JPH0810099B2 - Ice making equipment - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an ice making device in which water or an aqueous solution in an ice storage tank is circulated to be supercooled and then the supercooled state is eliminated to form a slurry-like ice product. In particular, it relates to measures to prevent freezing of pipelines.

[0002]

2. Description of the Related Art Conventionally, a water circulation path for circulating water in an ice storage tank is provided between a heat exchanger provided in a refrigerant circuit and the ice storage tank, and ice is stored by heat exchange with the refrigerant in the refrigerant circuit. As an ice making device in which water or the like in a tank is made into slurry-like ice, for example, as disclosed in Japanese Patent Laid-Open No. 63-217171,
The outlet side of the water circulation path is an upstream side that is directed downward, and the outlet end is an inclined gutter formed so as to open at a certain height above the water surface of the ice storage tank, and a heat exchanger is interposed between the gutters. Then, the water cooled by the heat exchanger in the water circulation path is frozen at the outlet of the gutter to be frozen into a slurry, and this ice product is dropped into an ice storage tank to cool the water ice. It is a known technique to prevent the freezing of the water circulation path due to the progress of liquefaction.

Further, as disclosed in Japanese Utility Model Laid-Open No. 1-112345, a heat exchanger is provided by opening an outlet end of a water circulation path above an ice storage tank and installing an inclined gutter having a baffle plate in front of it. By releasing the supercooled water into the atmosphere and colliding with the baffle plate, the supercooled state of the water is canceled and the water is frozen, and it is dropped into the ice storage tank through the gutter. It is a known technique to more reliably prevent freezing of the water circulation path.

[0004]

However, in the latter of the above-mentioned conventional ones, since the subcooling elimination portion is provided above the ice storage tank, the distance between the heat exchanger and the subcooling elimination portion is increased. If it is long, there is a risk that the supercooled state will be eliminated in the pipe between them. Therefore, since the heat exchanger has to be provided near the ice storage tank, there is a problem that design restrictions are large, such as difficulty in processing such as bending the water pipe.

On the other hand, in the former one of the above-mentioned conventional ones, it is necessary to install a gutter having a considerable height difference on two sides of the ice storage tank as the supercooling elimination portion, which also has a large design constraint. . In addition, since it is exposed to the atmosphere for a long time, there is a problem that heat is wasted due to heat exchange with the atmosphere.

Therefore, it is conceivable to make ice in the middle of a water circulation path for circulating water or the like in the ice storage tank and send the ice in a closed pipe to the ice storage tank as it is. In that case,
In a place where the supercooled state of water that has been supercooled by the heat exchanger is eliminated and the ice is frozen, ice products adhere to the pipe wall and, if they accumulate, freeze the pipe wall and the vicinity of the pipe. There is a problem of causing a decrease.

The present invention has been made in view of the above problems, and an object thereof is to provide means for preventing freezing of a supercooling eliminating portion for eliminating a supercooled state of water or the like and icing it. This is to effectively prevent a decrease in ice making efficiency.

[0008]

In order to achieve the above object, the first solution means of the present invention is, as shown in FIG. 1A, an ice storage tank for storing a slurry of iced water or an aqueous solution. (5), a main heat exchanger (22) connected to a cooling device for supercooling water or an aqueous solution, and water or water between the ice storage tank (5) and the main heat exchanger (22). A forward conduit (51A) and a reverse conduit (51B) for forcedly circulating the aqueous solution,
It is provided in the return pipe (51B) downstream of the main heat exchanger (22) and eliminates the supercooled state of the water or aqueous solution supercooled in the main heat exchanger (22) to form a slurry-like iced substance. It is intended for an ice making device provided with a subcooling elimination unit (8).

Then, in the vicinity of the supercooling elimination section (8), the freezing for heating the return conduit (51B) so as to dissociate the adhesion of the iced substance generated in the supercooling elimination section (8) to the tube wall. The configuration is such that a prevention section (9) is provided.

A second solving means is the same as the first solving means, as shown in FIG. 2, a refrigerant circuit (1 in which a cooling device is sequentially connected to a compressor, a condenser, a pressure reducing valve and an evaporator. ), The supercooling elimination section (8) cools water or an aqueous solution by heat exchange with the refrigerant of the refrigerant circuit (1), and the freeze prevention section (9) has the refrigerant circuit ( It is said that water or an aqueous solution is heated by heat exchange with the refrigerant of 1).

As shown in FIG. 4, the subcooling elimination section (8) and the antifreezing section (9) have their refrigerant passages connected in series, and the refrigerant flows from the downstream side of the condenser to the antifreezing section. It is introduced into (9) and returned to the upstream side of the compressor from the supercooling elimination section (8), and the depressurization section (F) is provided between the freeze prevention section (9) and the supercooling elimination section (8). ) Is installed.

