings (63, 63,...) Through the water flow path (B) as indicated by the dashed arrow in FIG. The water is led out from the water outlet pipe (78) through the openings (64, 64, ...). Thus, the refrigerant and the water are configured to perform heat exchange via the heat transfer plates (53 to 58).

-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 circuit (20), the refrigerant discharged from the compressor (21) exchanges heat with the outside air in the outdoor heat exchanger (23) as shown by the arrow 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, 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).

In this operation, a relatively high-temperature refrigerant flows through the preheater (11), and even if ice flows out of the heat storage tank (31), it is heated and melted by the preheater (11), and the supercooled heat is released. Exchanger (50)
Ice is prevented from being mixed into the air.

At this time, the flow of the refrigerant and the water in the supercooling heat exchanger (50) is, as described above, in each of the flow paths (A, B), the refrigerant and the water are both flowing in a state of large turbulence. For this purpose, heat exchange takes place with a high heat transfer coefficient, and the water is cooled rapidly, for example to -2 ° C. The supercooled water flows out of the subcooling heat exchanger (50).

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

As described above, in this embodiment, a plate-type heat exchanger (50) for generating supercooled water is used, so that the thickness of the heat transfer tube is reduced as in the conventional shell-and-tube type. It is not necessary to increase the size of the apparatus or to increase the size of the apparatus due to the necessity of inserting a rod into the apparatus, thereby reducing the size of the entire apparatus.

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 turned on. 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 circulation 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 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 to 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, since the generation portion of the supercooled water for making ice is constituted by the plate heat exchanger (50), the shell-and-tube type heat exchange as in the prior art is performed. As with the exchanger,
In order to secure cooling performance and reliability, it is possible to avoid a situation in which the heat transfer tube is set to a large plate thickness or a bar is inserted therein to cause an increase in size. For this reason,
It is possible to achieve both compactness and high efficiency of the supercooled water generation unit, and it is possible to reduce the overall size while maintaining the performance of the device.

-Experimental Example- Next, an experiment performed to confirm the effect of the present embodiment and the result thereof will be described. This experiment compares the sizes of a shell and tube heat exchanger and a plate heat exchanger having the same capacity.

More specifically, a heat exchanger of each type (shell and tube type and plate type) having a size necessary for lowering the water temperature of the water flowing at a flow rate of 150 liters per minute by 2.5 degrees is selected. It was done by doing.

According to this, the required volume of the shell-and-tube heat exchanger was 3.95 × 10 ⁴ cm ³ . In contrast, the required volume of the plate heat exchanger was 1.05 × 10 ⁴ cm ³ .

As described above, when the shell-and-tube type is compared with the plate-type, the plate-type type requires only about 1/4 the volume of the shell-and-tube type to exhibit the same performance. . Thereby, the plate type heat exchanger is compared with the shell and tube type heat exchanger.
This confirms that a high performance can be demonstrated with a compact configuration.

As the operation mode of the regenerative air conditioner of this embodiment, in addition to the operation modes described above, a heat storage operation and a heating operation using the heat storage may be performed.

(Second Embodiment) Next, a second embodiment of the present invention will be described. In this embodiment, the preheater (11) is configured as a plate-type heat exchanger. Thus, the plate type heat exchanger is preheated (11)
The configuration of the heat exchanger itself when used as is the same as that of the plate heat exchanger described in the above-described first embodiment, and a description thereof will be omitted.

In the case of the present embodiment, as the fluid flowing through each flow path (A, B) during the cold storage operation, the refrigerant flow path (A) has a relatively high temperature derived from the outdoor heat exchanger (23). Refrigerant flows,
On the other hand, water (water possibly containing ice) taken out of the heat storage tank (31) flows through the water flow path (B). Then, these fluids exchange heat with each other while flowing in each of the flow paths (A, B) in a state of great turbulence, so that heat is efficiently given to water.

Therefore, when the preheater (11) is configured as a plate-type heat exchanger as in this embodiment, the stirring is performed downstream as in the case where a conventional double tube structure is applied. The ice can be efficiently melted without disposing a container. For this reason, the heat exchange portion for melting the ice flowing out of the heat storage tank (31) can be made compact, which can also reduce the size of the entire apparatus.

