JPH109623A - Ice storage device - Google Patents

Abstract

(57) [Summary] [PROBLEMS] To improve the ice making efficiency by avoiding the operation of eliminating supercooling near the tube sheet by improving the configuration of a liquid-filled heat exchanger for generating supercooled water. Aim. SOLUTION: A refrigerant circulation circuit and a water circulation circuit are provided, and water is cooled by a heat storage heat exchanger (42) to a supercooled state, and ice nuclei generated by an ice nucleus generator are mixed into the water to supercool. For a device that makes ice by resolving the condition, the heat storage heat exchanger (42) is formed of a liquid-filled shell-and-tube type, with water inside the heat transfer tube (49) and refrigerant outside the heat transfer tube (49). Shed. The tube sheet (36) on the downstream side in the water flow direction is made of a material having a lower thermal conductivity than the material of the container (48) of the heat storage heat exchanger (42).

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat storage tank for cooling a heat storage medium such as water or an aqueous solution to a supercooled state by exchanging heat with a refrigerant, and then eliminating the supercooled state. The present invention relates to an improvement in the structure of a supercooling heat exchanger that exchanges heat between a heat storage medium and a refrigerant in an ice heat storage device that stores heat in a storage medium.

[0002]

2. Description of the Related Art Conventionally, as an ice heat storage device provided in an ice storage type air conditioner or the like, in view of reducing power demand during peak cooling load and expanding power demand during off-peak time. In addition, there is known an apparatus in which slurry-like ice to be used as cooling heat at the time of a cooling load peak is generated at the time of a cooling load off-peak and stored in a heat storage tank.

As one example of this type of ice heat storage device, as disclosed in Japanese Patent Application Laid-Open No. Hei 4-251177, a compressor, a condenser, an expansion mechanism and a refrigerant heat exchange section are sequentially connected by refrigerant piping. And a water circulation circuit in which a heat storage tank, a heat storage medium heat exchange unit capable of exchanging heat with the refrigerant heat exchange unit, and a supercooling elimination unit are sequentially connected by a water pipe. Are known.

[0004] 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.

[0005] A supercooling heat exchanger for exchanging heat between the heat storage medium heat exchanging section and the refrigerant heat exchanging section.
There is a liquid-fill type heat exchanger as a type. This type of heat exchanger is provided with a cylindrical container having a vertical axis, in which a heat storage medium introduction space is formed at a lower end portion and a heat storage medium outlet space is formed at an upper end portion. And a pair of upper and lower tube sheets are provided. Further, a plurality of heat transfer tubes are provided on each tube sheet, and the heat transfer tubes communicate the heat storage medium introduction space and the heat storage medium discharge space.
A water pipe is connected to the heat storage medium introduction space and the heat storage medium lead-out space, and a refrigerant is circulated in a substantially full state around each heat transfer tube between the respective tube plates. Heat is exchanged between water flowing in the heat transfer tube from the heat storage medium introduction space to the heat storage medium outlet space and the refrigerant around the heat transfer tube.

[0006]

When supercooled water is generated by using this type of liquid-filled heat exchanger, the boiling of the refrigerant near the gas-liquid interface of the refrigerant in the heat exchanger. As a result, the droplet-shaped refrigerant scatters on the lower surface of the upper tube sheet located on the low temperature side (the side on which the supercooled water flows). In such a situation, the scattered refrigerant evaporates from the lower surface of the tube sheet to cool the tube sheet, and heat conduction in the tube sheet cools the entire tube sheet. If the supercooled water flowing out of the heat transfer tube into the heat storage medium outlet space comes into contact with the tube sheet, the water is further cooled by the tube sheet, and the water is cooled in the heat storage medium outlet space. The cooling elimination operation may occur. In such a situation, ice adheres to the tube sheet, and the supercooled water flowing out of the heat transfer tube comes into contact with the ice. Grow,
There is a possibility that the heat transfer tube may be blocked, resulting in a problem that ice making efficiency is remarkably deteriorated.

[0007] The present invention has been made in view of such a point, and an object of the present invention is to improve the configuration of this type of heat exchanger to avoid the occurrence of the operation of eliminating supercooling near the tube sheet. And to improve the ice making efficiency.

[0008]

In order to achieve the above object, according to the first aspect of the present invention, the tube sheet facing the supercooled water is made of a material having a low thermal conductivity. Cold heat generated by the evaporation of the refrigerant is less likely to be transmitted to the surface in contact with the supercooled water.

Specifically, the compressor (1), the heat source side heat exchanger (3), the expansion mechanism (52a), and the refrigerant heat exchange part (42a) of the subcooling heat exchanger (42) It has a refrigerant circulation circuit (A) in which refrigerant can be circulated by a refrigerant pipe (8), a heat storage tank (T) for storing a heat storage medium, and a circulation means (P) for pumping the heat storage medium. And the refrigerant heat exchange section (42
a) a heat storage circuit (42) of a supercooling heat exchanger (42) capable of exchanging heat with the heat storage medium heat exchange section (42b). B), and the heat exchange between the refrigerant evaporated in the refrigerant heat exchange section (42a) and the liquid phase heat storage medium flowing through the heat storage medium heat exchange section (42b) cools the heat storage medium to a supercooled state. Then, after the heat storage medium is led out of the supercooling heat exchanger (42), an ice heat storage device that eliminates the supercooled state to generate ice and recovers the ice in the heat storage tank (T) is provided. It is assumed. And
The supercooling heat exchanger (42) has a tube plate (36) that defines a heat storage medium outlet space (48a) inside the container (48), and the upstream side communicates with the circulation pipe (45) and the downstream end stores heat. A heat transfer tube (49) opening to the medium outlet space (48a) is provided. Further, the heat storage medium heat exchange section (42b) is composed of the heat storage medium outlet space (48a) and the heat transfer tube (49), while the refrigerant heat exchange section (42a) is formed in the tube sheet (36) in the container (48). And a refrigerant flow space (48c) formed around the heat transfer tube (49), which is partitioned from the heat storage medium outlet space (48a), and through which the refrigerant flows in a substantially full state. Then, heat exchange is performed between the refrigerant in the refrigerant circulation space (48c) and the heat storage medium flowing in the heat transfer tube (49) toward the heat storage medium outlet space (48a). Further, at least a part of the tube sheet (36) is made of a material having a lower thermal conductivity than a material of the container (48).

With this configuration, the operation during ice making is as follows.
The heat storage medium taken out of the heat storage tank (T) exchanges heat with the refrigerant evaporating in the refrigerant heat exchange section (42a) in the heat storage medium heat exchange section (42b) and is cooled to a supercooled state. After being drawn out from the medium heat exchange section (42b), the supercooled state is eliminated and the phase changes to ice. Then, this ice is collected in the heat storage tank (T) and stored as cold storage heat. In such an ice making operation, in the supercooling heat exchanger (42), the heat storage medium flows in the heat transfer tube (49) toward the heat storage medium outlet space (48a), while the refrigerant is stored in the container (48). Refrigerant circulation space inside (48c)
Circulates in a substantially full state around the heat transfer tube (49). In the vicinity of the gas-liquid interface of the refrigerant in the refrigerant flow space (48c), the boiling refrigerant becomes droplets and becomes a droplet form.
6) will be scattered. Then, the surface of the tube sheet (36) facing the refrigerant circulation space (48c) is cooled by evaporation of the scattered refrigerant from the tube sheet (36). However,
In the present invention, at least a part of the tube sheet (36) is made of a material having a low thermal conductivity, so that the cold generated due to the evaporation of the refrigerant is a heat storage medium outlet space in the tube sheet (36).
(48a) The heat transfer tube
Even if the supercooled heat storage medium flowing out of (49) into the heat storage medium lead-out space (48a) comes into contact with the tube sheet (36), it is suppressed that the heat storage medium is further cooled by the tube sheet (36). As a result, the operation of eliminating the supercooling in the heat storage medium outlet space (48a) is prevented.

According to a second aspect of the present invention, in the ice heat storage device of the first aspect, the tube sheet (36) is constituted by a plurality of layers (36a to 36c), and at least one of the layers is formed by a container (48). It is configured to be formed of a material having a lower thermal conductivity than the material of which it is configured.

With this configuration, of the layers (36a to 36c), the layer formed of a material having low thermal conductivity is transferred to the surface of the tube sheet (36) facing the heat storage medium outlet space (48a). By functioning as a layer for suppressing heat and using a material having high rigidity for the other layers, it is possible to function as a pressure-resistant layer capable of withstanding the internal pressure of the refrigerant circulation space (48c). That is, it is possible to provide the heat insulation function while maintaining the pressure resistance required for the tube sheet (36).

According to a third aspect of the present invention, in the ice heat storage device of the second aspect, at least one of the layers is made of a resin material.

According to this configuration, the heat insulating function of the layer for suppressing the heat transfer of the cold heat can be further improved, and the operation of eliminating the supercooling in the heat storage medium outlet space (48a) can be reliably prevented.

According to a fourth aspect of the present invention, in the ice heat storage device of the first aspect, the tube sheet (36) has a three-layer structure, and both outer layers (36a, 36b) are made of a metal material, and the intermediate layer is made of an intermediate layer. (36c) are each formed of a resin material.

With this configuration, the intermediate layer (36c) formed of the resin material does not come into contact with the heat storage medium or the refrigerant, so that deterioration of the heat insulation performance due to corrosion of the material is avoided.

According to a fifth aspect of the present invention, in the ice heat storage device of the first aspect, the entire tube sheet (36) is formed of a resin material.

With this configuration, even if the thickness of the tube sheet (36) is reduced, sufficient heat insulation performance can be obtained, and the tube sheet (36) can be obtained while securing the operation according to the first aspect of the present invention. The size of the supercooling heat exchanger (42) can be reduced in accordance with the reduction in the thickness of ()).

According to a sixth aspect of the present invention, there is provided a heat transfer tube (49) so that the supercooled heat storage medium flowing out of the heat transfer tube (49) into the heat storage medium outlet space (48a) does not contact the tube sheet (36). In this case, the supercooling elimination operation is not performed in the heat storage medium outlet space (48a) even if the tube sheet (36) is cooled. Specifically, the premise is the same as that of the invention described in claim 1 described above, and instead of improving the material of the tube sheet (36), the heat transfer tube (49) is replaced with a heat storage medium outlet space.
The heat storage medium that flows into the heat storage medium (48a) is extended inside the heat storage medium outlet space (48a) so as not to flow along the tube sheet (36).

With this configuration, the supercooled heat storage medium that has flowed out of the heat transfer tube (49) into the heat storage medium outlet space (48a) can be cooled.
Since it does not flow along (36), even if the tube sheet (36) is formed of the same material as the conventional one, the supercooling elimination operation is not performed in the heat storage medium outlet space (48a). .

According to the present invention, the heat storage medium in a supercooled state is supplied to the tube sheet by providing heat insulation between the refrigerant in the refrigerant flow space and the surface of the tube sheet facing the heat storage medium outlet space. Even if it makes contact, supercooling is not eliminated. Specifically, the premise is the same as the above-described invention of claim 1,
Instead of improving the material of the tube sheet (36), the tube sheet (36)
Are constituted by a pair of plate members (68, 69) forming a space (C) between them at a predetermined interval.

Thus, the space inside the refrigerant flow space (48c) and the heat storage medium outlet space (48
Insulation between the surface facing a) and the supercooled heat storage medium does not disappear even if the supercooled heat storage medium comes into contact with the tube sheet (36).

According to an eighth aspect of the present invention, in the ice heat storage device according to the seventh aspect, the space between the plate members (68, 69) is provided.
(C) is configured to be filled with a heat insulating gas for heat insulation between the refrigerant in the refrigerant circulation space (48c) and the plate member (69) facing the heat storage medium outlet space (48a).

According to a ninth aspect of the present invention, in the ice heat storage device of the seventh aspect, the space between the plate members (68, 69) is provided.
(C) is configured to be in a vacuum state so as to provide heat insulation between the refrigerant in the refrigerant circulation space (48c) and the plate member (69) facing the heat storage medium outlet space (48a).

With this configuration, the space (C) can be provided with high heat insulation performance, and the heat storage medium lead-out space (48a) can be provided.
In this case, it is possible to more reliably prevent the supercooling of the heat storage medium from being eliminated.

According to a tenth aspect of the present invention, in the ice heat storage device of the seventh aspect, the space between the plate members (68, 69) is provided.
(C) a configuration in which a refrigerant for maintaining the temperature of the plate (69) at a predetermined value or more is introduced so as to prevent freezing of the heat storage medium on the surface of the plate (69) facing the heat storage medium outlet space (48a). And

Thus, the surface of the plate (69) facing the heat storage medium outlet space (48a) is always maintained at a temperature at which the supercooling of the heat storage medium is not eliminated, and the heat storage medium outlet space (48a) is maintained. The operation of eliminating supercooling in () does not occur.

[0028] The eleventh aspect of the present invention relates to the tenth aspect.
In the ice heat storage device described above, the high pressure side pipe of the refrigerant pipe (8) is connected to the space (C) between the plate members (68, 69),
A communication pipe (75) communicating the space (C) with the refrigerant circulation space (48c) is provided, and the communication pipe (75) is provided with an expansion mechanism (52a).

According to this configuration, of the refrigerant flowing through the refrigerant pipe (8), the high-temperature and high-pressure refrigerant flowing through the high-pressure side pipe is introduced into the space (C) between the plates (68, 69). (6
8,69) is heated. That is, the tube sheet (36) is heated. Thereafter, the refrigerant is decompressed by the expansion mechanism (52a) in the communication pipe (75), and is introduced into the refrigerant circulation space (48c) to perform heat exchange with the heat storage medium flowing through the heat transfer pipe (49). Become. For this reason, since the plate material (69) facing the heat storage medium lead-out space (48a) is always heated by the refrigerant, even if the heat storage medium in a supercooled state contacts the plate material (69), the supercooling is eliminated. Never. In addition, space (C)
May be provided with a function of condensing the refrigerant.