A third solving means is the above first or second solving means, as shown in FIG. 8, the freezing prevention section (9) is connected from the supercooling eliminating section (8) to the main heat exchanger (22). ), And has a function of preventing the progress of freezing to the main heat exchanger (22).

The fourth solution is as shown in FIG. 1B.
An ice storage tank (5) for storing a slurry of iced water or an aqueous solution, a main heat exchanger (22) connected to a cooling device for supercooling the water or the aqueous solution, and the above ice storage Forward line (51A) and return line (51) for forcedly circulating water or an aqueous solution between the tank (5) and the main heat exchanger (22).
B), the main heat exchanger (2) is provided in the return conduit (51B) downstream of the main heat exchanger (22).
The sub heat exchanger (10) is configured to repeat the cycle of heating the water or aqueous solution supercooled in 2) and the cycle of cooling.

A fifth solving means is the same as the above fourth solving means, as shown in FIG. 12, is provided with a plurality of sub heat exchangers (10) each having a different heating and cooling cycle. Is.

A sixth solving means is, in the fourth or fifth solving means, as shown in FIGS. 9 and 11, a cooling device is sequentially connected to a compressor, an evaporator, a pressure reducing valve and a condenser. The refrigerating apparatus is provided with the refrigerant circuit (1), and the sub heat exchanger (10) exchanges heat between the refrigerant in the refrigerant circuit (1) and water or an aqueous solution.

Then, the refrigerant inlet end of the sub heat exchanger (10) is connected to the liquid pipe and the discharge pipe of the refrigerant circuit (1) via the switching valve so as to alternately communicate with each other, and the sub heat exchanger (10) is connected. 2) is connected so that it communicates with the suction pipe of the refrigerant circuit (1).

The seventh solving means is any one of the above first to sixth solving means, as shown in FIGS. 14 and 15, in the return conduit (51B), the supercooling eliminating portion ( 8)
A flow velocity increasing member (75) is provided for removing the icing formed on the surface of the supercooling elimination portion (8) by increasing the flow velocity of water or the aqueous solution.

[0018]

With the above construction, in the invention of claim 1, in the return pipe (51B) downstream of the main heat exchanger (22), the supercooling elimination section (8) prevents the main heat exchanger (22) from overheating. The supercooled state of the cooled water or the like is eliminated, and a slurry-like iced substance is generated. At that time, if the produced iced substance adheres to the pipe wall of the supercooling elimination unit (8), the vicinity of the pipe wall of the supercooling elimination unit (8) freezes, which may reduce the ice making efficiency. In the invention, since the adhesion of the iced substance to the tube wall is dissociated by the antifreezing portion (9), the supercooling elimination portion (8) is prevented from freezing and the ice making efficiency is improved.

According to a second aspect of the present invention, in the first aspect of the present invention, the main heat exchanger (22) is connected to the refrigerant circuit (1) of the refrigeration system, and the freeze prevention section (9) includes the refrigerant circuit ( The relatively high temperature liquid refrigerant of 1) flows. The liquid refrigerant is cooled by heat exchange with water or an aqueous solution in the return conduit, further decompressed in the decompression section (F) to become low temperature, and flows into the supercooling elimination section (8). Therefore, since the sufficiently cooled refrigerant is supplied to the supercooling elimination section (8), heat exchange in each section can be efficiently performed without providing a separate heat source.

In the invention of claim 3, the above-mentioned claim 1 or 2
In the invention of claim 1, the freeze prevention section (9) includes a main heat exchanger (2).
Since it also functions to prevent the progress of freezing to 2), it is possible to reliably prevent a decrease in ice making efficiency with a simple configuration.

In the invention of claim 4, the main heat exchanger (22)
In the downstream return pipe (51B), the auxiliary heat exchanger (10)
As a result, the cycle of heating water, etc. and the cycle of cooling water are repeated, so that the supercooled state of water, etc. is eliminated by a single heat exchanger, and a slurry-like iced substance is generated, and the resulting ice The adhesion of the product to the pipe wall is dissociated, and the decrease in ice making efficiency due to freezing near the pipe wall is prevented.

According to a fifth aspect of the invention, in the fourth aspect of the invention, a plurality of sub heat exchangers (10) are provided, and each heating and cooling cycle is different. While passing through the exchangers (10), ..., they are alternately subjected to heating and cooling cycles, slurry-like iced substances are produced, while their adherence to the tube wall is dissociated.
This continuous action improves the ice making capacity.

In the invention of claim 6, the invention according to claim 4 or 5
In the invention, the main heat exchanger (22) is connected to the refrigerant circuit (1) of the refrigeration system, and the sub heat exchanger (9) discharges refrigerant from the refrigerant circuit (1) according to the switching of the switching valve. Since liquid and liquid refrigerant flow alternately, without providing a separate heat source,
Heating and cooling are easily performed, and the cost is reduced in each of the above inventions.