In the first and second embodiments described above, the case where the supercooling heat exchanger (50) and the preheater (11) are configured as plate heat exchangers has been individually described. Both may be constituted by a plate heat exchanger.

(Third Embodiment) Next, a third embodiment of the present invention will be described. In this embodiment, both the subcooling heat exchanger (50) and the preheater (11) are plate-type heat exchangers, and both are integrated.

The first part of the heat exchanger (50, 11) of the present embodiment
9 and 10 show the heat transfer plates (55, 54) of the second type. FIG. 9 shows a plate (55) of the first type,
0 indicates a second type of plate (54), respectively.

First, the first type plate (55) will be described. As shown in FIG. 9, the plate (55) is such that the coolant flows toward the near side and the water toward the far side in FIG. The plate (55) has a supercooling section (55c) on the upper side and a preheating section (55d) on the lower side. The ratio of the height of the supercooling section (55c) to the height of the preheating section (55d) is set to about 3: 1, and the area of the supercooling section (55c) is larger. Each part (55c, 55d) is made of a herringbone type corrugated sheet similar to that of the above-described embodiment, and the boundary between the supercooling part (55c) and the preheating part (55d) is shown in FIG. A partition protrusion (55e) is formed as a flow path partition portion bulging toward the front of the drawing.

At three corners of the subcooling section (55c), openings (61, 62, 64) for forming a fluid flow path are provided.
Is provided. In other words, the lower left opening (61) in FIG. 9 of the subcooling section (55c) is the opening for introducing the low-temperature refrigerant (the first opening).
(Corresponding to the first opening in the embodiment), and
The upper right opening (62) is a low-temperature refrigerant outlet opening (corresponding to the second opening in the first embodiment), and the upper left opening (64) is a water outlet opening (the first opening in the first embodiment). (Corresponding to 4 openings).

Openings (65, 66, 63) for forming a fluid flow path are also formed at three corners of the preheating section (55d). That is, the lower left opening (65) in FIG.
Is the opening for introducing the high-temperature refrigerant, and the opening at the upper right (66)
Is the opening for deriving the high-temperature refrigerant, and furthermore, the opening at the lower right (63)
Denotes an opening for water introduction (corresponding to the third opening in the first embodiment).

On the other hand, as shown in FIG. 10, the second type plate (54) is such that water flows toward the near side and refrigerant flows toward the far side in FIG. Similarly to the first type plate (55), openings (61 to 66) are formed in each part, and the other parts are formed in a corrugated plate shape. In addition, this plate (54) also has a supercooling section (5
4c) is provided with a preheating portion (54d) in a lower portion, and a boundary portion between the supercooling portion (54c) and the preheating portion (54d) is a partition protrusion (54e ) Is formed.
And, as in the first embodiment described above, the second type of plate (54) has a different herringbone shape from the first type.

The two types of heat transfer plates (53 to 58) having such a configuration are alternately arranged in the same manner as in the first embodiment described above, whereby the preheater (11) and the subcooler are supercooled. A heat exchanger integrated with the heat exchanger (50) is configured. In this state, in the refrigerant flow path (A), the bulging sides of the partitioning projections (54e, 55e) are joined to each other, whereby
Supercooling space corresponding to the subcooling section (55c) in the refrigerant passage (A)
(C) and a preheating space (D) corresponding to the preheating section (55d). In addition, as shown in FIG.
The opening (61) for introducing the low-temperature refrigerant is connected by a pipe (79). Then, the heat storage electric expansion valve (E
V-3) is provided.

Next, the operation of the heat exchanger (11, 50) during the cold storage operation of the present embodiment will be described. Water circulation circuit (30)
In this case, the water extracted from the heat storage tank (31) flows into the water flow path (B) from the water introduction opening (63) as shown by the arrow in FIG. 10, and is discharged from the water outlet opening (64). You. On the other hand, in the refrigerant circulation circuit (20), the relatively high-temperature refrigerant that has passed through the outdoor heat exchanger (23) passes through the high-temperature refrigerant introduction opening (65) as indicated by the arrow in FIG.
Then, the water is introduced into the preheating space (D), where heat is exchanged with water taken out of the heat storage tank (31). That is, the water is heated by the refrigerant, and when the water contains ice, the ice is melted. In the water flow path (B), since each heat transfer plate (53-58) is formed of a corrugated plate, the water flows in a state of large turbulence, so that the melting of the ice is performed efficiently. Will be