According to the twelfth aspect of the present invention, the tube sheet is heated by the refrigerant flowing through the refrigerant circuit so that the supercooled heat storage medium does not disappear even if it comes into contact with the tube sheet. . More specifically, the premise is substantially the same as the above-described invention. Instead of improving the material of the tube sheet (36), the temperature of the tube sheet (36) is higher than that of the heat storage medium flowing through the heat storage medium outlet space (48a) among the refrigerant flowing through the refrigerant circuit (A). Heat was exchanged with the refrigerant.

According to this specific matter, the tube sheet (36) is heated by the relatively high temperature refrigerant in the refrigerant circulation operation in the refrigerant circulation circuit (A). Therefore, also in this case,
Even if the supercooled heat storage medium flowing out of the heat transfer tube (49) into the heat storage medium outlet space (48a) comes into contact with the tube sheet (36), the heat storage medium is further cooled by the tube sheet (36). Is suppressed, and the operation of eliminating supercooling in the heat storage medium outlet space (48a) is prevented.

The inventions of claims 13 and 14 embody the structure of the invention of claim 12 described above. In other words, the invention according to claim 13 provides the tube sheet (36) with the heat storage medium outlet space (4) of the refrigerant flowing through the refrigerant circuit (A).
The pipe (11) through which the refrigerant having a higher temperature than the heat storage medium flowing through the pipe (11) flows is brought into contact with the pipe sheet (36) and the refrigerant flowing through the pipe (11) exchanges heat. In the invention according to claim 14, the high pressure side pipe (11) of the refrigerant pipe (8) is brought into contact with the tube sheet (36), and the tube sheet (36) and the refrigerant flowing through the high pressure side pipe (11) exchange heat. The pipes (11)
The tube sheet (36) can be heated by the high-temperature refrigerant flowing through the heat storage medium, so that the operation of eliminating the supercooling in the heat storage medium outlet space (48a) is reliably prevented.

[0033] The fifteenth aspect of the present invention is directed to the thirteenth aspect.
In the ice heat storage device described above, the pipe (11) is brazed to the tube sheet (36).

According to this specific matter, the pipe (11) and the tube sheet (36)
The contact area between the two (11, 36) is increased, and heat conduction between the two (11, 36) is performed well.

The sixteenth aspect of the present invention relates to the thirteenth aspect.
In the ice heat storage device described in the above, the outer periphery of the tube sheet (36) is
8) to the outer peripheral side from the outer peripheral surface.
d) forming a groove (80). The pipe (11) is configured to fit into the groove (80).

According to this specific matter, the pipe (11) is connected to the tube sheet (36).
Can be held. In addition, since the contact area between the two can be relatively large, the tube sheet (36) can be sufficiently heated.

According to a seventeenth aspect of the present invention,
In the ice heat storage device described above, the groove (80) is formed on one surface in the thickness direction of the tube sheet (36). The invention according to claim 18 is configured such that the groove (80) is formed on the outer peripheral end surface of the tube sheet (36).

With these specific items, the formation position of the groove (80) for fitting the pipe (11) can be specifically obtained, and the practical configuration of the configuration in which the pipe (11) is brought into contact with the tube sheet (36) can be obtained. The performance is improved.

According to the nineteenth aspect of the present invention, the above-mentioned sixteenth aspect
In the described ice heat storage device, the pipe (11) is brazed to the inner surface of the groove (80).

According to this specific matter, it is possible to prevent the pipe (11) from being detached from the groove (80). Also, this pipe (11) and groove
Since the adhesion to (80) is improved, heat conduction between the two (11, 80) is favorably performed.

According to a twentieth aspect of the present invention, there is provided the above-described sixteenth aspect.
In the ice heat storage device described in the above, a main body portion forming a refrigerant circulation space (48c) on one side in the thickness direction of the tube sheet (36) in the container (48).
(48A), and a lid (48B) forming a heat storage medium outlet space (48a) on the other side in the thickness direction of the tube sheet (36). A groove (80) is formed on the surface of the tube sheet (36) on the side of the lid (48B). The lid (48B) is provided with a restricting portion (82) for closing the open side of the groove (80) so as to prevent the pipe (11) fitted in the groove (80) from being detached.

Also according to this particular matter, the pipe (11) has the groove (8).
0) can be prevented, and the outer peripheral surface of the pipe (11) and the groove
A good contact state with the inner peripheral surface of (80) is obtained.

According to the twenty-first aspect, the twelfth aspect of the present invention provides
In the ice heat storage device described above, a flow passage (80) through which a refrigerant having a higher temperature than the heat storage medium flowing through the heat storage medium outlet space (48a) flows is formed inside the tube sheet (36). Specifically, as in the invention according to claim 22, a hole for penetrating the heat transfer tube (49) is formed in the tube sheet (36), and the flow passage (80) is formed in the tube sheet (3).
6) In the direction perpendicular to the thickness direction, the heat transfer tube (49)
It is configured to extend so as not to interfere with the hole for penetration.

According to this specific matter, the tube sheet (36) can also be used as a member for flowing a relatively high-temperature refrigerant, and the liquid-side piping can be used.
A special structure for bringing the outer peripheral surface of (11) into contact with the tube sheet (36) is not required.

According to the twenty-third aspect of the present invention,
In the ice heat storage device described above, the tube sheet (36) is made of a plurality of plate materials (36A, 36B) stacked on each other. Each plate (36A, 3
6B), grooves (80A, 80B) extending in a direction perpendicular to the thickness direction are formed. These plates (36A, 36B) are superimposed on each other, and the grooves (80A, 80B) are
Is formed.

According to this particular matter, the heat storage medium outlet space (48) is formed inside the tube sheet (36) by a relatively simple manufacturing operation.
a), through which a refrigerant having a higher temperature than the heat storage medium flowing through a) flows.

[0047]

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

(First Embodiment) FIG. 1 shows the overall configuration of a refrigerant circuit (A) provided in an ice storage type air conditioner according to a first embodiment of the present invention. FIG. 2 is a diagram showing a water circulation circuit (B) as a heat storage circulation circuit. As shown in FIG. 1, the present air conditioner has an outdoor unit (X).
And a plurality of indoor units (Y, Y, Y)
Liquid-side and gas-side communication pipes (RL, RG) that form part of (A)
The so-called indoor multi-type is connected by the. Hereinafter, the refrigerant circuit (A) and the water circuit (B) will be described.

-Explanation of Refrigerant Circulation Circuit- First, the main circuit configuration of the refrigerant circulation circuit (A) will be described.

This refrigerant circuit (A) is an outdoor unit
(X), an outdoor heat exchanger (3) as a heat source side heat exchanger in which a four-way switching valve (2), an outdoor fan (F) is disposed in close proximity, and a receiver (4) And first outdoor electric expansion valve
(5), a plurality of indoor electric expansion valves (6, 6, 6) provided in the indoor unit (Y), and an indoor heat exchanger (7, 7, 7) as a use-side heat exchanger are connected with refrigerant pipes. (8) A main refrigerant circuit (A-1) sequentially connected by (8).

A detailed description will be given of the connection state of each device by the refrigerant pipe (8). A gas-side pipe (10) is provided at one end on the gas side of the outdoor heat exchanger (3), and a gas-side pipe (10) is provided at the other end on the liquid side. Are connected to liquid side pipes (11), respectively. Gas side piping
(10) is connected to the discharge side and the suction side of the compression mechanism (1) by a four-way switching valve (2) so as to be switchable. That is, the gas side pipe (10) is connected between the discharge side of the compression mechanism (1) and the four-way switching valve.
(2), a second discharge gas line (10b) connecting the four-way switching valve (2) and the outdoor heat exchanger (3), a four-way switching valve (2). ) And a suction gas line (10c) connecting the suction side of the compression mechanism (1). Also,
The intake gas line (10c) is provided with an accumulator (12).

On the other hand, the liquid side pipe (11) is connected to the outdoor heat exchanger (3).
A first liquid line (11a) connecting the receiver and the receiver (4), a second liquid line (11b) connecting the receiver (4) and the first outdoor electric expansion valve (5), and an outdoor electric expansion valve (5) And a third liquid line (11c) for connecting the liquid side communication pipe (RL) with the third liquid line (11c). The first liquid line (11a) has a receiver from the outdoor heat exchanger (3).
Check valve (CV1) that allows only refrigerant flow to (4)
However, in the third liquid line (11c), two check valves (CV2, CV3) each permitting only the flow of the refrigerant from the outdoor electric expansion valve (5) to the liquid side communication pipe (RL) are provided. Have been.

The check valve in the first liquid line (11a)
The fourth liquid line (11d) is connected between (CV1) and the receiver (4) and the downstream side of the check valve (CV3) in the third liquid line (11c). The fourth liquid line (11d) is provided with a check valve (CV4) that allows only the flow of the refrigerant from the third liquid line (11c) to the first liquid line (11a).

The liquid side communication pipe (RL) is connected to the liquid side of each indoor heat exchanger (7, 7, 7) via a plurality of indoor liquid pipes (7a, 7a, 7a). . Each of the indoor liquid pipes (7a, 7a, 7a) is provided with the indoor electric expansion valve (6, 6, 6).

On the other hand, the gas side communication pipe (RG) is connected to each indoor heat exchanger (7, 7, 7) via a plurality of indoor gas pipes (7b, 7b, 7b).
Is connected to the gas side. In addition, this gas side communication pipe (R
G) is connected to a four-way switching valve (2) via a gas pipe (15), and the connection state between the discharge side and the suction side of the compression mechanism (1) is switched by the four-way switching valve (2). It is possible.

The compression mechanism (1) includes a variable capacity upstream compressor (COMP-1) whose capacity is controlled in a number of stages by inverter control, and a switching control in three stages of full load, unload and stop. A so-called twin type in which a downstream compressor (COMP-2) with an unloader mechanism is connected in parallel.

The refrigerant circuit (A) is provided with an oil return mechanism (20) for returning lubricating oil to the compression mechanism (1). The oil return mechanism (20) includes an oil separator (21, 22) and an oil return pipe (23, 24). The above oil separator (21,22)
Are the discharge pipes (1) of the upstream compressor (COMP-1) and the downstream compressor (COMP-2) which are part of the first discharge gas line (10a).
0a-1, 10a-2). The oil return pipes (23, 24) each include a capillary tube (CP), and have a lower end of an oil separator (21, 22) and an upstream compressor (part of the suction gas line (10c)). The lubricating oil stored in the oil separators (21, 22) is returned to the upstream compressor (COMP-1) by being connected to the suction pipe (10c-1) of the COMP-1). Also,
Downstream of the oil separator (21, 22) in each discharge pipe (10a-1, 10a-2), a four-way switching valve (2) from each compressor (COMP-1, COMP-2)
Check valves (CV5, CV6) each permitting only the flow of the refrigerant toward the outlet are provided.

The suction pipe (10c-2) of the downstream compressor (COMP-2), which is a part of the suction gas line (10c), is connected to the suction pipe (10c) of the upstream compressor (COMP-1). -1) The pressure loss is set to be greater than that of the compressor, and an oil equalizing pipe (25) having a capillary tube (CP) is connected between both compressors (COMP-1 and COMP-2). As a result, the high-pressure side upstream compressor (COMP-1)
The lubricating oil collected at the downstream compressor (CO
The lubricating oil is supplied to the compressors (COMP-1) and the compressors (COMP-1, COMP-2).

An auxiliary heat exchanger (30) is provided adjacent to the outdoor heat exchanger (3).
The gas side of (0) is connected to the downstream side of the check valves (CV5, CV6) in the first discharge gas line (10a) by the auxiliary gas line (31). On the other hand, the liquid side of the auxiliary heat exchanger (30) is connected to the downstream side of the check valve (CV1) in the first liquid line (11a) by the auxiliary liquid line (32). The auxiliary liquid line (32) has a capillary tube (CP) and a first solenoid valve.
(SV1) is provided.

Further, a check valve in the third liquid line (11c)
Check valve (C) in the upstream side of (CV2) and the first liquid line (11a).
The heating liquid line (33) is connected to the upstream side of V1). This heating liquid line (33) has a third liquid line (11c)
A check valve (CV7) is provided to allow only the flow of the refrigerant from the outside to the outdoor heat exchanger (3).

The second liquid line (11b) and the downstream side of the check valve (CV2) in the third liquid line (11c) are connected by a bypass line (34). This bypass line (3
4) is provided with a second solenoid valve (SV2) and a check valve (CV8) that allows only the flow of refrigerant from the second liquid line (11b) to the third liquid line (11c). The main circuit configuration of the refrigerant circuit (A) has been described above.

—Description of Water Circulation Circuit— Next, the configuration of the water circulation circuit (B) will be described.

As shown in FIG. 2, the water circulation circuit (B) includes a heat storage tank (T), a pump (P) as a circulating means, a preheater (40) composed of a heat exchanger having a double pipe structure, (41), a heat storage heat exchanger (42) as a subcooling heat exchanger composed of a vertical shell and tube heat exchanger, and a subcooling eliminator (4
3) are sequentially connected by a water pipe (45) so that water circulation (see the arrow in FIG. 2) is possible. The water pipe (45a) connecting the heat storage heat exchanger (42) and the supercooling canceller (43) is provided with an ice nucleus generator (46) and an ice growth preventer (47). The preheater (40) and the heat storage heat exchanger (42) exchange heat between the refrigerant flowing in the refrigerant circuit (A) and water.

Hereinafter, the preheater (40) and the heat storage heat exchanger (4)
The configuration of the refrigerant circuit (A) for supplying a refrigerant that exchanges heat with water in 2) will be described.