According to a seventh aspect of the present invention, in any one of the first to sixth aspects of the invention, a flow velocity increasing member (75) is provided at the location of the subcooling elimination section (8) in the return conduit (51B). Since it is provided, the hydrostatic head of the energy of the fluid changes to the speed head, and the speed head increases. Due to this increased velocity head energy, the icing formed on the surface of the supercooling elimination portion (8) is removed.

[0025]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to FIGS.

FIG. 2 shows the structure of the refrigerant circuit (1) of the air conditioner of the first embodiment according to the invention of claim 1, (11)
Is a first compressor, (12) is an outdoor heat exchanger that is arranged on the discharge side of the first compressor (11) and exchanges heat between the refrigerant and outdoor air, and (13) is the outdoor heat exchanger ( 12) An outdoor electric expansion valve for adjusting the refrigerant flow rate of 12) or for reducing the pressure, wherein the above-mentioned devices (11) to (13) are connected in series in a first conduit (14). Further, (21) is the second compressor,
(22) is arranged on the discharge side of the second compressor (21),
A water heat exchanger that is a main heat exchanger for supercooling water or an aqueous solution in an ice storage tank (5) described later, and (23) is a refrigerant flow rate when the water heat exchanger (22) functions as a condenser. Is a water-side electric expansion valve that reduces the pressure of the refrigerant when it functions as an evaporator by adjusting the above-mentioned devices (21) to (2).
3) are connected in series in the second conduit (24).

Incidentally, (SD1) and (SD2) are oil separators provided in the discharge pipes of the compressors (11) and (21), and (C1) and (C2) are the oil separators (SD1). ),
The pressure reducing capillary tubes are respectively provided in oil return pipes (RT1) and (RT2) provided on the suction sides of the compressors (11) and (21) from (SD2).
Further, (32) and (32) are indoor heat exchangers arranged in each room, and (33) and (33) are indoor electric expansion valves as pressure reducing valves for reducing the pressure of the refrigerant, and each of the devices (3)
2) and (33) are connected in series, and each set is connected in parallel in the third conduit (34).

The first conduit (14) and the second conduit (24) are connected in parallel with the third conduit (34). In addition, (Ac) is each compressor (11), (21)
Is an accumulator provided in the third pipe line (34) on the suction side of.

Further, in (2), the gas pipe of the outdoor heat exchanger (12) and the gas pipes of the indoor heat exchangers (32) and (32) are connected to the discharge sides of the compressors (11) and (21) or A four-way switching valve (2) that is switched so as to communicate alternately with the suction side. When the four-way switching valve (2) is switched to the solid line side in the figure, the outdoor heat exchanger (12) is a condenser, an indoor unit. Heat exchanger (32),
While (32) functions as an evaporator and performs the cooling operation indoors, when the four-way switching valve (2) is switched to the broken line side in the figure, the outdoor heat exchanger (12) is an evaporator and an indoor heat exchanger. (3
2) and (32) function as a condenser to perform heating operation in the room.

Further, a branch passage (25) for bypass-connecting the gas pipe of the water heat exchanger (22) and the suction pipes of the compressors (11) and (21) and the water heat exchanger (22). A water side switching valve (26) for alternately connecting the gas pipe to the discharge pipe of the second compressor (21) and the branch passage (25) is provided. The water side switching valve (26) utilizes three ports of the four-way switching valve, and when the water side switching valve (26) is switched to the solid line side in the figure, the water heat exchanger (22 ) Is connected to the branch passage (25) side, that is, the suction side of each compressor (11), (21), and the water heat exchanger (22) functions as an evaporator, while the water side switching valve (26 ) Is switched to the broken line side in the figure, the gas pipe of the water heat exchanger (22) communicates with the discharge pipe of the second compressor (21) so that the water heat exchanger (22) functions as a condenser. Has been done. In addition, (C3)
Is a capillary tube provided in the dead port side pipe of the water side switching valve (26).

Further, a bypass passage (3) for connecting the discharge pipes of the first compressor (11) and the second compressor (21) is provided, and the second compressor is provided in the bypass passage (3). A check valve (4) that allows only the refrigerant to flow from the discharge pipe side of (21) to the discharge pipe side of the first compressor (11) is interposed.

That is, when the outdoor heat exchanger (12) and the water heat exchanger (22) function as condensers, when the condensation temperature in the water heat exchanger (22) is high and the pressure is high, the second compression The gas discharged from the machine (21) is used as an outdoor heat exchanger (1
The amount of heat radiation can be distributed by letting it escape to the 2) side.