The refrigerant flowing out of the high-temperature refrigerant outlet opening (66) into the pipe (79) through the preheating space (D) is decompressed by the heat storage electric expansion valve (EV-3), and then is cooled. 61)
From the water to the supercooling space (C), where heat exchange is performed with the water flowing through the water flow path (B). That is, water is cooled by the refrigerant, and the water enters a supercooled state, and thereafter flows from the water outlet opening (64) toward the supercooling elimination section (34). That is, in the present embodiment, the water flowing in the water flow path (B) is heated in the preheating section (54d), and after the mixed ice is melted, cooled in the supercooling section (54c), and becomes a supercooled state. After that, it flows out of the heat exchanger.

As described above, in the present embodiment, a portion for melting ice mixed with water taken out of the heat storage tank (31) and a portion for cooling water to a supercooled state are integrally formed, and a water flow path is provided.
In (B), the water is made to flow in a turbulent state.
Therefore, there is no need for a space for separately disposing the preheater (11) and the subcooling heat exchanger (50) as in the first embodiment described above. Also, no mixer (33) is required. Therefore, the overall size of the apparatus can be further reduced.

In this embodiment, the refrigerant flow path is formed by joining the partition projections (54e, 55e) of the heat transfer plate (54, 55).
(A) is divided into a supercooling space (C) and a preheating space (D) .Instead of this configuration, a heat insulating partition member (54, 55) is interposed between the heat transfer plates (54, 55). Super cooling space
(C) and a preheating space (D) may be formed. In this case, heat exchange between the refrigerant flowing in the supercooling space (C) and the refrigerant flowing in the preheating space (D) is suppressed, and the preheating space (D)
The melting of the ice by the refrigerant flowing through the supercooled space and the generation of the supercooled water by the refrigerant flowing through the supercooled space (C) can be performed efficiently.

(Fourth Embodiment) Next, a fourth embodiment of the present invention will be described with reference to FIGS. This embodiment is different from the third embodiment described above in that the supercooling heat exchanger (50) and the preheater (11) are integrated, and the supercooling section of the heat transfer plates (54, 55) is also provided. (54c, 5
This is an improvement of the wave shape of 5c). Therefore, in the present embodiment, the same components as those in the above-described third embodiment are denoted by the same reference numerals in FIGS. 11 and 12, and the description thereof is omitted.

Hereinafter, each plate which is a characteristic part of the present embodiment will be described.
The configuration of the supercooling section (54c, 55c) of (54, 55) will be described. The supercooling section (55c) of the first type plate (55) has an upstream portion (lower portion) and a downstream portion (upper portion) from an intermediate position in the fluid flow direction (vertical direction in FIG. 11). Have different wave shapes.

The wave shape of the upstream portion will be described in detail. As for the wave shape of the upstream portion, the extension direction of the peaks and valleys is inclined upward toward the right in FIG. Up slope (5
5a) and the downstream slope that is arranged to incline downward
(55b) are formed alternately with a so-called herringbone shape.

On the other hand, as for the wave shape of the downstream portion, the extending direction of the peaks and the valleys is vertical. Further, at the boundary between the upstream portion and the downstream portion, the corrugated sheet is bent so that the peaks and the valleys thereof are continuous.
FIG. 13A is a sectional view taken along the line II in FIG.
3 (b) is a sectional view taken along line II-II in FIG.

On the other hand, as shown in FIG. 12, the supercooling portion (54c) of the second type plate (54) also has a fluid flow direction (FIG. 12) similar to the first type plate (55). The wave shape is different between the upstream portion (lower portion) and the downstream portion (upper portion) of the intermediate position (up and down direction). The second type of plate (54) is different from the first type in the wave shape in the upstream portion.

With such a configuration, the flow of the refrigerant and water in the subcooling heat exchanger (50) during the cold storage operation is such that the refrigerant and water are both turbulent upstream of the subcooling sections (54c, 55c). Due to the large flow, the heat exchange takes place with a high heat transfer coefficient, the water is cooled rapidly and in this area (E), for example, to 0 ° C.