As shown in FIG. 1, the preheater (40) is provided in the middle of the third liquid line (11c). When the refrigerant in the third liquid line (11c) flows through the outer space, heat is exchanged between the two (see FIG. 2). Also, the third
The thawing bypass line (50) connects the liquid line (11c) between the preheater (40) and the connection position of the bypass gas line (34) and the upstream side of the accumulator (12).
The defrost bypass line (50) is provided with a third solenoid valve (SV3).

Next, the configuration of the heat storage heat exchanger (42) as a characteristic feature of the present embodiment will be described. As shown in FIG. 3, the heat storage heat exchanger (42) includes a closed cylindrical container (48) having a vertically extending axis. At the upper and lower ends of this container (48), the water circulation portions (48a) on the outlet side and the inlet side as outlet and inlet spaces for the heat storage medium defined by the tube sheets (36) and (37), 48b) and its outlet-side water circulation section (48a) and inlet-side water circulation section (48b).
And a plurality of heat transfer tubes (49, 4
9,…) are provided. Specifically, the outlet-side tube sheet (36) located on the upper side is arranged over the entire inner surface of the container (48) at a lower position at a predetermined distance from the upper surface of the container (48), The outlet side water circulation part (4
8a) and a refrigerant circulation portion (48c) as a refrigerant circulation space which is a lower space. On the other hand, the introduction-side tube sheet (37) located on the lower side is arranged over the entire inner surface of the container (48) at an upper position at a predetermined distance from the lower surface of the container (48), and Introductory water circulation section (4
8b) and the refrigerant flow section (48c). In addition, a water pipe (45c) extending from the mixer (41) is provided in the inlet side water circulation section (48b), and a water pipe (45d) connected to the subcooling canceller (43) is provided in the outlet side water circulation section (48a). Are connected respectively. Each of the heat transfer tubes (49, 49,...) Is a straight tube provided with a radiation fin (not shown) on the outer peripheral surface, and is arranged in parallel at positions equidistant from each other. (36) and opens to the outlet side water circulation part (48a), and the lower end penetrates the introduction side tube sheet (37) to open to the introduction side water circulation part (48b). In other words, each heat transfer tube (49, 49,…)
Water can be distributed from (48b) to the outlet-side water circulation section (48a).

A lower connecting pipe (52) is connected to the lower part of the refrigerant flow part (48c), and an upper connecting pipe (51) is connected to the upper part. The upper connection pipe (51) and the lower connection pipe (52)
In a cold storage operation, a defrosting operation, a simultaneous cold storage / cooling operation, and a heating operation using hot storage, which will be described later, a refrigerant introduction pipe and a refrigerant flow for introducing a refrigerant into the refrigerant circulation part (48c) of the heat storage heat exchanger (42). The portion (48c) functions as a refrigerant outlet pipe for extracting the refrigerant from the inside. With such a configuration, a heat storage medium heat exchange unit (42b) is configured by each water circulation unit (48a, 48c) and the heat transfer tube (49), and a refrigerant heat exchange unit (42a) is defined by the refrigerant circulation space (48c). It is configured.

As shown in FIG. 1, the upper connection pipe (51) has one end connected to the upper end of the outer peripheral surface of the refrigerant flow part (48c) and the other end connected to the defrost bypass line (50) in the suction gas line (10c). Each is connected upstream of the position. Meanwhile, the lower connecting pipe
(52), one end is located at the lower end position of the outer peripheral surface of the refrigerant flow portion (48c),
The other end is connected between the preheater (40) and the check valve (CV3) in the third liquid line (11c). The upper connecting pipe (51) is provided with a fourth solenoid valve (SV4), and the lower connecting pipe (52) is provided with a second outdoor electric expansion valve (52a).
Then, in the refrigerant circulation part (48c), the refrigerant flows through the gas-liquid interface (G) into the refrigerant circulation part (48c) by introduction or derivation of the refrigerant from the upper connection pipe (51) and the lower connection pipe (52). And circulates in a substantially full state. That is, the heat storage heat exchanger (42) is connected to the upper connecting pipe (5) in the refrigerant flow section (48c).
1) and the refrigerant introduced and discharged by the lower connection pipe (52) flows around each heat transfer pipe (49), and performs heat exchange between the refrigerant and water flowing through each heat transfer pipe (49). It is configured.

The feature of this embodiment resides in the constituent material of the outlet side tube sheet (36). Explaining the material of each member constituting the heat storage heat exchanger (42), the container (48) is made of carbon steel for pressure piping (STPG: thermal conductivity of about 50 W / mK (normal temperature)), an inlet side tube sheet ( 37) is made of mild steel (thermal conductivity of about 52 W / mK (normal temperature)), and is made of a general material as a heat exchanger with sufficient rigidity to withstand internal pressure changes in the refrigerant flow section (48c). On the other hand, the outlet side tube sheet (36) is made of a material having a lower thermal conductivity than these. For example, gray cast iron (thermal conductivity of about 42 W / mK (normal temperature)), stainless steel (thermal conductivity of about 16 W / mK (austenitic, normal temperature)) and the like are applied. In other words, in the outlet side tube sheet (36), even if the lower surface facing the refrigerant flow portion (48c) is cooled, the cold heat is hardly transmitted to the upper surface facing the outlet side water flow portion (48a). I have. The above is the main configuration of the heat storage heat exchanger (42).

A heat storage utilization bypass pipe (53) is provided between the upper end of the receiver (4) and the second outdoor electric expansion valve (52a) and the heat storage heat exchanger (42) in the lower connection pipe (52). Connected by The heat storage bypass pipe (53) is provided with a capillary tube (CP) and a fifth solenoid valve (SV5).

Further, between the connection position of the auxiliary gas line (31) in the first discharge gas line (10a) and the check valves (CV5, CV6), and the heat storage bypass pipe (53) in the lower connection pipe (52). )
And the second outdoor electric expansion valve (52a) are connected by a hot gas supply pipe (54). The hot gas supply pipe (54) is provided with a sixth solenoid valve (SV6).

Further, the downstream side of the sixth solenoid valve (SV6) in the hot gas supply pipe (54) and the upper side of the heat storage heat exchanger (42) are connected by a heat storage utilization supply pipe (55). I have.
The heat storage utilization supply pipe (55) is provided with a seventh solenoid valve (SV7).

As described above, since the refrigerant pipes are connected to the preheater (40) and the heat storage heat exchanger (42), when the refrigerant is supplied from the refrigerant pipes to the devices (40, 42), Heat exchange is performed between the refrigerant and the water to cool or heat the water. Specifically, for example, the water is cooled so as to generate supercooled water for ice making in the heat storage heat exchanger (42), or the ice is melted when the ice circulates through the water pipe (45). The water is heated by the preheater (40).

Next, the ice nucleus generator (46) and the ice progress preventing device (47) will be described. The ice nucleator (46) is connected to the water pipe (4
5a) A part of the water flowing through the refrigerant circulation circuit (A) is cooled and iced by the refrigerant flowing through the refrigerant circulation circuit (A), and the ice is used as ice nuclei to remove the supercooling
Is to be supplied to The ice nucleus generator (46) has an ice nucleation refrigerant introduction pipe (58) and an ice nucleation refrigerant extraction pipe (59).
Is connected. One end of the ice nucleation refrigerant introduction pipe (58) is located between the connection position of the hot gas supply pipe (54) in the lower connection pipe (52) and the second outdoor electric expansion valve (52a), and the other end is an ice nucleus. Each is connected to a generator (46). Further, the ice nucleation refrigerant introduction pipe (58) includes a capillary tube (CP).
One end of the ice nucleation refrigerant outlet pipe (59) has one end of the downstream compressor (C
The other end is connected to the suction pipe (10c-2) of the OMP-2) and the ice nucleus generator (46). As a result, the ice nucleation refrigerant introduction pipe (5
Refrigerant and water pipe (45a) introduced from 8) to ice nucleus generator (46)
Cooling the water by performing heat exchange with the water flowing through it, a part of this water adheres to the inner wall surface of the water pipe (45a) as ice lumps, and the ice lumps are formed by the water pressure in the water pipe (45a). A part is peeled off, and this is flown as an ice nucleus toward the supercooling elimination part (43).

The ice growth preventer (47) is disposed upstream of the ice nucleus generator (46) in the direction of water flow, and is connected to the water pipe (45a) from the ice nucleus generator (46). Of ice along the pipe wall. And this ice progress prevention device (47)
The anti-progression refrigerant inlet pipe (60) and the anti-progression refrigerant outlet pipe (6
1) is connected. One end of the propagation preventing refrigerant introduction pipe (60) is connected to the auxiliary gas line (31), and the other end is connected to the ice growth preventing device (47). The expansion prevention refrigerant outlet pipe (61) has one end of the capillary tube (CP) in the auxiliary liquid line (32).
The other end is connected between the first solenoid valve (SV1) and the other end of the ice prevention device (47).
Connected to each other. Also, this progress prevention refrigerant outlet pipe
(61) has a capillary tube (CP). As a result, the ice nucleus generator (4) is heated by heating the wall of the water pipe (45a) with the refrigerant introduced from the propagation prevention refrigerant introduction pipe (60).
6) to stop ice from developing.

Further, the mixer (41) and the supercooler (4)
3) is composed of a hollow cylindrical container, and water is introduced from the tangential direction of the inner peripheral surface by a water pipe (45), and the water introduced into the container is swirled. This allows the mixer
In (41), as described later, the ice discharged from the heat storage tank (T) and the water heated by the preheater (40) are mixed and stirred to promote the melting of the ice, while the supercooling is performed. Elimination device (43)
In the above, the ice nuclei generated by the ice nucleus generator (46) and the supercooled water generated by the heat storage heat exchanger (42) are mixed and stirred to promote the elimination of the supercooling.

A filter (62) in FIG. 2 is a filter for removing ice and impurities contained in the water introduced into the preheater (40).

The open / close state of the four-way switching valve (2), the solenoid valves (SV1 to SV7) and the electric expansion valves (5, 6, 52a) is controlled by the controller (70). ing.

-Configuration of Sensors- Various sensors are provided in the refrigerant circuit (A) and the water circuit (B). First, in the refrigerant circuit (A), an outdoor air temperature sensor (Th-1) for detecting the outdoor air temperature is provided near the outdoor heat exchanger (3). An outdoor liquid temperature sensor (Th-2) for detecting the liquid refrigerant temperature of the compression mechanism (1) is provided on the branch pipe side, and discharge gas temperature sensors (Th-31, Th-32) for detecting the discharge gas refrigerant temperature of the compression mechanism (1). The discharge pipes (10a-1, 10a-2) of each compressor (COMP-1, COMP-2)
A suction gas temperature sensor (Th-4) for detecting a suction gas refrigerant temperature of the compression mechanism (1) is provided in each of the suction gas lines (10c) of the compression mechanism (1). Further, a high pressure sensor (SEN-H) for detecting the refrigerant pressure discharged from the compression mechanism (1) is provided to the first discharge gas line (10a), and a low pressure pressure sensor (SEN-H) for detecting the suction refrigerant pressure of the compression mechanism (1). -L) is provided in each of the upper connection pipes (51) connected to the suction gas line (10c),
The high pressure protection switches (HPS, HPS) that operate when the discharge refrigerant pressure of each compressor (COMP-1, COMP-2) reaches a predetermined high pressure are connected to the discharge pipe (10a) of each compressor (COMP-1, COMP-2). -1,10a-2).

On the other hand, in the water circulation circuit (B), an inlet water temperature sensor (Th-W1) is provided at the water inlet at the lower end of the preheater (40).
Near the water outlet at the lower end of (41), an outlet water temperature sensor (Th-W
2) The supercooled water temperature sensor (Th-W3) is provided at the water outlet side at the upper end of the heat storage heat exchanger (42), and the ice formation detection sensor (Th-W4) is provided at the supercool eliminator (43). It detects the water temperature at each part. Further, a flow switch (SW) which is turned on when the flow rate of the water in the water inlet pipe (45b) is detected at the water inlet pipe (45b) connected to the lower end of the preheater (40) and becomes lower than a predetermined value is detected. -F) is provided.

-Configuration of Control-The air conditioner of the present invention has various sensors (Th-1 to SEN-L, Th
-W1 to Th-W4), switch (HPS), and switch (SW-F) detection signals are input to the controller (70), and based on these detection signals, open / close switching of each solenoid valve (SV1 to SV7) is performed. Each electric expansion valve
(5, 6, 52a) and the capacity of the compression mechanism (1) are controlled.

-Operational Operation- Next, the operational operation of the air conditioner configured as described above will be described. The operation modes of the air conditioner include a normal cooling operation, a normal heating operation, an ice nucleation operation, a cold storage operation, a thawing operation, a simultaneous cold storage / cooling operation, a cooling operation using cold storage, a hot storage operation, and a hot storage operation. There are simultaneous heating operation and heating operation using thermal storage.

Hereinafter, the refrigerant circulation operation in each operation mode will be described.

-Normal Cooling Operation- In this operation mode, the controller (70) switches the four-way switching valve (2) to the solid line side in the drawing, and the indoor electric expansion valve
(6) is adjusted to a predetermined opening (superheat control), and the other electric expansion valves are closed. On the other hand, the second solenoid valve (SV2) is opened, and the other solenoid valves are closed.

When the compression mechanism (1) is driven in this state, the refrigerant discharged from the compression mechanism (1) passes through the four-way switching valve (2) as shown by the arrow in FIG. The heat is exchanged with the outside air in the outdoor heat exchanger (3) and condensed. Thereafter, the refrigerant is introduced into the indoor unit (Y, Y, Y) via the liquid side pipe (11) and the bypass line (34), and is depressurized by the indoor electric expansion valve (6, 6, 6). The heat exchanger (7, 7, 7) exchanges heat with room air to evaporate and cool the room air. This gas refrigerant is supplied to the gas pipe (15), the four-way switching valve (2), and the suction gas line (10
Through c), it is returned to the suction side of the compression mechanism (1). By performing such a circulation operation of the refrigerant, indoor cooling is performed.