Here, the air conditioner is provided with an ice storage tank (5) for storing a slurry-like iced product of water or an aqueous solution as a heat storage medium, and the ice storage tank (5). The water and the water heat exchanger (22) are connected by a water circulation path (51) so that water or an aqueous solution can circulate. The water circulation path (51) extends from the bottom of the ice storage tank (5) to the water heat exchanger (2).
Outgoing line (51A) for supplying water etc. to 2) and returning line (51B) for returning slurry-like iced matter such as water from the water heat exchanger (22) to the upper part of the ice storage tank (5) And a pump (52) provided in the forward passage (51A) forcibly circulates the water or the aqueous solution in the ice storage tank (5) in the water circulation passage (51).

Then, the forward path (51) of the water circulation path (51)
A water circulation path (51) is provided downstream of the pump (52) of A).
A strainer (53) for removing solid matters such as iced matter and dust in the water or aqueous solution of the above is interposed, and further, a water heat exchanger (22) is provided on the downstream side of the strainer (53). A preheat heat exchanger (6) for preheating water or the like supplied to the is installed. On the other hand, the liquid line of the refrigerant circuit (1) is provided with a preheating bypass passage (61) for allowing a part of the liquid refrigerant to bypass the water side electric expansion valve (23) and flow to the preheating heat exchanger (6). A preheat electric expansion valve (62) having a refrigerant decompression function and a flow rate control function is provided downstream of the preheat heat exchanger (6) in the preheat bypass passage (61). The preheat electric expansion valve (62) and the water side electric expansion valve (23) adjust the refrigerant flow rate in the preheat bypass passage (61) and reduce the pressure of the refrigerant during the ice making operation of the water heat exchanger (22). Is also supposed to do.

Further, in the return pipe (51B) of the water circulation passage (51), the water or the like in the return pipe (51B) is cooled on the downstream side of the water heat exchanger (22) to cool the water heat exchanger. (2
A recooler (8) is provided as a supercooling elimination unit for eliminating a supercooled state of water or the like supercooled in 2), and further,
Between the recooler (8) and the water heat exchanger (22), a freezing progress prevention unit for preventing freezing of the return conduit (51B) from proceeding to the water heat exchanger (22). A heat insulation heat exchanger (7) is provided. Further, a heat retaining passage (71) for circulating a liquid refrigerant from the liquid line of the refrigerant circuit (1) to the heat retaining heat exchanger (7) is provided, while the heat retaining passage (71) is operated during the ice making operation of the water heat exchanger (22). A recooling bypass passage (81) extends from the liquid line on the downstream side of 71), and the recooling bypass passage (81) passes through the recooling capillary tube (C4) to the recooler (8). ), The refrigerant outlet end of which is connected to the compressor (11),
It is connected to a branch passage (25) on the suction side of (21).

Further, in the water circulation path (51), heaters (9A) and (9B) are provided around the recooler (8) to prevent freezing of the pipeline. The heaters (9A) and (9B) are provided on both the upstream side and the downstream side of the recooler (8).
The refrigerant inlet end is connected to the discharge pipe of the second compressor (21) via the heating bypass passage (91), and the refrigerant outlet end is downstream of the accumulator (Ac) of each compressor (11), (21). Side is connected to the suction pipe.

That is, in the recooler (8), the water etc. supercooled in the water heat exchanger (22) is recooled by heat exchange with the refrigerant decompressed in the recooling capillary tube (C4). Then, the supercooled state is eliminated to make it ice like a slurry, and the slurry-like iced matter is circulated to the ice storage tank (5) through the return conduit (51B), while the heater (9A) ，
By bypassing the discharge gas to (9B), the tube wall is heated to dissociate the adhesion of the iced substance generated by the elimination of the supercooled state to the tube wall.

Further, in the heat retention heat exchanger (7), the heat is exchanged with the liquid refrigerant in the liquid line to heat it, and the supercooling of water or the like is eliminated in the recooler (8) and the return pipe (51B). The produced frost is prevented from adhering to the pipe wall of the return pipe (51B) and freezing to the water heat exchanger (22).

Next, the operation of the air conditioner will be described. First, the four-way switching valve (2) is switched to the solid line side in the figure when the air conditioner is operating and the indoor cooling operation is performed. When the water side switching valve (26) is switched to the solid line side in the figure, the compressors (11), (2
The refrigerant discharged from 1) is condensed in the outdoor heat exchanger (12) and then evaporated in the indoor heat exchangers (32) and (32) to cool the room. Further, when the water side switching valve (26) is switched to the broken line side in the figure,
The refrigerant discharged from the first compressor (11) is the outdoor heat exchanger (12).
On the other hand, the refrigerant discharged from the second compressor (21) flows to the water heat exchanger (22), is condensed, and is circulated so as to be evaporated in the indoor heat exchangers (32) and (32).