Thereafter, the refrigerant and water flowing out of the turbulent region (E) flow into the turbulent region (F), and exchange heat in this region (F). here,
The heat transfer coefficient is not so high as the above-mentioned area of large turbulence (E), the water is gradually cooled, and the area of small turbulence (F)
Is cooled to, for example, -2 ° C. The supercooled water flows out of the supercooling heat exchanger (50) with little disturbance.

As described above, in the downstream area of the water flow path (B), there is no significant change in the water temperature, so that the temperature of the water taken out of the heat exchanger (50) can be set relatively easily.
Also, since the supercooled water does not flow in a turbulent state in this part, the elimination of this supercooling is also suppressed, and the occurrence of freezing inside the supercooled heat exchanger (50) can be avoided. As a result, a stable supercooled water generation operation can be performed.

In the present embodiment, the subcooling heat exchanger (50) and the preheater (11) are integrated, and the region constituting the supercooling heat exchanger (50) has a large turbulence region (E). Small area of disturbance
(F) and each of these areas (E, F)
The preheater (11) may be constituted by a separate plate-type heat exchanger.

(Fifth Embodiment) Next, a fifth embodiment as a modification of the refrigerant circuit (20) will be described. Note that, in the present embodiment, only portions different from the refrigerant circuit (20) of the above-described first embodiment will be described.

As shown in FIG. 14, the refrigerant circuit (20) of the present embodiment includes a second four-way switching valve (22) and an outdoor heat exchanger (23) of the first embodiment. A switching valve (90) is provided, and the second four-way switching valve (90) is connected to the port (P1) connected to the first four-way switching valve (22) and the outdoor heat exchanger (23). In addition to the port (P2), the supercooling heat exchanger (50) in the heat storage refrigerant circuit (2a)
And a second port (P4) connected to the second solenoid valve (SV2) via a hot gas passage (2c), and a port (P4) connected to an accumulator (25) via a refrigerant recovery passage (91). ing. A switching state in which the first four-way switching valve (22) communicates with the outdoor heat exchanger (23) and connects the hot gas passage (2c) and the refrigerant recovery passage (91) (shown by a solid line in FIG. 14) Switching state)
And a switching state in which the first four-way switching valve (22) communicates with the hot gas passage (2c) and connects the outdoor heat exchanger (23) and the refrigerant recovery passage (91) (shown by a broken line in FIG. 14). (Switching state).

In this embodiment, the outdoor electric expansion valve (EV-1)
Is provided closer to the outdoor heat exchanger (23) than the connection position of the heat storage refrigerant circuit (2a) in the refrigerant pipe (26), and closer to the indoor unit than the connection position of the heat storage refrigerant circuit (2a). A fourth solenoid valve (SV-4) is provided.

Further, in the present circuit (20), the upstream end of the ice nucleus circuit (2b) is located between the preheater (11) and the heat storage electric expansion valve (EV-3), and the downstream end is located at the second solenoid valve (EV). SV-2) and an accumulator (25). The ice core circuit (2b) has the fifth
An electromagnetic valve (SV-5) is provided.

Further, a plurality of indoor units are provided, each of which includes an indoor electric expansion valve (EV-2) and an indoor heat exchanger (24), and the units are connected in parallel with each other.

-Operation- Next, the operation of the regenerative air conditioner (10) according to the present embodiment will be described.

-Cold heat storage operation- In this operation mode, both the first four-way switching valve (22) and the second four-way switching valve (90) are switched to the solid line side in FIG. 3) is set to a predetermined opening degree, and the outdoor electric expansion valve (EV-1) is set to a fully opened state. Also, first, second and fifth solenoid valves
(SV-1, SV-2, SV-5) are opened, and the fourth solenoid valve (SV-4) is closed.

In this state, as in the case of the cold storage operation in the first embodiment, the refrigerant discharged from the compressor (21) exchanges heat with the outside air in the outdoor heat exchanger (23) and condenses. Then, the pressure is reduced by the heat storage electric expansion valve (EV-3). Thereafter, the water is exchanged with water in the supercooling heat exchanger (50) to evaporate, and the water is cooled to a supercooled state (for example, -2 ° C). The water circulation circuit (3
The water circulation operation in (0) is the same as in the first embodiment.