-Normal heating operation-In this operation mode, the four-way switching valve (2) is switched to the broken line side by the controller (70), and the first outdoor electric expansion valve is operated.
While (5) is adjusted to a predetermined opening, the indoor electric expansion valve (6)
Is fully opened. Also, the second outdoor electric expansion valve (52a)
And each solenoid valve is closed together.

When the compression mechanism (1) is driven in this state, the refrigerant discharged from the compression mechanism (1) passes through the four-way switching valve (2) and the gas pipe (15) as shown by arrows in FIG. After being introduced into the indoor unit (Y, Y, Y), the indoor heat exchanger (7, 7, 7) exchanges heat with the indoor air to condense and heat the indoor air. Thereafter, the refrigerant reaches the receiver (4) via the third liquid line (11c) and the fourth liquid line (11d), flows from the receiver (4) through the second liquid line (11b), and flows into the first outdoor electric line. After the pressure is reduced by the expansion valve (5), the heat is introduced into the outdoor heat exchanger (3) from the heating liquid line (33), and the outdoor heat exchanger (3) exchanges heat with the outside air to evaporate. . After that, the compression mechanism (1) passes through the four-way switching valve (2) and the suction gas line (10c).
Is returned to the suction side. The indoor heating is performed by performing such a circulation operation of the refrigerant.

-Ice nucleus generation operation-This operation mode is for generating ice nuclei for eliminating the supercooled state of the supercooled water in the cold heat storage operation described later. In this operation mode, a water cooling operation for cooling water in the water circulation circuit (B) to a predetermined temperature (for example, 2 ° C.) is performed before the start of the ice nucleation operation. Explaining the circulation operation of water and refrigerant in the water cooling operation, the second outdoor electric expansion valve (52a) is adjusted to a predetermined opening, and the first and second electromagnetic valves (SV1, SV2) are opened. Other electric expansion valves and solenoid valves are closed. Further, the four-way switching valve (2) is switched to the solid line side. In this state, the pump (P) is driven to circulate water in the water circulation circuit (B), and the compression mechanism (1) is driven. The refrigerant discharged from the compression mechanism (1)
After condensing in the outdoor heat exchanger (3), the pressure is reduced in the second outdoor electric expansion valve (52a) through the liquid side pipe (11) and the lower connecting pipe (52), and then the refrigerant in the heat storage heat exchanger (42) Introduced into the distribution department (48c),
Here, heat exchange is performed with water flowing through each heat transfer tube (49), and the water is cooled and evaporated. Then, this refrigerant distribution section
The refrigerant in (48c) is supplied to the upper connection pipe (51) and the suction gas line.
By (10c), it is returned to the suction side of the compression mechanism (1). At this time, the upper connection pipe (51) functions as a refrigerant outlet pipe that guides the refrigerant in the refrigerant flow part (48c).

When such a water cooling operation is performed for a predetermined time and the water temperature of the water circulation circuit (B) reaches a predetermined temperature,
Move to the following ice nucleation operation.

In this ice nucleus generating operation, the controller (70)
Accordingly, the four-way switching valve (2) is set to the solid line side, the second outdoor electric expansion valve (52a) is adjusted to a predetermined opening degree, and the other electric expansion valves are closed. In addition, the first and second solenoid valves (SV1, SV1
2) is opened while other solenoid valves are closed.

In this state, in the water circulation circuit (B),
The pump (P) is driven to circulate the water cooled by the water cooling operation in the water circulation circuit (B). on the other hand,
In the refrigerant circuit (A), only the upstream compressor (COMP-1) of the compression mechanism (1) is driven. And this compressor (COM
The refrigerant discharged from P-1) is, as indicated by the arrow in FIG.
Part of the heat is introduced into the outdoor heat exchanger (3) through the four-way switching valve (2), and heat exchanges with the outside air in the outdoor heat exchanger (3) to condense. After that, this refrigerant is
(11), the bypass line (34), the lower connection pipe (52), the second outdoor electric expansion valve (52a), and the ice nucleus generating refrigerant (46). Another part of the refrigerant discharged from the compressor (COMP-1) is introduced into the auxiliary heat exchanger (30) through the auxiliary gas line (31), and the auxiliary outdoor heat exchanger (30)
Also in the above, heat exchange is performed with the outside air to condense. Thereafter, the refrigerant joins the liquid side pipe (11). The refrigerant condensed in the outdoor heat exchanger (3) and the auxiliary outdoor heat exchanger (30) is decompressed by the second outdoor electric expansion valve (52a).
After cooling the water flowing through the water pipe (45a) inside the ice nucleus generator (46) to generate ice nuclei, the ice nucleation refrigerant outlet pipe (5)
9) and is returned to the suction side of the upstream compressor (COMP-1) via the suction pipe (10c-1).

On the other hand, a part of the refrigerant flowing through the auxiliary gas line (31) is supplied from the expansion prevention refrigerant introduction pipe (60) to the ice expansion prevention device.
Heat is supplied to the pipe (47) to heat the pipe wall of the water pipe (45a), thereby preventing ice from developing along the pipe wall from the ice nucleus generator (46). Then, the refrigerant is joined to the auxiliary liquid line (32) from the expansion prevention refrigerant outlet pipe (61). For this reason,
Even in a situation where ice grows along the wall surface upstream (toward the heat storage heat exchanger (42)), so-called ice progresses, this growing ice reaches the growth preventer (47). This progress is made possible by the heat storage heat exchanger
It does not reach (42). After such an ice nucleation operation is continuously performed for a predetermined time (for example, 5 minutes), the process proceeds to a cold heat storage operation described later.

-Cold heat storage operation- In this operation mode, supercooled water is brought into contact with ice nuclei generated by the above-described ice nucleus generation operation.
The supercooled state is eliminated around the ice nuclei to generate ice for heat storage.

In this operation mode, the four-way switching valve (2) is set to the solid line side by the controller (70), the second outdoor electric expansion valve (52a) is adjusted to a predetermined opening degree, and the other electric expansions are adjusted. The valve is closed. Also, the first, second, and fourth solenoid valves (SV1, S
V2, SV4) are opened, while the other solenoid valves are closed.

In this state, in the water circulation circuit (B),
The pump (P) is driven to circulate water in the water circulation circuit (B). On the other hand, in the refrigerant circuit (A), the compression mechanism
(1) is driven, and a part of the refrigerant discharged from the compression mechanism (1) is turned into a four-way switching valve as shown by an arrow in FIG.
It is introduced into the outdoor heat exchanger (3) via (2), and heat exchanges with the outside air in the outdoor heat exchanger (3) to condense.
Thereafter, the refrigerant is supplied to the liquid side pipe (11) and the bypass line.
(34), it is introduced into the heat storage heat exchanger (42) through the lower connecting pipe (52). Further, another part of the refrigerant discharged from the compression mechanism (1) is introduced into the auxiliary heat exchanger (30) through the auxiliary gas line (31), and is connected to the outside air in the auxiliary outdoor heat exchanger (30). It exchanges heat between it and condenses. Thereafter, the refrigerant joins the liquid side pipe (11) via the auxiliary liquid line (32). Each heat exchanger (3,3
The refrigerant condensed in step (0) is reduced in pressure by the second outdoor electric expansion valve (52a). And, the refrigerant flow section of the heat storage heat exchanger (42)
The refrigerant introduced into (48c) exchanges heat with the water flowing through each heat transfer tube (49) in the refrigerant circulation part (48c) of the heat storage heat exchanger (42). Evaporate and cool the water to a supercooled state (eg -2 ° C). Then, connect the upper connection pipe (5
1) and is returned to the suction side of the compression mechanism (1) through the suction gas line (10c). Also at this time, the upper connection pipe (51) functions as a refrigerant outlet pipe that guides the refrigerant from inside the refrigerant flow part (48c).

[0096] Even in this operation, the above-described ice nucleation operation is performed at the same time. That is, the lower connecting pipe (52)
A part of the refrigerant flowing through the ice nucleus generator (46) is introduced into the ice nucleus generator (46) through the ice nucleation refrigerant introduction pipe (58). Thereby, continuous ice making can be performed. And this ice nucleus generator (46)
In the same manner as in the ice nucleation operation described above, the refrigerant that has cooled the water to generate ice nuclei passes through the ice nucleation refrigerant outlet pipe (59) and the suction gas line (10c) to the suction side of the compression mechanism (1). Will be returned.

At the same time, an auxiliary gas line (31)
A part of the refrigerant flowing through the ice is supplied to the ice progress preventing device (47), and prevents the progress of ice in the same manner as described above. As a result, the progress of the ice reaches the heat storage heat exchanger (42), in which the supercooled state of the supercooled water is eliminated, and the heat storage heat exchanger (4) is released.
2) is prevented from freezing.

The supercooled water generated by the heat storage heat exchanger (42) by performing such water and refrigerant circulation operation includes:
In the vicinity of the ice nucleus generator (46), the ice nuclei from the ice nucleus generator (46) are mixed and introduced into the supercooling canceller (43) in this state. Then, in the supercooling canceller (43), the supercooled water is released from the supercooled state around the ice nucleus with the swirling flow, thereby producing slurry-like ice for heat storage. This ice is collected in the heat storage tank (T) and stored in the heat storage tank (T).

At this time, whether or not the supercooling elimination operation is being performed in the supercooling eliminator (43) is determined by the supercooling water temperature sensor (Th-W3) and the ice formation detecting sensor (Th-W4). This is performed according to the detected water temperature. In other words, when a good ice making operation is being performed, the supercooled water temperature sensor (Th-
In W3), the supercooled water temperature (for example, -2 ° C) is detected, and in the ice formation detection sensor (Th-W4), the supercooling is eliminated and the water temperature in which ice and water are mixed (for example, 0 ° C) is detected. Then, it can be confirmed that the supercooling elimination operation is being performed by detecting these water temperatures by the respective sensors (Th-W3, Th-W4).

The compression mechanism in the cold heat storage operation
The capacity control of (1) is performed so that the water temperature detected by the supercooling water temperature sensor (Th-W3) is maintained at a predetermined temperature (for example, −2 ° C. described above). In addition, during the main operation, relatively high-temperature refrigerant flows into the preheater (40), so that ice temporarily flows out of the heat storage tank (T) into the water pipe (45), and this flows out of the preheater (40). ), The preheater (4
The ice and the water heated in (0) are stirred in the mixer (41) to melt the ice, and to prevent the ice from being mixed into the heat storage heat exchanger (42) while preventing the ice from being mixed. The operation of generating the supercooled water in (42) is performed favorably, and the supercooled water is not released from the supercooled state until it reaches the supercooled canceller (43). In other words, the heat storage heat exchanger (42)
As a result, freezing is avoided by eliminating supercooling.

-Thawing operation-In the cold heat storage operation as described above, if the supercooling of water in the heat storage heat exchanger (42) is eliminated and the heat storage heat exchanger (42) freezes, Temporarily suspend the heat storage operation and switch to the thawing operation. In this thawing operation, the second outdoor electric expansion valve (52a), the third, fourth, and sixth solenoid valves (SV3, SV4, SV6)
Is opened, and the other electric expansion valves and solenoid valves are closed. In this state, the compression mechanism (1) is driven, and the high-temperature gas refrigerant from the compression mechanism (1) is supplied to the lower connecting pipe (52) by the hot gas supply pipe (54) as shown by an arrow in FIG. Then, a part is introduced into the refrigerant circulation part (48c) of the heat storage heat exchanger (42) through the lower connection pipe (52), and the other part is introduced into the preheater (40). And the refrigerant (hot gas) introduced into the heat storage heat exchanger (42)
Melts the ice in the heat storage heat exchanger (42) by the heat. At this time, if the pump (P) of the water circulation circuit (B) is driven, the ice is slightly melted, and the ice is stored in the heat storage heat exchanger (42) by the water pressure from the pump (P). The water is easily separated from the wall surface of the water path and is washed away toward the supercooling canceller (43). Then, this refrigerant passes through the upper connection pipe (51) and the suction gas line (10c), and the compression mechanism (1)
Is returned to the suction side. On the other hand, the refrigerant introduced into the preheater (40) is supplied to the thawing bypass line (50) and the suction gas line (10
Through c), it is returned to the suction side of the compression mechanism (1). Also at this time, the upper connection pipe (51) is connected to the refrigerant flow section of the heat storage heat exchanger (42).
(48c) functions as a refrigerant outlet pipe that leads the refrigerant inside.

In the cold storage operation, the heat storage heat exchanger (4
The operation for detecting that the subcooling water temperature sensor (T-W3) is frozen when the water temperature detected by the supercooling water temperature sensor (Th-W3) suddenly rises from −2 ° C. to 0 ° C.
It is determined that ice has been generated by performing the supercooling elimination operation on the upstream side of h-W3), and the thawing operation described above is performed for a predetermined time (for example, 5 minutes). In addition, as an operation for starting the thawing operation, when the flow rate of the water detected by the flow switch (SW-F) becomes equal to or less than a predetermined value,
It is determined that ice blocks part of the water circulation circuit (B), and in this case also, the thawing operation is performed to melt the ice. When the thawing operation is completed, the cold storage operation is started again.

-Simultaneous operation of cold storage and cooling
The operation of storing ice in (T) is performed in a state where the cooling load is relatively small.

In this operation mode, the operation is performed by opening the indoor electric expansion valves (6, 6, 6) in the above-mentioned cold storage operation. That is, as indicated by arrows in FIG. 9, a part of the refrigerant condensed in the outdoor heat exchanger (3) and the auxiliary heat exchanger (30) is supplied to the indoor unit (Y, Y, Y), and Expansion valve
After the pressure is reduced at (6,6,6), it is evaporated by the indoor heat exchanger (7,7,7). And this gas refrigerant is gas pipe
(15), is returned to the suction side of the compression mechanism (1) via the four-way switching valve (2) and the suction gas line (10c). The other water and refrigerant circulation operations are the same as in the cold storage operation described above.