When the electric power is cheap at night or the like, the cold storage operation for storing the cold heat in the ice storage tank (5) is performed. That is, the four-way switching valve (2) and the water side switching valve (26) are switched to the solid line side in the figure, and the indoor electric expansion valves (33), (33) are switched.
Closed and the refrigerant discharged from the compressors (11) and (21) is condensed in the outdoor heat exchanger (12).
3) (or preheat electric expansion valve (62)) to reduce pressure and evaporate in water heat exchanger (22) to supercool water or aqueous solution in ice storage tank (5) to store ice storage tank (5). Stores cold heat by icing water, etc.

Here, in the invention of claim 1, in the return pipe (51B) on the downstream side of the water heat exchanger (main heat exchanger) (22), the water supercooled by the water heat exchanger (22) is And the like are recooled by a recooler (supercooling elimination section) (8), the supercooled state is eliminated, and the ice is turned into a slurry. Then, this iced substance is forcibly circulated in the ice storage tank (5) in the form of a water slurry through the return pipe (51B), and the iced slurry in the form of a slurry is stored in the ice storage tank (5) for the daytime. The cold energy required for cooling operation is stored.

At this time, in the recooler (8), the iced substance generated by the elimination of the supercooled state of water or the like tends to adhere to the pipe wall, so if it is left as it is, it accumulates and the vicinity of the pipe wall freezes. However, there is a risk that the efficiency of ice making will decrease.
In the present invention, the return pipe (5) is provided by the heaters (freezing prevention portions) (9A) and (9B) provided around the recooler (8).
Since 1B) is heated, the adhesion of the iced substance to the tube wall is dissociated, and the freezing of the return conduit (51B) is effectively prevented. Therefore, it is possible to improve the ice making efficiency.

Next, a second embodiment according to the invention of claim 2 will be described.

A schematic configuration of the second embodiment is shown in FIG. In this embodiment, the refrigerant is guided from the main heat exchanger (12) to the heater (9) and then to the recooler (8) by utilizing the recooling bypass passage (81) of FIG. 9) to recooler (8)
And is returned to the branch passage (25) on the suction side of each compressor (11), (21). In this embodiment, the heating chamber (9a) on the upstream side and the heating chamber (9b) on the downstream side are formed so as to be freely flowable to each other in the casing slightly led out into the return conduit (51B), and the heater (9 ) Is formed, and a vertically long recooler (8) is formed between both heating chambers (9a) and (9b). Then, while the refrigerant from the main heat exchanger (22) is supplied to the upstream heating chamber (9a), the downstream heating chamber (9b) and the recooler (8) are connected to each other by a connecting pipe (84). Are connected in series via. The connecting pipe (84) has a pressure reducing valve (F) as a pressure reducing unit (F).
1) is interposed, and one end of the connecting pipe (84) is introduced to the bottom of the recooler (8) (lower part of FIG. 4). Therefore, the heater (9) has a main heat exchanger (12).
A high-pressure, high-temperature refrigerant flows into the heater (9) from the liquid refrigerant, and the liquid refrigerant heats the tube wall in the return conduit (51B) while cooling itself. Next, the refrigerant whose pressure has been reduced by the pressure reducing valve (F1) and has become lower than the temperature of the water or aqueous solution flows into the recooler (8) to cool the water or aqueous solution. Therefore, the sufficiently cooled refrigerant is supplied to the supercooling elimination section (8). still,
Reference numeral (52) is a check valve provided to prevent the reverse flow of the refrigerant, but the installation is optional.

Therefore, in the invention of claim 2, in the invention of claim 1 described above, the recooler (8), which is a supercooling elimination portion, removes water and the like by heat exchange with the refrigerant of the refrigerant circuit (1) of the refrigeration system. Since the heater (9) which is for cooling and heats the pipe by heat exchange with the refrigerant in the refrigerant circuit (1), it does not require a separate heat source for cooling and heating. It is possible to obtain the same effect as the invention of claim 1 above. In addition, the heater (9) and pressure reducing valve (F
The refrigerant which has been subjected to the cooling operation twice in 1) can sufficiently function as a low temperature refrigerant for cooling water or an aqueous solution, so that the heat can be effectively used.

FIG. 5 shows a first modification of the second embodiment. In this modified example, instead of the connecting pipe (84) and the pressure reducing valve (F1) in FIG. 4, a fine hole (F2) is bored in the partition wall that separates the recooler (8) and the heater (9). (F2) is made to function as a decompression section (F). The details will be described with reference to FIG.