-Normal Cooling Operation- In this operation mode, both the first four-way switching valve (22) and the second four-way switching valve (90) are switched to the solid line side, and each indoor electric expansion valve is switched.
(EV-2) is superheated. In addition, outdoor electric expansion valve (EV-1)
Is fully opened, and the heat storage electric expansion valve (EV-3) is controlled to be fully closed. On the other hand, the fourth solenoid valve (SV-4) is opened, and the other solenoid valves (SV-1, SV-2, SV-5) are closed.

In this state, as in the case of the normal cooling operation in the first embodiment, the refrigerant circulates to cool the room.

In the operation mode, the first four-way switching valve (22) is moved to the solid line side.
The second four-way switching valve (90) is switched to the broken line side, the indoor electric expansion valve (EV-2) is controlled to a predetermined opening, and the heat storage electric expansion valve (EV-
3) Fully open and fully close the outdoor electric expansion valve (EV-1). Further, the second and fifth solenoid valves (SV-2, SV-5) are closed, and the other solenoid valves (SV-1, SV-4) are opened.

In this state, all of the refrigerant discharged from the compressor (21) passes through the four-way switching valves (22, 90) and the hot gas passage (2c) as shown by arrows in FIG. After that, it flows to the supercooling heat exchanger (50) and exchanges heat with cold water circulating in the water circulation circuit (30) to condense. Then, the condensed refrigerant is decompressed by the indoor electric expansion valve (EV-2), evaporated by the indoor heat exchanger (24), cooled the indoor air, and then passed through the accumulator (25) to the compressor (21). ).

As described above, in the cooling operation using the main cold storage energy,
By preventing the refrigerant from flowing to the outdoor heat exchanger (23), only cold water is used as the heat of condensation, and the cold heat of ice in the heat storage tank (31) is effectively used. Tank
(31) No ice remains inside. In other words, when all the ice in the heat storage tank (31) is melted in the cooling operation utilizing cold storage heat, the operation is switched to the normal cooling operation described above.

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

-Heat storage operation- In this operation mode, the first four-way switching valve (22) is moved to the solid line side,
The second four-way switching valve (90) is switched to the broken line side, the outdoor electric expansion valve (EV-1) is opened at a predetermined opening, the thermal storage electric expansion valve (EV-3) is fully opened, and the indoor electric expansion valve (EV) is opened. Set each EV-2) to the fully closed state. Further, the first solenoid valve (SV-1) is opened, and the other solenoid valves (SV-2, SV-4, SV-5) are closed.

In this state, the refrigerant discharged from the compressor (21) receives the four-way switching valve (2) as shown by the arrow in FIG.
After passing through (2,90), heat is exchanged with water in the supercooling heat exchanger (50) to condense and heat the water. And this condensed refrigerant
After reducing the pressure with the outdoor electric expansion valve (EV-1), the outdoor heat exchanger (23)
Then, heat exchange is performed with the outside air to evaporate and return to the compressor (21). Thereby, the hot water is stored in the heat storage tank (31).

-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, each four-way switching valve (22, 9
0) is switched to the broken line side, the outdoor electric expansion valve (EV-1) is controlled to a predetermined opening, the indoor electric expansion valve (EV-2) is fully opened, and the thermal storage electric expansion valve (EV-3) is fully opened. Control to the closed state. On the other hand, the fourth solenoid valve (SV-4) is opened and the other solenoid valves (SV-1, SV-2, SV
-5) is closed together.

In this state, the refrigerant circulates to heat the room as in the case of the first embodiment described above.

In this operation mode, the first four-way switching valve (22) is switched to the broken line side, and the heat storage electric expansion valve (EV-3) is controlled to a predetermined opening degree, and the indoor electric expansion is performed. Fully open the valve (EV-2) and fully close the outdoor electric expansion valve (EV-1). Further, the fifth solenoid valve (SV-5) is closed, and the other solenoid valves (SV-1, SV-2, SV-4) are opened.