-Cooling / Heat Storage Cooling Operation- In this operation mode, the room is cooled while utilizing the cold heat of the ice stored in the heat storage tank (T) in the cold storage operation described above.

In this operation mode, the four-way switching valve (2) is switched to the solid line side by the controller (70), the indoor electric expansion valves (6, 6, 6) are adjusted to a predetermined opening degree, and the second outdoor While the electric expansion valve (52a) is fully opened, the first outdoor electric expansion valve (5) is closed. In addition, the fifth, sixth, and seventh solenoid valves (S
V5, SV6, SV7) are opened, and the other solenoid valves are closed.

In this state, in the water circulation circuit (B),
The pump (P) is driven to circulate water in the water circulation circuit (B). As a result, the heat storage tank is located in the water circulation circuit (B).
The cold water cooled by the ice in (T) circulates. On the other hand, in the refrigerant circuit (A), the compression mechanism (1)
As a result, the refrigerant discharged from the compression mechanism (1) partially becomes a four-way switching valve (2) as shown by an arrow in FIG.
Is introduced into the outdoor heat exchanger (3) through the outdoor heat exchanger (3).
In the above, heat exchange is performed with the outside air to condense. Thereafter, the refrigerant is supplied to the first liquid line (11a), the receiver (4),
It flows toward the indoor unit (Y, Y, Y) via the heat storage bypass pipe (53), the lower connecting pipe (52), and the third liquid line (11c). In addition, some other refrigerant flows through the hot gas supply pipe (54) and the heat storage supply pipe (55), bypassing the four-way switching valve (2) and the outdoor heat exchanger (3), and performing heat storage heat exchange. The heat is exchanged with the cold water circulating in the water circulation circuit (B) to condense the water, and is introduced into the lower connecting pipe (52). The refrigerant introduced into the lower connecting pipe (52) joins the third liquid line (11c) and flows toward the indoor unit (Y, Y, Y). The refrigerant that has reached the indoor unit (Y, Y, Y) is depressurized by the indoor electric expansion valves (6, 6, 6), and then evaporated by the indoor heat exchanger (7, 7, 7). The gas is returned to the suction side of the compression mechanism (1) through the gas pipe (15) and the suction gas line (10c). In this manner, the indoor cooling operation using the cold heat of the ice stored in the heat storage tank (T) is performed.

In the cooling operation utilizing the cold storage energy, if the water temperature detected by the supercooling water temperature sensor (Th-W3) reaches a predetermined temperature (for example, 5 ° C.), the second outdoor electric expansion valve is operated. (52a), the fifth, sixth and seventh solenoid valves (SV5, S5
V6 and SV7) are closed, and the second solenoid valve (SV2) is opened to terminate the cold storage utilizing cooling operation and switch to normal cooling operation. In other words, after the supercooled water temperature sensor (Th-W3) detects that most of the cold heat in the heat storage tank (T) has been used, the operation is switched to the normal cooling operation.

-Heat storage operation- This operation mode is for storing hot water in the heat storage tank (T) as the heat used during the heating operation.

In this operation mode, the four-way switching valve (2) is switched to the broken line side by the controller (70), the first outdoor electric expansion valve (5) is adjusted to a predetermined opening, and the second outdoor electric expansion valve is adjusted. The valve (52a) and the seventh solenoid valve (SV7) are opened, while the other electric expansion valves and solenoid valves are closed.

In this state, in the water circulation circuit (B),
The pump (P) is driven to circulate water in the water circulation circuit (B). On the other hand, in the refrigerant circuit (A), the compression mechanism
(1) is driven, and the refrigerant discharged from the compression mechanism (1) is supplied to the hot gas supply pipe (54) as shown by an arrow in FIG.
Then, the heat is supplied to the heat storage heat exchanger (42) through the heat storage supply pipe (55), where the heat is exchanged with water in the water circulation circuit (B) to heat and condense the water. The refrigerant is supplied to the lower connecting pipe (52), the third liquid line (11c), and the fourth liquid line (11d).
Through the second liquid line (11b) and the heating liquid line (33),
After the pressure is reduced by the first outdoor electric expansion valve (5), the outdoor heat exchanger
Introduced in (3). Then, in the outdoor heat exchanger (3), heat is exchanged with the outside air to evaporate, and then the air passes through the four-way switching valve (2) and the suction gas line (10c) to the suction side of the compression mechanism (1). Will be returned. By performing the circulation operation of the water and the refrigerant, the water flowing through the water circulation circuit (B) receives heat from the refrigerant in the heat storage heat exchanger (42), becomes high-temperature hot water, and enters the heat storage tank (T). Will be stored.

During the warm heat storage operation, when the water temperature detected by the inlet water temperature sensor (Th-W1) reaches a predetermined high temperature (for example, 35 ° C.), the heat storage tank
Judging that sufficient heat has been stored in (T), the operation is terminated.

-Simultaneous operation of heat storage / heating- This operation mode is a mode in which the heat storage tank is heated while heating the room.
(T) is an operation for storing hot water, which is performed in a state where the heating load is relatively small.

In this operation mode, the operation is performed by opening the indoor electric expansion valves (6, 6, 6) in the above-mentioned warm heat storage operation. That is, as shown by the arrow in FIG. 12, a part of the refrigerant discharged from the compression mechanism (1) is introduced into the indoor heat exchanger (7, 7, 7) through the gas pipe (15), and this indoor heat exchange is performed. The heat is exchanged with the room air in the chambers (7, 7, 7) to heat and condense the room air, and then join the refrigerant in the third liquid line (11c). The other water and refrigerant circulation operations are the same as in the above-described warm heat storage operation.

[0115]-Heating operation using warm heat storage-In this operation mode, the room is heated while utilizing the heat of the warm water stored in the heat storage tank (T) in the warm heat storage operation described above.

In this operation mode, the four-way switching valve (2) is switched to the broken line side by the controller (70), the first outdoor electric expansion valve (5) is adjusted to a predetermined opening, and the indoor electric expansion is adjusted. The valve (6,6,6) and the second outdoor electric expansion valve (52a) are fully opened. Further, the fourth solenoid valve (SV4) is opened, and the other solenoid valves are closed.

When the compression mechanism (1) is driven in this state, the refrigerant discharged from the compression mechanism (1) passes through the four-way switching valve (2) and the gas pipe (15) as shown by arrows in FIG. After being introduced into the indoor unit (Y, Y, Y), the indoor heat exchanger (7, 7, 7) exchanges heat with the indoor air to condense and heat the indoor air. Thereafter, the refrigerant is supplied to the third liquid line (11c).
Then, the pressure reaches the receiver (4) via the fourth liquid line (11d), and is reduced from the receiver (4) via the second liquid line (11b) by the first outdoor electric expansion valve (5). Thereafter, a part of this refrigerant is introduced into the refrigerant circulation part (48c) of the heat storage heat exchanger (42) through the second liquid line (11b) and the lower connection pipe (52), where the refrigerant flows between the refrigerant and the hot water. After heat exchange and evaporation, the upper connecting pipe (5
The gas is collected at the suction side of the compression mechanism (1) through (1) and the suction gas line (10c). Also at this time, the upper connection pipe (51) functions as a refrigerant outlet pipe that guides the refrigerant from inside the refrigerant inflow portion (48c) of the heat storage heat exchanger (42).

Then, another part of the refrigerant decompressed by the first outdoor electric expansion valve (5) is introduced into the outdoor heat exchanger (3) through the heating liquid line (33), and this outdoor heat exchanger (3) 3) After evaporating by performing heat exchange with outdoor air in
(2) and is returned to the suction side of the compression mechanism (1) through the suction gas line (10c). In this manner, the indoor heating operation using the heat of the hot water stored in the heat storage tank (T) is performed.

[0119] Also, in this heating operation utilizing the heat storage, the water temperature detected by the inlet water temperature sensor (Th-W1) reaches a predetermined temperature (for example, 20 ° C), similarly to the heating operation utilizing the cold storage described above. The second outdoor electric expansion valve (52
a) and the fourth solenoid valve (SV4) are closed to end the heating operation using the heat storage, and the operation shifts to the normal heating operation. That is,
The heat storage tank is detected by detecting the water temperature of the inlet water temperature sensor (Th-W1).
After it is determined that most of the heat in (T) has been used, the operation is switched to the normal heating operation. The air conditioning in the room is performed by each operation as described above.

The operation characteristic of the present embodiment is the operation inside the heat storage heat exchanger (42) during the cold storage operation and during the simultaneous cold storage / cooling operation. In other words, in such an operating state, as described above,
The liquid refrigerant introduced from the lower connection pipe (52) into the refrigerant flow section (48c) exchanges heat with water flowing through the heat transfer pipe (49), evaporates, and flows from the upper connection pipe (51). At this time, in the vicinity of the gas-liquid interface (G) of the refrigerant in the refrigerant flow part (48c), the refrigerant in the form of droplets is discharged from the discharge side tube plate (36) with the boiling of the refrigerant. It will scatter toward the lower surface. Then, in such a situation, the scattered refrigerant evaporates from the lower surface of the outlet side tube sheet (36), whereby the lower surface is cooled. However, in the present embodiment, since the tube sheet (36) is formed of a material having low thermal conductivity, it is difficult for this cold heat to be transmitted to the upper surface of the tube sheet (36). In other words, since the upper surface of the tube sheet (36) facing the outlet side water circulation part (48a) is not cooled, the supercooled state flowing out from the upper end of the heat transfer tube (49) to the outlet side water circulation part (48a). Even if the water comes in contact with the upper surface of the tube sheet (36), further cooling of the water is suppressed, and the supercooled state is not eliminated. For this reason, as in the conventional case, the supercooling is eliminated in the outlet side water circulation part (48a), and ice adheres to the upper surface of the tube sheet (36), and this ice grows and blocks the heat transfer tube (49). It is possible to avoid occurrence of such a situation that the user does not. For this reason, the ice making efficiency can be constantly maintained at a high level, and the reliability of the apparatus can be improved.

Further, in the present embodiment, the tube sheet (36) on the outlet side is made of a metal material, but it may be made entirely of a resin material. In this case, even if the thickness of the tube sheet (36) is reduced, sufficient heat insulating performance can be obtained, so that the tube sheet (36) can be made thinner, and accordingly, the supercooling heat exchanger (42) can be reduced in size. When such a configuration is adopted, the tube sheet (36)
Must be selected in consideration of pressure resistance and corrosion resistance.

(Modifications) Next, modifications of the first to third types for setting the thermal conductivity of the outlet side tube sheet (36) low will be described.

-Modification of First Type- First, as a modification of the first type, as shown in FIG. 14 (longitudinal sectional view of the upper end portion of the heat transfer tube), the outlet side tube sheet (36) has a two-layer structure. The lower layer (36b) is made of mild steel which has been conventionally used as a constituent material of a tube sheet.
(36a) is made of a material having a lower thermal conductivity than this mild steel. Specifically, a plate material (36a) made of a metal material used as a constituent material of the upper tube sheet (36) in the first embodiment is integrally welded to the lower layer (36b). A tube sheet (36) is formed by using a resin material or the like and bonding it to the upper side of the lower layer (36b). Further, a heat insulating paint may be applied to the upper side of the lower layer (36b). Incidentally, in FIG.
(63) is inserted into each heat transfer tube (49), and the heat transfer tube (49)
Is a resin rod that forms a water flow passage between itself and the inner peripheral surface.

According to this configuration, while the rigidity (pressure resistance) of the outlet side tube sheet (36) is sufficiently ensured by the lower layer (36b), the upper layer (36a) secures the tube sheet (36). Thermal conductivity can be reduced. That is, it is possible to provide the heat insulation function while maintaining the pressure resistance which is the original function of the tube sheet (36).

-Modification of Second Type-Next, a modification of the second type will be described. As shown in FIG. 15, this modified example also has a two-layer structure of the outlet side tube sheet (36). The upper layer (36a) is made of mild steel which has been conventionally used as a constituent material of the tube sheet, and the lower layer (36b) is made of a material having a lower thermal conductivity than the mild steel. ing. Specific materials are the same as those of the above-described first type of modification.

According to this structure, the rigidity of the outlet side tube sheet (36) is sufficiently ensured by the upper layer (36a), while the lower layer
By (36b), the thermal conductivity of the tube sheet (36) can be reduced. However, in this example, since the lower layer (36b) comes into contact with the refrigerant, when using a resin or the like as the material, it is necessary to select a material that does not corrode by the refrigerant. There is.

-Modification of Third Type- Next, a modification of the third type will be described. In this modification, as shown in FIG. 16, the outlet tube sheet (36) has a three-layer structure. The layers (36a, 36b) located on both the upper and lower sides are made of mild steel, and the intermediate layer (36c) is made of a material having a lower thermal conductivity than the mild steel. Specific materials are the same as those of the above-described first type of modification.

According to this configuration, while the rigidity of the tube sheet (36) is sufficiently ensured by the upper and lower layers (36a, 36b), the heat conduction of the tube sheet (36) is achieved by the intermediate layer (36c). And the material constituting the intermediate layer (36c) does not come into contact with water or refrigerant, so there is no need to consider rust and corrosion. Can be greatly increased.

Further, in this tube plate (36) having a three-layer structure, not only the intermediate layer (36c) but also other layers may function as a heat insulating layer.

In each of the above modifications, the tube sheet (36) is composed of two or three layers. However, it is composed of four or more layers, and at least one of the layers functions as a heat insulating layer. It is also possible to select the material.

(Second Embodiment) Next, a second embodiment according to the present invention will be described. This form is a heat transfer tube (49)
And other configurations are the same as those of the first embodiment described above.
Therefore, only the configuration of the heat transfer tube (49) will be described here.