FIG. 6 shows the structure of the recooler (8) and the heater (9) near the pipe. The upstream heater (9) and the downstream heater (9B) are configured such that the refrigerant is supplied from the recooling bypass passage (81) and discharged to the recooler (8) independently of each other. There is. The cooler (8) and the heaters (9A) and (9B) on both sides of the cooler (8) are housed in one square tubular casing (CA). The case (CA)
Is the return conduit (51B) so that its shaft end projects into the pipe.
Mounted on The three chambers extending in the axial direction are partitioned from each other, and the heater (9
A), a recooler (8), and a heater (9B) are formed, and heat is exchanged with water or the like through the wall surface at the shaft end in order from the upstream side. Further, each of the upstream side and downstream side heaters (9A), (9B) is connected to a recooling bypass passage (81), and each chamber (9A),
Pores (F1) and (F1) are provided in the partition walls that partition (9B) and the central recooler (8). Then, both the heaters (9A) and (9B) are individually supplied with the refrigerant from the recooling bypass passage (81), and the refrigerant is discharged from the fine holes (F1) and (F1) to the recooler (8). To be done. The pores (F1) and (F1) both have a function of reducing the pressure of the refrigerant. The other end (outlet end) of the central recooler (8) is connected to the compressors (11), (2
It is connected to the branch path (25) on the suction side of 1).
Other configurations are similar to those shown in FIG.

That is, a liquid refrigerant having a temperature higher than that of the water or the like in the return conduit (51B) circulates through each of the upstream side and downstream side heaters (9A), (9B), while the central recooler is used. In (8), a refrigerant whose pressure is reduced by the respective fine holes (F1) and (F1) and has a low temperature is circulated.

Therefore, in this modification, the same effect as that of the embodiment of FIG. 4 can be exhibited without separately providing the pressure reducing valve (F) or the connecting pipe (84).

FIG. 7 shows a second modification of the second embodiment. In this modification, instead of the pressure reducing valve (F1) of FIG. 4, the end of the connecting pipe (84) is connected to the capillary tube (F3) built in the recooler (8). Heater (9)
The refrigerant cooled in (1) is passed through the connecting pipe (84) and immediately before heat exchange with water or an aqueous solution, the capillary tube (F
It is decompressed by 3) and flows into the recooler (8). This allows the recooler (8) to efficiently exchange heat with water or an aqueous solution. Other than that, the same effects as those of the embodiment of FIG. 5 are exhibited.

Next, a third embodiment according to the invention of claim 3 will be described. FIG. 8 shows the configurations of the water heat exchanger (22), the recooler (8) and the heater (9) in the third embodiment, and the configuration of the refrigerant circuit is omitted, but the above-mentioned FIGS.
The heaters (9A) and (9B) in the figure are integrated and further extended to the water heat exchanger (22) to prevent the freezing of the water heat exchanger (22) near the pipe wall. It has a function to do. Then, the refrigerant circuit (1) is connected to the heater (9) through the heat retention passageway (71).
The relatively high temperature liquid refrigerant of is made to circulate,
Therefore, the heating bypass passage (91) is unnecessary.

Therefore, in the third aspect of the invention, the heater (9) is extended to the periphery of the recooler (8), and the recooler is constituted by a single heater (9). In addition to preventing the adhesion of iced matter to the pipe wall in (8), the return pipe (51) from the water heat exchanger (22) to the recooler (8) is also provided.
It is possible to prevent the adhesion of the iced substance to the wall of B),
Therefore, there is an advantage that the piping configuration can be simplified as compared with the invention of claim 1.

Next, a fourth embodiment according to the invention of claim 4 will be described. FIG. 9: shows the refrigerant piping system of the air conditioning apparatus which concerns on 4th Example, The sub heat exchanger (10) is interposed in the return pipe line (51B) of the water heat exchanger (22) downstream, and this sub The refrigerant inlet end of the heat exchanger (10) is connected to a recooling bypass passage (81) extending from the liquid line of the refrigerant circuit (1) via a check valve (82) and a recooling capillary tube (C4). On the other hand, the refrigerant outlet end of the sub heat exchanger (10) is connected to the compressors (11), (2
It is connected to the branch passage (25) on the suction side of 1). The recooling bypass passage (81) between the recooling capillary tube (C4) and the sub heat exchanger (10) has a second
One end of a hot gas bypass passage (92) branched and extending from the discharge pipe of the compressor (21) is connected to the hot gas bypass passage (92) to open and close the hot gas bypass passage (92). A valve (93) is interposed.

That is, when the on-off valve (93) is closed, the sub-heat exchanger (10) is recooled.
By circulating the low-temperature liquid refrigerant decompressed by the valve (C4), the sub heat exchanger (10) functions as a supercooling elimination section, while the compressor (21) opens when the on-off valve (93) opens. The hot gas discharged from the auxiliary heat exchanger (1
More passing it through 0), it has been auxiliary heat exchanger (10) so as to function as anti-freeze section. Here, as shown in FIG. 10, a fixed time tc (for example, 5 to 5
While the on-off valve (93) is closed and the low temperature (Tc) refrigerant flows through the sub heat exchanger (10) during an interval of about 10 minutes), the low temperature (Tc) refrigerant flows through the sub heat exchanger (10) for a predetermined time (for example, 1 to 2) at every constant time tc. The on-off valve (93) is opened only for about a minute) so that the liquid refrigerant having a temperature (Th) higher than that of water or the like flows.