In this state, the refrigerant discharged from the compressor (21) condenses by exchanging heat with the indoor air in the indoor heat exchanger (24) as shown by an arrow in FIG. And this condensed refrigerant is decompressed by the heat storage electric expansion valve (EV-3),
The heat is exchanged with hot water in the supercooling heat exchanger (50) to evaporate, and then the air is sucked into the compressor (21) through the accumulator (25).

With the above operation, the indoor heating operation using the heat of the hot water stored in the heat storage tank (31) is performed.

Incidentally, even in this embodiment, the subcooling heat exchanger (50)
Only as a plate type heat exchanger or a preheater (1
Only 1) may be configured as a plate heat exchanger, or both may be integrally configured as a plate heat exchanger.

(Sixth Embodiment) Next, a sixth embodiment as a modification of the refrigerant circuit (20) will be described. In this embodiment, brine is cooled or heated using a heat source (ice or hot water) stored in a heat storage tank (31), and the brine is used to cool or heat the room.

In this embodiment, only parts different from the refrigerant circuit (20) of the first embodiment will be described.

-Refrigerant circuit (20)-As shown in FIG. 18, the refrigerant circuit (20) includes a compressor (21).
, Four-way switching valve (22), outdoor heat exchanger (23), outdoor electric expansion valve (EV-1), preheater (11), and heat storage electric expansion valve (EV-3)
A supercooling heat exchanger (50) and an accumulator (25) are sequentially connected by a refrigerant pipe (26), and a main refrigerant circuit (27) capable of reversible operation is provided.

The refrigerant circulation circuit (20) is provided with an ice core circuit (2b). The ice core circuit (2b) has one end between the preheater (11) and the heat storage electric expansion valve (EV-3), and the other end between the four-way switching valve (22) and the accumulator (25). At the same time, the solenoid valve (SV-5), the capillary tube (CP), and the ice nucleus generator (13) are connected in this order.

The supercooling heat exchanger (50) and the preheater (1
1) is constituted by a plate-type heat exchanger as in the above-described embodiment.

Water circulation circuit (30) The water circulation circuit (30) comprises a heat storage tank (31), a pump (32), a preheater (11), a supercooling heat exchanger (50), The cooling elimination unit is connected to the cooling pipe by a water pipe (35) so that circulation of water as a heat storage medium is possible. This water circulation circuit
The configuration of each device of (30) is the same as that of the above-described first embodiment, and a description thereof will not be repeated.

-Utilization side circuit (40)-Next, the utilization side circuit (40) for utilizing the cold or warm heat stored in the heat storage tank (31) will be described. The utilization side circuit (40) exchanges cold or hot water taken out of the heat storage tank (31) with brine to cool or heat the brine, and to supply the brine to the indoor heat exchanger (24). Has become.

More specifically, a heat storage heat exchanger (41) is provided, and this heat storage heat exchanger (41) is connected to the heat storage tank (31) by a water extraction pipe (42) and a water return pipe (43). Water is circulated between the heat storage tank (31) and the pump (44) provided in the water extraction pipe (42).

The heat storage utilization heat exchanger (41) is connected to each of the indoor heat exchangers (24, 24,...) By a brine supply pipe (45) and a brine recovery pipe (46).
The brine is circulated between the indoor heat exchangers (24, 24,...) As the pump (47) provided in (45) is driven.

The heat storage utilizing heat exchanger (41) is constituted by the same plate type heat exchanger as in each of the above embodiments.

Therefore, in the heat storage operation (the cooling operation using the cold storage and the heating operation using the heat storage) in this embodiment, the pumps (42) provided in the water extraction pipe (42) and the brine supply pipe (45) are provided. 44, 47) are driven together, and the heat stored in the heat storage tank (31) is supplied to the indoor heat exchanger (24) by brine to cool or heat the room.

In the present embodiment, the heat storage heat exchanger (4
Heat storage was given to the brine using 1), but this heat storage use heat exchanger (41) was not provided, and the heat storage tank (31) and the indoor heat exchanger (24) were directly connected by piping, During the heat storage operation, cold or hot water in the heat storage tank (31) may be supplied directly to the indoor heat exchanger (24).