As shown in FIG. 17, the heat transfer tube (49) according to the present embodiment has an upper end portion penetrating through the outlet side tube plate (36) and protruding into the outlet side water circulation portion (48a) by a predetermined size. ing.
That is, the upper end of the heat transfer tube (49), which is the water outflow portion, is located above the upper surface of the tube sheet (36).

The operation of this configuration will be described below. At the time of the cold storage operation described above, the water flowing through the heat transfer tube (49) to be in a supercooled state and flowing out from the upper end portion of the heat transfer tube (49) to the outlet water flowing portion (48a) is as shown in FIG. As shown by an arrow in FIG. 7, the water flows above the upper surface of the outlet side tube sheet (36) by a predetermined size and flows out to the water pipe (45d). That is,
The supercooled water flowing out of the heat transfer tube (49) flows in a region away from the upper surface of the tube sheet (36), and thus hardly comes into contact with the tube sheet (36).

Therefore, as in the case of the first embodiment described above, ice adheres to the upper surface of the tube sheet (36), and this ice grows and blocks the heat transfer tube (49). Can be avoided, the ice making efficiency can be maintained high, and the reliability of the apparatus can be improved. Therefore, even when using a tube sheet (36) formed of the same material as the conventional one,
Ice does not adhere to the tube sheet (36). Further, if the configuration of the present embodiment is combined with the configuration of the above-described first embodiment or each of the modifications, it is possible to more reliably prevent ice from adhering to the tube sheet (36).

In each of the above embodiments, the present invention is applied to a configuration in which water is introduced into the heat storage heat exchanger (42) from the lower side and supercooled water is derived from the upper side. However, conversely, the present invention is also applicable to a heat storage heat exchanger in which water is introduced from the upper side and supercooled water is derived from the lower side. The above-mentioned improvement will be made to the lower end of the plate or the heat transfer tube.

(Third Embodiment) Next, a third embodiment of the present invention will be described with reference to FIGS.

FIG. 18 shows a refrigerant circuit (A) according to this embodiment.
19 shows the details of the water circulation circuit (B). The refrigerant circuit (A) includes a compressor (1), an outdoor heat exchanger (3), a first outdoor electric expansion valve (5), and a heat storage heat exchanger (4).
2), preheater (40), indoor electric expansion valve (6), indoor heat exchanger
(7) and the accumulator (12) are connected by a refrigerant pipe (8), and the discharge side of the compressor (1) is connected to the outdoor heat exchanger (3) and the suction side is connected by a four-way switching valve (2). Indoor heat exchanger
(7), the discharge side of the compressor (1) is connected to the indoor heat exchanger (7) and the suction side is connected to the outdoor heat exchanger (3). (A state shown by a broken line in FIG. 18).

Further, first and second three-way solenoid valves are provided at two places between the first outdoor electric expansion valve (5) and the heat storage heat exchanger (42).
(CRV-1, CRV-2). Each solenoid valve (CRV-1, CRV
Explaining -2), the first three-way solenoid valve (CRV-1) located on the side of the first outdoor electric expansion valve (5) has the first port (P-1) of the three ports connected to the outdoor heat exchanger. On the (3) side, the second port (P-2) is on the second three-way solenoid valve (CRV-2) side, and on the third port (P-2).
-3) are connected between the preheater (40) and the indoor electric expansion valve (6) via the first bypass pipe (8a). The second three-way solenoid valve (CRV-2) located on the side of the heat storage heat exchanger (42)
The first port (P-1) of the three ports is the first three-way solenoid valve
On the (CRV-1) side, the second port (P-2) is on the heat storage heat exchanger (42) side, and the third port (P-3) is on the indoor heat exchanger via the second bypass pipe (8b). Each is connected between (7) and the four-way switching valve (2).

Further, a third bypass pipe (8c) is provided between the outdoor heat exchanger (3) and the first outdoor electric expansion valve (5) and in the first bypass pipe (8a). The heat storage heat exchanger (42) is connected to a pilot pipe (8d) for extracting refrigerant from a position below the connection position of the upper connection pipe (51) (FIG. 2).
0), and the other end of the pilot pipe (8d) is connected to the downstream side of the accumulator (12). A part of the third bypass pipe (8c) and the pilot pipe (8d) are in contact with each other so as to be able to exchange heat, thereby constituting a pilot heat exchanger (65).

Next, the water circulation circuit (B) according to this embodiment will be described. As shown in FIG. 19, the water circulation circuit (B) according to this embodiment includes a heat storage tank (T), a pump (P), and a preheater (4).
0), the heat storage heat exchanger (42) and the subcooler (43)
By 5), water circulation (see arrows in FIG. 19) is connected in order so as to be possible. In this embodiment, an ice nucleus generator (46) is provided integrally with the subcooling canceller (43). That is, both generation of ice nuclei and elimination of supercooling are performed inside the subcooling canceller (43).
In the heat storage heat exchanger (42), an inlet for water is formed on the upper side, and an outlet is formed on the lower side. Note that (6) in FIG.
(6) is a bypass pipe for flowing the water derived from the heat storage heat exchanger (42) during the thawing operation to the upstream side of the pump (P), bypassing the subcooler (43) and the heat storage tank (T). And
(67) pumps part of the water flowing out of the preheater (40) (P)
This is a return pipe for returning to the upstream side of.

Next, the heat storage heat exchanger (4
The configuration 2) will be described. Here, only differences from the heat storage heat exchanger (42) of the above-described first embodiment will be described. Further, as described above, since the heat storage heat exchanger (42) of the present embodiment has the water inlet formed on the upper side and the outlet formed on the lower side, the inlet tube sheet (37) is formed on the upper side. Outlet tube sheet
(36) will be located below each. The upper space defined by the inlet tube sheet (37) is an inlet water circulation section (48b), and the lower space defined by the outlet tube sheet (36) is the outlet water circulation section. (48a).

As shown in FIG. 20, in the heat storage heat exchanger (42) of the present embodiment, the outlet side tube sheet (36) is constituted by a pair of plate members (68, 69) having a predetermined interval in the vertical direction. I have. The lower connecting pipe (52) is connected to the space (C) between the plate members (68, 69) so that a refrigerant can be introduced. Further, a pressure reducing pipe (75) as a communication pipe is erected between the space (C) and the refrigerant flow part (48c), and the second outdoor electric expansion valve ( 52a) is provided. The degree of opening of the second outdoor electric expansion valve (52a) is adjusted so as to keep the degree of superheating of the refrigerant drawn out of the pilot pipe (8d) and superheated in the pilot heat exchanger (65) constant.

Next, the operation of the present embodiment during the cold storage operation will be described. During this cold storage operation, the water circulation circuit
In (B), the pump (P) is driven and the water circulation circuit
Water circulates in (B). On the other hand, in the refrigerant circuit (A), the four-way switching valve (2) is switched to the solid line side in FIG.
Three-way solenoid valve (CRV-1) has 1st port (P-1) and 3rd port
(P-3) and the second three-way solenoid valve (CRV-2) is in a switching state for communicating the second port (P-2) and the third port (P-3). . The opening degree of the second outdoor electric expansion valve (52a) is controlled so as to keep the degree of superheating of the refrigerant in the pilot pipe (8d) downstream of the pilot heat exchanger (65) constant, and the indoor electric expansion valve (6) Is fully closed, and the first outdoor electric expansion valve (5) is fully opened. As a result, as shown by solid arrows in FIG. 18, the refrigerant discharged from the compressor (1) is introduced into the outdoor heat exchanger (3) through the four-way switching valve (2), and The heat is exchanged with the outside air in the vessel (3) to condense. Thereafter, the refrigerant is supplied to the preheater (4
Through the lower connection pipe (52) through the lower connection pipe (52), the heat is introduced into the space (C) between the respective plate members (68, 69) in the heat storage heat exchanger (42). This space
The refrigerant introduced into (C) heats each plate (68, 69) and then flows through the pressure reducing pipe (75), where the second outdoor electric expansion valve
The pressure is reduced by (52a). The low-pressure refrigerant is introduced into the refrigerant distribution section (48c), exchanges heat with water flowing in the heat transfer pipe (49), evaporates, and evaporates.
It will be derived from (51). In addition, the refrigerant distribution section (48
c) Some of the refrigerant near the gas-liquid interface (G)
After being led out to (8d) and superheated in the pilot heat exchanger (65), it is returned to the compressor (1). This pilot pipe (8
d) is arranged so as to be inclined downward toward the downstream side, and has the function of collecting the lubricating oil near the gas-liquid interface (G) to the compressor (1) and the height of the gas-liquid interface (G). It has a function to adjust the length.

As described above, according to the present embodiment, since the outlet side tube sheet (36) located on the low temperature side is heated by the refrigerant flowing through the space (C), particularly, the lower plate material ( Even if supercooled water comes into contact with the lower surface of (69), further cooling of the water is suppressed, and the supercooled state is not eliminated. Therefore, according to this embodiment, the tube sheet
It is possible to avoid, for a long period of time, a situation in which ice adheres to (36) and this ice grows and blocks the heat transfer tube (49).

As a modification of the embodiment in which the tube sheet (36) is constituted by a pair of plate members (68, 69) as in the present embodiment, a space (C) formed between the plate members (68, 69) is formed. ) May be used as a closed space, and this space (C) may be evacuated, or the space (C) may be filled with air or the like (inert gas, etc.). (48a)
Can be insulated from the coolant by a simple configuration, and the formation of ice on the tube sheet (36) can be avoided.

In this embodiment, the case where the present invention is applied to a configuration in which water is introduced into the heat storage heat exchanger (42) from the upper side and supercooled water is derived from the lower side is described. However, conversely, the present invention can also be applied to a heat storage heat exchanger in which water is introduced from the lower side and supercooled water is derived from the upper side. It will be composed of a double structure.

Further, in the refrigerant circulation circuit (A) of the present embodiment, all of the refrigerant introduced into the refrigerant circulation part (48c) is once in a space.
(C), but the present invention is not limited to this, and a part of the refrigerant derived from the outdoor heat exchanger (3) is introduced into the space (C), and other refrigerants are individually After the pressure is reduced by the expansion valve, the refrigerant may be introduced into the refrigerant flow section (48c). The refrigerant introduced into the space (C) is not limited to the one derived from the outdoor heat exchanger (3), and the temperature of the tube sheet (36) is equal to or higher than a predetermined temperature (the supercooling water is not cooled. Any refrigerant may be circulated as long as the temperature is maintained at or above the temperature.

(Fourth Embodiment) Next, a fourth embodiment according to the present invention will be described. This embodiment is an improvement of the heat storage heat exchanger (42), and the other configuration is the same as that of the first embodiment described above. Therefore, here, only the configuration of the heat storage heat exchanger (42) will be described. explain.

As shown in FIG. 21, the container (48) of the heat storage heat exchanger (42) in the present embodiment comprises a main body (48A) and a lid (48B).
And The main body (48A) has a cylindrical shape, and its upper end surface is joined to the lower surface of the outlet side tube sheet (36). On the other hand, the lid (48B) has a bottomed cylindrical shape, and its lower end, which is the open side, is joined to the upper surface of the outlet side tube sheet (36). That is, the outlet-side tube sheet (36) is sandwiched between the main body (48A) and the lid (48B), and the refrigerant flow section () is formed inside the main body (48A). 48c) and an outlet-side water circulation section (48a) formed inside the lid (48B). The outer diameters of the main body (48A) and the lid (48B) are substantially the same, while the outer diameter of the outlet side tube sheet (36) is the same as that of the main body (48A) and the lid (48B). It is set larger than the outer diameter dimension. In other words, the outer peripheral portion of the outlet side tube sheet (36) is a protruding portion (36d) that protrudes further outward than the main body (48A) and the lid (48B).

An annular groove (80) in a plan view is formed on the upper surface of the projecting portion (36d) so as to surround the periphery of the lid (48B). The groove (80) has a substantially U-shaped cross section, and the radius of curvature at the bottom thereof substantially matches the radius of the liquid-side pipe (11).

A part of the liquid side pipe (11) (for example, the first liquid line (11a)) is fitted in the groove (80). Thereby, the outlet side tube sheet (36) is in a state of being constantly in contact with the liquid side pipe (11). That is, heat exchange is possible between the refrigerant flowing through the liquid side pipe (11) and the outlet side tube sheet (36).

The operation of this configuration will be described below. At the time of the cold storage operation described above, the outdoor heat exchanger
The high-temperature liquid refrigerant condensed in (3) flows through the liquid-side pipe (11).
The liquid refrigerant flowing through the liquid-side pipe (11) exchanges heat with the outlet-side tube sheet (36) to heat the outlet-side tube sheet (36).

Thus, the outlet tube sheet (36) can be maintained at a higher temperature than the supercooled water flowing through the outlet water flow part (48a). Therefore, it is possible to avoid a situation in which ice adheres and forms on the upper surface of the tube sheet (36), and this ice grows and closes the heat transfer tube (49). The reliability of the device can be improved.

(Modification) Next, the first to fourth embodiments of the fourth embodiment will be described.
A modification of the third type will be described.

-First Type Modification- First, as a first type modification, as shown in FIG.
A groove (80) is formed on the outer peripheral end surface of the projecting portion (36d) of the outlet side tube sheet (36) over the entire periphery thereof, and a part of the liquid side pipe (11) is formed in the groove (80). It is fitted.

Also in this embodiment, the outlet side tube sheet (36) can be maintained at a relatively high temperature, and ice adheres and forms on the upper surface of the tube sheet (36), and the ice grows to form the heat transfer tube (49). Can be avoided.

-Modification of Second Type-This modification is a modification of the joining state of the liquid side pipe (11) to the groove (80) formed in the outlet side tube sheet (36). In the above-described fourth embodiment (FIG. 21) and the modification of the first type (FIG. 22), a brazing material (not shown) is poured between the groove (80) and the liquid side pipe (11). . Thereby, the liquid side piping (11)
Are integrally joined to the inner surface of the groove (80), so that separation of the liquid side pipe (11) can be prevented. Further, since the adhesion between the liquid side pipe (11) and the groove (80) is improved, the heat conduction between the two (11, 80) is favorably performed. Therefore, the outlet tube sheet (3
The heating of 6) can be reliably performed, and the reliability of the function of inhibiting the growth of ice on the upper surface of the tube sheet (36) can be maintained at a high level.