The heaters (9A), (9B) and the heating bypass passage (91) in the refrigerant circuit (1) shown in FIG.
Is not provided. Other configurations are the same as those in FIG.

Therefore, in the invention of claim 4, the cycle of cooling water and the like in the return conduit (51B) and the cycle of heating by the sub heat exchanger (10) are alternately repeated, so that the sub heat exchanger ( During the cooling cycle of 10), the supercooled state of water or the like is eliminated to perform the freezing, while the sub heat exchanger (1
During the heating cycle of 0), by heating the return conduit (51B), it is possible to dissociate the adhesion of the iced substance to the tube wall and effectively prevent freezing near the tube wall. Therefore, there is an advantage that highly efficient ice making can be performed with a simple configuration using a single heat exchanger (10).

Next, a fifth embodiment according to the invention of claim 5 will be described. FIG. 11: shows a part of refrigerant piping system of the air conditioning apparatus which concerns on 5th Example, Comprising: The auxiliary heat exchanger (10), the recooling bypass passage (81), and the hot gas bypass passage (92) in the said FIG. Only the part is shown. Also, FIG.
2 shows the structure of the sub heat exchanger (10). Other configurations are similar to those shown in FIG.

Here, the sub heat exchanger (10) includes four sub heat exchangers (10A) in order from the upstream side of the return conduit (51B).
It is divided into 1), (10B1), (10A2) and (10B2). Then, the sub heat exchangers (10A1) and (10A2) arranged alternately are joined together by the confluence pipe (102A).
Thus, the sub heat exchangers (10B1) and (10B2) are connected in parallel by the merging pipe (102B).
The refrigerant inlet side of each of the confluent pipes (102A) and (102B) is connected in parallel to the recooling bypass passage (81) of FIG. 9 via check valves (82A) and (82B). The refrigerant outlet side of each of the merging pipes (102A) and (102B) is connected in parallel to the return pipe line (101) of FIG. On the other hand, the tip of the hot gas bypass passage (92) shown in FIG.
02A) and (102B) on the refrigerant inlet side of the check valve (82
A) and (82B) are connected to the upstream side portion, and the hot gas bypass passage (9
A three-way switching valve (94) is provided for switching so as to selectively communicate 2) with the merging pipe (102A) or (102B). That is, when the three-way switching valve (94) is switched to the solid line side in the figure, each sub heat exchanger (10A1),
The refrigerant (A) flowing through (10A2) is reduced in temperature by the recooling capillary tube (C4) introduced through the recooling bypass passage (81) and has a low temperature, while each sub heat exchanger ( Refrigerant (B) flowing through 10B1) and (10B2)
Will be of high temperature introduced via the hot gas bypass (92). Also, when the three-way switching valve (94) is switched to the broken line side in the figure, each sub heat exchanger (10A1
), (10A2), (10B1), and (10B2), the temperatures of the refrigerants (A) and (B) flowing are switched between high and low. FIG. 13 shows each sub heat exchanger (10
A1), (10A2) and (10B1), (10B2)
Showing changes in the temperature of the refrigerant (A) (shown by the solid line in the figure) and the refrigerant (B) (shown by the broken line in the figure) flowing in the temperature range, and the temperature of the refrigerant every constant time t0 (for example, about 5 to 10 minutes) The high and low levels of the temperature change alternately between the high temperature Th and the low temperature Tc.

Therefore, according to the invention of claim 5, in the invention of claim 4, the sub heat exchangers (10A1) to (1) are used.
0B2) are arranged and each sub heat exchanger (10A1)
), (10A2) and (10B1) and (10B2), the heating and cooling cycles of the refrigerants are different, so that water or the like is used as a sub heat exchanger (10A1) to (10A1).
The supercooling and heating are alternately repeated while passing through B2). That is, while the slurry-like iced substance is continuously produced, its adhesion to the tube wall is peeled off, and therefore the effect of the invention of claim 4 can be remarkably exhibited.

Further, in the invention of claim 6, as shown in each of the above-mentioned embodiments, the compressors (11), (2
1) and the like are connected to each other to form a refrigerating apparatus (air conditioner) having a refrigerant circuit (1), and a sub heat exchanger ((10) in the fourth embodiment or (10A1 in the fifth embodiment)). ) To (10B2)), the low-temperature refrigerant or the high-temperature refrigerant flows through the switching valve (the on-off valve (93) in the fourth embodiment or the three-way switching valve (94) in the fourth embodiment) at the refrigerant inlet end. Thus, it is possible to recool and heat the water and the like supercooled by the water heat exchanger (22) without separately providing a heat source for recooling and heating. Therefore, there is an advantage that the effects of the inventions of claims 4 and 5 can be exhibited while suppressing an increase in power consumption.