In each of the above-described embodiments, the periphery of the opening for flowing the refrigerant and water in each heat transfer plate and the peripheral edge of the plate are sealed by brazing, but are sealed by welding or gasket. May be applied.

[0137]

As described above, according to the present invention, the following effects are exhibited. According to the first aspect of the present invention, the plate type heat exchanger is applied to the heat exchange means of the heat storage device that stores heat in the heat storage medium by heat exchange between the refrigerant and the heat storage medium, so that the heat exchange means is high. A compact configuration can be achieved while maintaining heat exchange performance. As a result, downsizing can be achieved while maintaining the performance of the entire device, and the practicality of the heat storage device can be improved.

According to the first aspect of the present invention, the ice making is performed by the supercooling elimination operation, and thereby, the supercooling heat exchanger of the ice heat storage device for storing the cold heat is described above. By employing the configuration of the present invention, high ice making efficiency can be realized, and cold heat can be efficiently stored in a short time.

Further, according to the first aspect of the present invention, the flow path of the heat storage medium is provided with a large turbulence region and a small turbulence region so that the supercooled heat storage medium flows through the small turbulence region. Due to this, it is possible to avoid such a problem that the heat storage medium in the supercooled state is agitated, the supercooling is eliminated, and the heat exchanger freezes.

According to the second aspect of the present invention, the herringbone-shaped projection is formed at the portion where the region with large disturbance is formed, and the extension direction of the projection of the portion where the region with small disturbance is formed is extended in the longitudinal direction of the plate. Thus, a specific configuration for forming a region with large disturbance and a region with small disturbance is obtained, and the device can be made highly practical.

According to the third and fourth aspects of the present invention, a preheat heat exchange section through which a high-temperature refrigerant for heating the heat storage medium flows in the refrigerant flow path, and a low-temperature heat exchange section for cooling the heat storage medium to a supercooled state. A cooling heat exchange section through which the refrigerant flows was formed. Therefore, it is possible to avoid a situation in which ice existing inside the heat storage medium in a supercooled state becomes a core for eliminating supercooling and causes the heat exchanger to freeze, thereby improving the reliability of the device.

[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 view showing a first type of heat transfer plate.

FIG. 5 is a view showing a second type of heat transfer plate.

FIG. 6 is a diagram showing a state in which the plates are superimposed.

FIG. 7 is a circuit diagram of a regenerative air conditioner for explaining cold storage operation.

FIG. 8 is a circuit diagram of a regenerative air conditioner for explaining cooling operation using cold storage energy.

FIG. 9 is a diagram corresponding to FIG. 4 in a third embodiment.

FIG. 10 is a diagram corresponding to FIG. 5 in a third embodiment.

FIG. 11 is a diagram corresponding to FIG. 4 in a fourth embodiment.

FIG. 12 is a diagram corresponding to FIG. 5 in a fourth embodiment.

13A is a sectional view taken along the line II in FIG. 11, FIG.
FIG. 12 is a sectional view taken along the line II-II of FIG.

FIG. 14 is a diagram corresponding to FIG. 1 in a fifth embodiment.

FIG. 15 is a circuit diagram of a regenerative air conditioner for illustrating a cooling operation using cold storage heat in a fifth embodiment.

FIG. 16 is a circuit diagram of a heat storage type air conditioner for explaining a warm heat storage operation in a fifth embodiment.

FIG. 17 is a circuit diagram of a regenerative air conditioner for explaining a heating operation using warm energy storage in a fifth embodiment.

FIG. 18 is a view corresponding to FIG. 1 in a sixth embodiment.

[Explanation of symbols]

 (11) Preheater (heat exchange means) (20) Refrigerant circulation circuit (30) Water circulation circuit (heat storage circuit) (31) Heat storage tank (32) Pump (circulation means) (35) Water pipe (50) Subcooling heat exchange (Heat exchange means) (53-58) Heat transfer plate (79) Decompression pipe (EV-3) Decompression mechanism (A) Refrigerant circulation part (B) Water circulation part (C) Cooling space (D) Preheating space ( E) Large turbulence area (F) Small turbulence area