-Modification of Third Type-In this example, the liquid-side pipe (11) is fitted into the groove (80) formed on the upper surface of the outlet-side tube sheet (36) as in the above-described fourth embodiment. This is a modification of the lid (48B) in such a case. As shown in FIG. 23, the lid (48B) of the heat storage heat exchanger (42) according to the present embodiment has a plurality of (four in this example) regulating members extending radially outward at the lower end thereof. Plates (82, 82, ...) are protruded. FIG.
When the lid (48B) is joined to the upper surface of the outlet side tube sheet (36) as shown in FIG. 3 (b), the holding plate (82, 82,...) The upper side of the side pipe (11) will be pressed down.

According to the structure of this embodiment, the situation in which the liquid side pipe (11) is separated from the groove can be surely prevented.

Further, as a member for holding down the liquid side pipe (11), holding plates (82, 82,...) Are provided at predetermined intervals in the circumferential direction, but the lower end of the lid (48B) is provided. A configuration in which a flange-shaped pressing plate is provided on the entire circumference of the above-described configuration may be adopted.

-Modification of Fourth Type- This embodiment is a modification of the flow path of the liquid refrigerant for performing heat exchange with the outlet tube plate (36). As shown in FIG. 24, the outlet side tube sheet (36) according to the present example has a plurality of through holes (80, 8
0,...), And the inside of the through holes (80, 80,...) Serves as a flow passage for the liquid refrigerant. These through holes (80,
Although not shown, they are joined at both ends on the upstream side and the downstream side, and are provided at positions where they do not interfere with the heat transfer tubes (49, 49,...). This merged through hole (8
0,80,...) Communicate with the liquid side pipe (11), respectively.

According to this configuration, heat is exchanged with the liquid refrigerant also in the central portion of the outlet tube sheet (36), and the entire outlet tube sheet (36) can be maintained at a relatively high temperature. . In other words, in each of the above-mentioned types, there is a concern that ice will adhere to the center portion of the outlet side tube sheet (36), but according to the present example, such a situation can be avoided.

-Fifth Modified Example- This example is an improvement in order to easily obtain the configuration of the fourth type modified example described above. As shown in FIG. 25, the outlet side tube sheet (36) of this example is formed by stacking two plate members (36A, 36B). Specifically, the surface of each plate (the lower surface of the upper plate (36A) and the upper surface of the lower plate (36B))
A groove (80A, 80B) having a semicircular cross section is formed, and these plate materials (36A, 36B) are overlapped so that their surfaces are in contact with each other. (3
6) is configured.

As described above, according to this example, each plate (36A, 3
By forming grooves (80A, 80B) in 6B) and superimposing them, the outlet tube sheet (36) having the refrigerant flow passage (80) therein can be manufactured. Therefore, it is possible to obtain the outlet side tube sheet (36) that can achieve the same effect as that of the above-described modification of the fourth type by a relatively simple manufacturing operation.

In the above-described fourth embodiment and its modifications, the outlet tube plate (36) is heated by the high-pressure liquid refrigerant flowing through the liquid pipe (11). The outlet-side tube sheet (36) may be heated by the gas refrigerant discharged from the outlet. Also, without providing the groove (80) in the tube sheet (36), the piping (1
1) may be directly brazed to the tube sheet (36).

In each of the above embodiments, water is used as the heat storage medium for heat storage. However, an aqueous brine solution or the like may be used. Also, the case where the present invention is applied to an ice heat storage device for an air conditioner has been described, but the present invention is also applicable to other devices utilizing cold storage heat.

In the first, second and fourth embodiments described above, the directions of flow of the refrigerant and water inside the heat storage heat exchanger (42) are the same, and in the third embodiment, Although the directions are reversed, these distribution directions are not limited to this.

In each embodiment, the heat storage heat exchanger (42)
Although the supercooler and the supercooler (43) are provided separately, they may be integrated. Further, the preheater (40) and the heat storage heat exchanger (42) may be integrated.

[0169]

As described above, according to the present invention, the following effects can be obtained. According to the invention as set forth in claim 1, an ice heat storage device that supercools a heat storage medium by a liquid-filled shell-and-tube heat exchanger and eliminates the supercooled state to generate ice. By forming at least a part of the tube sheet on the side where the heat storage medium in the supercooled state flows is made of a material having a lower thermal conductivity than the material constituting the container of the heat exchanger, the surface located on the refrigerant circulation space side Even if is cooled by evaporation of the refrigerant, it is difficult for cold to be transmitted to the surface facing the heat storage medium outlet space. For this reason, the heat storage medium in the supercooled state flowing out of the heat transfer tube can be suppressed from being further cooled by the tube sheet, and the occurrence of the operation of eliminating the supercooling in the heat storage medium lead-out space can be prevented. Therefore, it is possible to avoid a situation in which the heat transfer tube is clogged by the ice, and it is possible to always keep the ice making efficiency stable and high, thereby improving the reliability of the apparatus.

According to the second aspect of the present invention, since the tube sheet is composed of a plurality of layers, and at least one of the layers is formed of a material having a lower thermal conductivity than the material constituting the container, it has a heat insulating function. It is possible to provide a layer having a pressure-resistant function and a layer having a pressure-resistant function, and to provide a heat-insulating function while maintaining the pressure resistance required of the tube sheet, thereby improving the practicality of the tube sheet. Can be.

According to the third aspect of the present invention, since at least one of the layers constituting the tube sheet is made of a resin material, the heat insulating function of the tube sheet can be further improved.
It is possible to more reliably prevent the supercooling elimination operation in the heat storage medium lead-out space.

According to the fourth aspect of the invention, the tube sheet has a three-layer structure, the outer layers are formed of a metal material, the intermediate layer is formed of a resin material, and the intermediate layer is formed of a heat storage medium or a refrigerant. Since the contact is prevented, the material constituting the heat insulating layer can be selected without considering corrosion due to the heat storage medium or the refrigerant, and the degree of freedom in selecting the material can be improved.

According to the fifth aspect of the present invention, since the entire tube sheet is formed of a resin material, sufficient heat insulating performance can be obtained even if the thickness of the tube sheet is reduced. For this reason, it is possible to reduce the size of the supercooling heat exchanger accompanying the thinning of the tube sheet while securing the effect according to the first aspect of the present invention, and obtain a highly practical supercooling heat exchanger. be able to.

According to the sixth aspect of the present invention, the heat transfer tube is extended inside the heat storage medium outlet space so that the heat storage medium flowing into the heat storage medium outlet space does not flow along the tube sheet. Even when the tube sheet is made of the same material, the supercooling elimination operation is not performed in the heat storage medium outlet space, and the ice making efficiency is always stable with a simple configuration such as improving the arrangement of the heat transfer tubes Therefore, it can be maintained high, and the reliability of the device can be improved.

According to the seventh aspect of the present invention, since the tube sheet is constituted by a pair of plate members forming a space at a predetermined interval, the space is formed by the refrigerant in the refrigerant circulation space,
Since the heat insulation of the surface of the tube sheet facing the heat storage medium lead-out space is performed, according to the present invention, the occurrence of the operation of eliminating supercooling in the heat storage medium lead-out space can be prevented, and the reliability of the device can be reduced. Improvement can be achieved.

According to the eighth aspect of the present invention, the space between the plate members is filled with a heat insulating gas. According to the ninth aspect of the present invention, the space is evacuated so that the space can be formed with a simple structure. High heat insulation performance can be provided,
The practicality of the device can be improved.

According to the tenth aspect of the present invention, by introducing a refrigerant for maintaining the temperature of the plate material at a predetermined value or more into the space between the plate materials, the surface of the plate material facing the heat storage medium lead-out space is reduced. Can be always maintained at a temperature at which the supercooling elimination is not performed, and the occurrence of the supercooling elimination operation in the heat storage medium lead-out space can be more reliably prevented.

According to the eleventh aspect of the present invention, the high pressure side pipe of the refrigerant pipe is connected to the space between the plate members,
Provide a communication pipe that communicates this space and the refrigerant circulation space,
An expansion mechanism is provided in the communication pipe so that the plate material facing the heat storage medium outlet space is always heated by the refrigerant, so that overcooling operation in the heat storage medium outlet space for a long period of time is ensured. Can be prevented.

According to the twelfth aspect of the present invention, the tube sheet exchanges heat with the refrigerant having a higher temperature than the heat storage medium flowing through the heat storage medium outlet space among the refrigerant flowing through the refrigerant circuit. Therefore, in the present invention, the tube sheet can be maintained at a relatively high temperature, and even if the supercooled heat storage medium flowing out of the heat transfer tube into the heat storage medium outlet space comes into contact with the tube sheet, the heat storage medium is formed by the tube sheet. Further cooling is suppressed. Therefore, it is possible to avoid a situation in which the heat transfer tube is clogged by the ice, and the ice making efficiency can be constantly maintained at a high level.

In the present invention, the tube sheet is heated by a relatively high-temperature refrigerant. For this reason, the occurrence of the supercooling elimination operation in the heat storage medium lead-out space is reliably prevented, and the reliability of the function of preventing the heat transfer tube from being blocked by ice can be further improved.

According to the fifteenth aspect, in the heat storage device, the pipe through which the relatively high-temperature refrigerant flows is brazed to the tube sheet. This increases the area of contact between the pipe and the tubesheet,
Heat conduction between the two is performed well. Therefore, the heat transfer between the two is performed well, and it is possible to more reliably prevent the heat transfer tube from being blocked by the ice.

According to the sixteenth aspect of the present invention, a groove is formed in a projecting portion of the tube sheet projecting outward from the outer peripheral surface of the container.
The pipe is fitted into this groove. In the invention according to claim 17, this groove is formed on one surface in the thickness direction of the tube sheet,
According to the eighteenth aspect, the grooves are formed on the outer peripheral end surface of the tube sheet. Therefore, the pipe can be held on the tube sheet, and the contact area between the two can be relatively large, so that the tube sheet can be sufficiently heated.

According to the nineteenth aspect, the pipe is brazed to the inner surface of the groove. As a result, the liquid-side pipe can be prevented from coming off from the groove, and the adhesion between the liquid-side pipe and the groove is improved. Can be more reliably prevented from being blocked.

According to the twentieth aspect, the groove is formed on the surface of the tube sheet on the lid side, and the opening side of the groove is closed by the restricting portion formed on the lid. Thereby, detachment of the pipe can be prevented, and good contact between the outer peripheral surface of the pipe and the inner peripheral surface of the groove can be obtained. Also, special means such as fasteners for preventing the pipe from being detached from the tube sheet are not required.

According to the twenty-first aspect, a flow passage through which a high-temperature refrigerant flows is formed inside the tube sheet. In the invention according to claim 22, the flow passage is extended in a direction orthogonal to the thickness direction of the tube sheet. Thereby, the tube sheet can also be used as a member for flowing a relatively high-temperature refrigerant, and a special structure for bringing the outer peripheral surface of the pipe into contact with the tube sheet is not required, and the number of parts can be reduced. .

According to the twenty-third aspect of the present invention, grooves extending in a direction perpendicular to the thickness direction are formed in a plurality of plate members, and these plate members are overlapped with each other to form a flow passage by each groove. With this, it is possible to form a flow passage through which a refrigerant having a higher temperature than the heat storage medium flowing through the heat storage medium lead-out space flows inside the tube sheet with a relatively simple manufacturing operation. Can be improved.

[Brief description of the drawings]

FIG. 1 is a diagram illustrating an entire configuration of a refrigerant circuit provided in an air conditioner according to a first embodiment.

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

FIG. 3 is a cross-sectional view showing the internal structure of the heat storage heat exchanger.

FIG. 4 is a circuit diagram showing a refrigerant circulation operation in a normal cooling operation.

FIG. 5 is a circuit diagram showing a refrigerant circulation operation in a normal heating operation.

FIG. 6 is a circuit diagram showing a refrigerant circulation operation of the ice nucleus generation operation.

FIG. 7 is a circuit diagram showing a refrigerant circulation operation of the cold storage operation.

FIG. 8 is a circuit diagram showing a refrigerant circulation operation of a thawing operation.

FIG. 9 is a circuit diagram showing a refrigerant circulation operation of the cold storage / cooling simultaneous operation.

FIG. 10 is a circuit diagram showing a refrigerant circulation operation in a cooling operation utilizing cold storage heat.

FIG. 11 is a circuit diagram showing a refrigerant circulation operation of the heat storage operation.

FIG. 12 is a circuit diagram showing a refrigerant circulation operation of the simultaneous heat storage / heating operation.

FIG. 13 is a circuit diagram showing a refrigerant circulation operation of the heating operation using the heat storage.

FIG. 14 is a cross-sectional view of an upper end portion of a heat transfer tube according to a modification of the first type.

FIG. 15 is a diagram corresponding to FIG. 14 according to a modification of the second type.

FIG. 16 is a diagram corresponding to FIG. 14 according to a modification of the third type.

FIG. 17 is a diagram corresponding to FIG. 14 in the second embodiment.

FIG. 18 is a diagram corresponding to FIG. 1 in a third embodiment.

FIG. 19 is a diagram corresponding to FIG. 2 in the same embodiment.

FIG. 20 is a diagram corresponding to FIG. 3 in the same embodiment.

FIG. 21 is a cross-sectional view showing an upper part of a heat storage heat exchanger according to a fourth embodiment.

FIG. 22 is a diagram corresponding to FIG. 21 according to a modification of the first type in the same embodiment.

FIGS. 23A and 23B show a second type of modification of the embodiment, in which FIG. 23A is a plan view of a lid portion, and FIG.

FIG. 24 is a diagram corresponding to FIG. 21 according to a modification of the third type in the same embodiment.

FIG. 25 is a diagram corresponding to FIG. 21 according to a modification of the fourth type in the embodiment.

[Explanation of symbols]

 (1) Compressor (3) Outdoor heat exchanger (heat source side heat exchanger) (8) Refrigerant piping (11) Liquid side piping (high pressure side piping) (36) Tube plate (42) Heat storage heat exchanger (supercooling) (42a) Refrigerant heat exchange part (42b) Heat storage medium heat exchange part (45) Circulation piping (48) Vessel (48a) Water circulation part (heat storage medium lead-out space) (48c) Refrigerant circulation part (refrigerant circulation space) (48A) Main body (48B) Lid (49) Heat transfer tube (52a) Second outdoor electric expansion valve (expansion mechanism) (68) Upper plate (69) Lower plate (75) Decompression pipe (communication pipe) (80) Groove (82) Holding plate (regulator) (A) Refrigerant circulation circuit (B) Water circulation circuit (C) Space (P) Circulation means (T) Heat storage tank

 ──────────────────────────────────────────────────の Continuing on the front page (72) Isao Kondo, Inventor 1304, Kanaokacho, Sakai-shi, Osaka Daikin Industries Inside the Kanaoka Plant of Sakai Seisakusho Co., Ltd. Sakai Factory Kanaoka Factory

Claims (23)

[Claims] 1. A compressor (1), a heat source side heat exchanger (3),
Expansion mechanism (52a) and refrigerant heat exchange part of subcooling heat exchanger (42)
(42a) is connected to the refrigerant pipe (8) so that the refrigerant can circulate in the refrigerant circuit (A) .The heat storage tank (T) for storing the heat storage medium and the heat storage medium are pumped. The heat exchange unit (4) of the supercooling heat exchanger (42) capable of exchanging heat between the circulation unit (P) and the refrigerant heat exchange unit (42a).
2b) and a heat storage circulation circuit (B) connected by a circulation pipe (45) so that the heat storage medium can be circulated, wherein the refrigerant evaporated in the refrigerant heat exchange section (42a) and the heat storage medium heat exchange section (42b) The heat storage medium in the liquid phase flowing through (42b) is subjected to heat exchange to cool the heat storage medium to a supercooled state, and after the heat storage medium is led out from the supercooled heat exchanger (42), the supercooled state is eliminated. In the ice heat storage device configured to generate ice and collect the ice in the heat storage tank (T), the supercooling heat exchanger (42) includes a heat storage medium outlet space (48a) inside the container (48). ), And a heat transfer tube (49) whose upstream side communicates with the circulation pipe (45) and whose downstream end opens into the heat storage medium outlet space (48a). 42b)
Is composed of a heat storage medium outlet space (48a) and a heat transfer tube (49), while the refrigerant heat exchange section (42a) is a tube plate inside the container (48).
A refrigerant flow space (48c) is formed around the heat transfer tube (49), which is partitioned from the heat storage medium outlet space (48a) by (36), and allows the refrigerant to flow in a substantially full state. The heat exchange between the refrigerant in the space (48c) and the heat storage medium flowing in the heat transfer tube (49) toward the heat storage medium outlet space (48a) is performed, and the tube sheet (36) Is an ice heat storage device characterized in that at least a part thereof is made of a material having a lower thermal conductivity than a material constituting the container (48). 2. The tube sheet (36) is composed of a plurality of layers (36a to 36c), and at least one of the layers is formed of a material having a lower thermal conductivity than a material of the container (48). The ice heat storage device according to claim 1, wherein 3. The ice heat storage device according to claim 2, wherein at least one of the layers is made of a resin material. 4. The tube sheet (36) has a three-layer structure, in which both outer layers (36a, 36b) are formed of a metal material, and the intermediate layer (36c) is formed of a resin material. The ice heat storage device according to claim 1. 5. The ice heat storage device according to claim 1, wherein the tube sheet (36) is entirely formed of a resin material. 6. A compressor (1), a heat source side heat exchanger (3),
Expansion mechanism (52a) and refrigerant heat exchange part of subcooling heat exchanger (42)
(42a) is connected to the refrigerant pipe (8) so that the refrigerant can circulate in the refrigerant circuit (A) .The heat storage tank (T) for storing the heat storage medium and the heat storage medium are pumped. The heat exchange unit (4) of the supercooling heat exchanger (42) capable of exchanging heat between the circulation unit (P) and the refrigerant heat exchange unit (42a).
2b) and a heat storage circulation circuit (B) connected by a circulation pipe (45) so that the heat storage medium can be circulated, wherein the refrigerant evaporated in the refrigerant heat exchange section (42a) and the heat storage medium heat exchange section (42b) The heat storage medium in the liquid phase flowing through (42b) is subjected to heat exchange to cool the heat storage medium to a supercooled state, and after the heat storage medium is led out from the supercooled heat exchanger (42), the supercooled state is eliminated. In the ice heat storage device configured to generate ice and collect the ice in the heat storage tank (T), the supercooling heat exchanger (42) includes a heat storage medium outlet space (48a) inside the container (48). ), And a heat transfer tube (49) whose upstream side communicates with the circulation pipe (45) and whose downstream end opens into the heat storage medium outlet space (48a). 42b)
Is composed of a heat storage medium outlet space (48a) and a heat transfer tube (49), while the refrigerant heat exchange section (42a) is a tube plate inside the container (48).
A refrigerant flow space (48c) is formed around the heat transfer tube (49), which is partitioned from the heat storage medium outlet space (48a) by (36), and allows the refrigerant to flow in a substantially full state. The heat exchange between the refrigerant in the space (48c) and the heat storage medium flowing in the heat transfer tube (49) toward the heat storage medium outlet space (48a) is performed. Is an ice heat storage device characterized in that the heat storage medium flowing out of the heat storage medium outlet space (48a) is extended inside the heat storage medium outlet space (48a) so as not to flow along the tube sheet (36). . 7. A compressor (1), a heat source side heat exchanger (3),
Expansion mechanism (52a) and refrigerant heat exchange part of subcooling heat exchanger (42)
(42a) is connected to the refrigerant pipe (8) so that the refrigerant can circulate in the refrigerant circuit (A) .The heat storage tank (T) for storing the heat storage medium and the heat storage medium are pumped. The heat exchange unit (4) of the supercooling heat exchanger (42) capable of exchanging heat between the circulation unit (P) and the refrigerant heat exchange unit (42a).
2b) and a heat storage circulation circuit (B) connected by a circulation pipe (45) so that the heat storage medium can be circulated, and a refrigerant evaporating in the refrigerant heat exchange unit (42a) and a heat storage medium heat exchange unit. (42b) The heat storage medium in the liquid phase flowing through (42b) is subjected to heat exchange to cool the heat storage medium to a supercooled state, and after the heat storage medium is led out from the supercooled heat exchanger (42), the supercooled state is eliminated. In the ice heat storage device configured to generate ice and collect the ice in the heat storage tank (T), the supercooling heat exchanger (42) includes a heat storage medium outlet space (48a) inside the container (48). ), And a heat transfer tube (49) whose upstream side communicates with the circulation pipe (45) and whose downstream end opens into the heat storage medium outlet space (48a). 42b)
Is composed of a heat storage medium outlet space (48a) and a heat transfer tube (49), while the refrigerant heat exchange section (42a) is a tube plate inside the container (48).
A refrigerant flow space (48c) is formed around the heat transfer tube (49), which is partitioned from the heat storage medium outlet space (48a) by (36), and allows the refrigerant to flow in a substantially full state. The heat exchange between the refrigerant in the space (48c) and the heat storage medium flowing in the heat transfer tube (49) toward the heat storage medium outlet space (48a) is performed, and the tube sheet (36) Is a pair of plate members (68, 69) forming a space (C) between them at predetermined intervals. 8. A space (C) between the plate members (68, 69) includes:
The refrigerant in the refrigerant circulation space (48c) and the heat storage medium outlet space (48a)
8. The ice heat storage device according to claim 7, wherein the heat storage gas is filled with a heat insulating gas for heat insulation between the plate material and the plate material facing the side. 9. The space (C) between the plate members (68, 69) includes a refrigerant in the refrigerant circulation space (48c) and a heat storage medium outlet space (48a).
8. The ice heat storage device according to claim 7, wherein a vacuum state is provided so as to insulate the plate material (69) facing the side. 10. The space (C) between the plate members (68, 69) is provided so as to prevent freezing of the heat storage medium on the surface of the plate material (69) facing the heat storage medium lead-out space (48a). 8. The ice heat storage device according to claim 7, wherein a refrigerant for maintaining the temperature of (69) at or above a predetermined value is introduced. 11. A high pressure side pipe of a refrigerant pipe (8) is connected to a space (C) between the plate members (68, 69), and the space (C) and the refrigerant circulation space (48c) are connected to each other. Connecting piping (7
The ice heat storage device according to claim 10, wherein 5) is provided, and the communication pipe (75) is provided with an expansion mechanism (52a). 12. A compressor (1) and a heat source side heat exchanger (3)
A refrigerant circulation circuit (A) in which the expansion mechanism (52a) and the refrigerant heat exchange part (42a) of the subcooling heat exchanger (42) are connected so that refrigerant can be circulated by the refrigerant pipe (8). A supercooling heat exchanger capable of exchanging heat between the heat storage tank (T) for storing the heat storage medium, the circulation means (P) for pumping the heat storage medium, and the refrigerant heat exchange section (42a). (42) Heat storage medium heat exchange section (4
2b) and a heat storage circulation circuit (B) connected by a circulation pipe (45) so that the heat storage medium can be circulated, and a refrigerant evaporating in the refrigerant heat exchange unit (42a) and a heat storage medium heat exchange unit. (42b) The heat storage medium in the liquid phase flowing through (42b) is subjected to heat exchange to cool the heat storage medium to a supercooled state, and then the supercooled state of the heat storage medium is eliminated by the eliminating means (43) to produce ice. In the ice heat storage device configured to collect the ice in the heat storage tank (T), the subcooling heat exchanger (42) includes a pipe that forms a heat storage medium outlet space (48a) inside the container (48). Plate (36), a heat transfer tube (49) having an upstream side communicating with the circulation pipe (45) and a downstream end opening into the heat storage medium outlet space (48a), and a heat storage medium heat exchange section (42b).
Is composed of a heat storage medium outlet space (48a) and a heat transfer tube (49), while the refrigerant heat exchange section (42a) is a tube plate inside the container (48).
A refrigerant flow space (48c) is formed around the heat transfer tube (49), which is partitioned from the heat storage medium outlet space (48a) by (36), and allows the refrigerant to flow in a substantially full state. The heat exchange between the refrigerant in the space (48c) and the heat storage medium flowing in the heat transfer tube (49) toward the heat storage medium outlet space (48a) is performed, and the tube sheet (36) An ice heat storage device characterized in that heat exchange is possible with a refrigerant having a higher temperature than a heat storage medium flowing through a heat storage medium outlet space (48a) among refrigerants flowing through a refrigerant circulation circuit (A). 13. The pipe sheet (36) is in contact with a pipe (11) through which a refrigerant having a higher temperature than the heat storage medium flowing through the heat storage medium outlet space (48a) among the refrigerant flowing through the refrigerant circuit (A) is conducted. ,
13. The ice heat storage device according to claim 12, wherein heat is exchanged with a refrigerant flowing through the pipe. 14. The tube sheet (36) is configured such that the high pressure side pipe (11) of the refrigerant pipe (8) is brought into contact with the pipe sheet (36) to exchange heat with the refrigerant flowing through the high pressure side pipe (11). Claim 1.
2. The ice heat storage device according to 2. 15. The ice heat storage device according to claim 13, wherein the pipe (11) is brazed to a tube sheet (36). 16. An outer peripheral portion of the tube sheet (36) protrudes to the outer peripheral side from the outer peripheral surface of the container (48), and a groove (80) is formed in the protruding portion (36d), and the pipe (11) 14. The ice heat storage device according to claim 13, wherein the ridges are fitted in the grooves. 17. The ice heat storage device according to claim 16, wherein the groove (80) is formed on one surface in the thickness direction of the tube sheet (36). 18. The ice heat storage device according to claim 16, wherein the groove (80) is formed on an outer peripheral end surface of the tube sheet (36). 19. The ice heat storage device according to claim 16, wherein the pipe (11) is brazed to an inner surface of the groove (80). 20. The container (48) includes a main body (48A) forming a refrigerant flow space (48c) on one side in the thickness direction of the tube sheet (36);
Heat storage medium outlet space (48a) on the other side in the thickness direction of the tube sheet (36)
The groove (80) is formed on the surface of the tube plate (36) on the side of the lid (48B), and the groove (80B) is formed in the lid (48B). (80) Piping fitted inside (1
17. A restricting portion (82) for closing the open side of the groove (80) so as to prevent the detachment of (1).
The ice heat storage device as described in the above. 21. A flow passage (80) through which a refrigerant having a higher temperature than the heat storage medium flowing in the heat storage medium outlet space (48a) is formed inside the tube sheet (36). The ice heat storage device according to claim 12. 22. A hole for penetrating the heat transfer tube (49) is formed in the tube sheet (36), and the flow passage (80) is formed in the direction perpendicular to the thickness direction of the tube sheet (36). The ice heat storage device according to claim 21, wherein the ice heat storage device is extended so as not to interfere with a hole for penetrating the heat transfer tube (49). 23. The tube sheet (36) is composed of a plurality of sheet materials (36A, 36B) superimposed on each other, and each sheet material (36A, 36B) has
Grooves extending in the direction perpendicular to the thickness direction (80
A, 80B) are formed, and the plate members (36A, 36B) are overlapped with each other, and the flow passages (8,
22. The ice heat storage device according to claim 21, wherein 0) is formed.