Continuation of the front page (56) References JP-A-4-251177 (JP, A) JP-A-4-158194 (JP, A) JP-A 2-69272 (JP, U) JP-A-59-148964 (JP) , U) Japanese Utility Model Application Hei 4-33881 (JP, U) Japanese Patent Publication No. 47-29828 (JP, B1) Japanese Patent Application Publication No. 7-508581 (JP, A) (58) Fields surveyed (Int. Cl. ⁷ , DB) Name) F24F 5/00 F25C 1/00 F28D 9/00

Claims (4)

(57) [Claims] 1. A heat storage circuit (30) including a heat storage tank (31) and circulating a heat storage medium, and a refrigerant circuit (20) through which a refrigerant circulates, and after cooling or heating the heat storage medium by the refrigerant, In a heat storage device that stores heat by storing the heat storage medium in a heat storage tank (31), a heat exchange unit (5) that exchanges heat between the heat storage medium and the refrigerant is provided.
0), and the heat exchange means (50) includes a plurality of heat transfer plates (53-58) superimposed on each other, and each of the heat transfer plates (53
To 58), a heat storage medium flow path (B) and a refrigerant flow path (A) are respectively formed, and the heat storage medium and the refrigerant flowing through each flow path (A, B) are heat-transfer plates (53 to 58). The heat exchange means (50) is a subcooling heat exchanger that cools the heat storage medium to a supercooled state by the evaporating refrigerant, The supercooled state of the heat storage medium supercooled by the heat exchanger (50) is eliminated to make ice, and the supercooled heat exchanger (50) is located downstream of the heat storage medium in the flow direction of the heat storage medium and is in the supercooled state. Heat exchange unit (F) that allows the heat storage medium to flow in a state of small turbulence that does not eliminate supercooling of the heat storage medium
And a heat exchange unit (E) which is located upstream of the heat exchange unit (F) and flows the heat storage medium in a state of greater turbulence than the heat exchange unit (F). Heat storage device. 2. The heat storage device according to claim 1, wherein the heat transfer plates (53 to 58) have first protrusions projecting in one direction in the thickness direction and second protrusions projecting in the other direction alternately. The channels (A, B) are formed between the respective plates (53-58), and the channels (A, B) of the heat storage medium formed between the respective plates (53-58) are formed. B), a heat exchange section (E) through which the heat storage medium flows with large turbulence and a heat exchange section (F) through which the heat storage medium flows with small turbulence are provided continuously. In the part where the heat storage medium (E) through which the heat storage medium flows in a large turbulence state in (58) to (58), the extension direction of each protrusion is at a predetermined angle with respect to the longitudinal direction of the heat transfer plates (53 to 58). While the herringbone-type projections are formed in the direction of the heat exchange, the extension of each projection is A heat storage device characterized in that the direction extends along the longitudinal direction of the heat transfer plates (53-58). 3. The heat storage device according to claim 1, wherein the heat storage circuit (30) includes a heat storage tank (31) for storing the heat storage medium, a circulating means (32) for pumping the heat storage medium, and a heat storage medium. A supercoolable supercooling heat exchanger (50) is connected by a circulation pipe (35), and the heat storage medium taken out of the heat storage tank (31) is supercooled by the supercooling heat exchanger (50). Thereafter, the supercooled state is eliminated to generate ice, and the supercooled heat exchanger (50) is provided with a high-temperature refrigerant for heating the heat storage medium taken out of the heat storage tank (31). A preheating heat exchange section (D) that flows, and a cooling heat exchange section (C) through which a low-temperature refrigerant flows to cool the heat storage medium heated by the refrigerant in the preheating heat exchange section (D) to a supercooled state. A heat storage device, comprising: 4. The heat storage device according to claim 3, wherein the preheat heat exchange section (D) and the cooling heat exchange section (C) are provided with a pressure reducing pipe (79).
The pressure-reducing pipe (79) has a pressure-reducing mechanism (EV-3) for reducing the pressure of the refrigerant derived from the preheating heat exchange section (D).
The refrigerant that has exchanged heat with the heat storage medium in the preheat heat exchanger (D) is depressurized by the pressure reducing mechanism (EV-3), and then heat-exchanges with the heat storage medium in the cooling heat exchange section (C). A heat storage device characterized by being evaporated.