FIG. 14 shows a seventh embodiment according to the invention of claim 7. In this embodiment, the flow velocity increasing member (75) is provided at and around the location of the recooler (8) in the return conduit (51B).
As a result, a diaphragm portion (75A) is provided. In other words, on the surface of the recooler (8), ice accretion spreads to the surroundings due to the elimination of the supercooled state, but the heaters (9) arranged on both sides of the recooler (8) are along the pipe wall. Although the spread of ice accretion in the direction can be prevented, it cannot prevent the growth of ice particles toward the center of the pipe as shown in FIG. Therefore, coarse particles are formed, which causes the blockage of the conduit. Therefore, in this embodiment, the flow velocity of the flow is increased by the throttle portion (75A), the energy of the velocity head is increased, and the ice accretion can be crushed or separated from the pipe wall. It is considered that the increase in the flow velocity causes the elimination of the supercooled state, but this can be avoided by removing the speed range where the elimination of the supercooled state occurs.

FIG. 15 shows a modification of the seventh embodiment. In this modified example, as the flow velocity increasing member (75), a flow path changing plate (75B) is inserted in the upstream side of the recooler (8). This flow path changing plate (75B) is connected to the return conduit (5
The base end is fixed to the facing surface of the wall surface of 1B), is inclined toward the downstream side from the base end toward the recooler (8), and the tip is formed in the vicinity of the recooler (8). ing.

As a result, the flow velocity can be increased near the recooler (8). Therefore, the same effect as that of the seventh embodiment can be exhibited.

[0064]

As described above, according to the first aspect of the present invention, the water or the aqueous solution in the ice storage tank is circulated between the main heat exchanger and the main pipe through the forward conduit and the return conduit. A subcooling elimination unit for eliminating a supercooled state of water or the like supercooled in the main heat exchanger to generate slurry-like iced substances is provided in the return pipe downstream of the heat exchanger, and the subcooling elimination unit is provided. Since a freezing prevention unit that dissociates the adhesion of iced substances to the pipe wall is provided near the pipe wall, it is possible to effectively prevent freezing near the pipe wall due to the iced substances generated in the supercooling elimination unit. It is possible to improve efficiency.

According to the invention of claim 2, in the invention of claim 1, the main heat exchanger is connected to the refrigerant circuit of the refrigeration system, and the refrigerant inlet end of the antifreezing portion is connected to the liquid pipe of the refrigerant circuit. The refrigerant outlet end of the supercooling elimination portion is connected to the suction side of the compressor of the refrigerant circuit, and the refrigerant inlet end of the supercooling elimination portion and the refrigerant outlet end of the antifreezing portion are connected via the pressure reducing portion. Therefore, it is possible to further reduce the pressure of the refrigerant cooled by heat exchange with water or the like in the freeze prevention unit and use it as a cold heat source for eliminating supercooling. The heat can be effectively used.

According to the invention of claim 3, in the invention of claim 1 or 2, it is provided so as to extend from the supercooling elimination portion to the main heat exchanger to prevent the progress of freezing to the main heat exchanger. Since it also works, the above-mentioned claim 1 or 2
In the invention described above, the structure can be simplified.

According to the invention of claim 4, a sub heat exchanger that repeats a cycle for heating water and a cycle for cooling water is provided in the return pipe downstream of the main heat exchanger. It is possible to generate slurry-like iced matter in the exchanger and prevent freezing due to the adhesion of the produced iced matter to the tube wall, thus simplifying the configuration.

According to the invention of claim 5, in the invention of claim 4, since a plurality of sub heat exchangers are provided and the heating and cooling cycles are different from each other, water or the like passes through the return conduit. According to the invention of claim 4, it is possible to alternately heat and cool, thereby continuously producing a slurry-like iced substance and preventing freezing of the vicinity of the pipe wall due to the iced substance. The ice making capacity can be improved.

According to the invention of claim 6, in the invention of claim 4 or 5, the main heat exchanger is connected to the refrigerant circuit of the refrigeration system, and the auxiliary heat exchanger is connected to the refrigerant circuit via a switching valve. Since the discharge gas refrigerant and the liquid refrigerant are configured to flow alternately, it is possible to obtain the effect of the invention of claim 4 or 5 without providing a separate heat source, thus reducing the cost in each invention. Can be achieved.

[0070] According to the invention of claim 7,
6 In any one of the inventions, since the flow velocity increasing member is provided at the location of the supercooling elimination portion in the return conduit, the flow velocity is increased, and icing on the surface of the supercooling elimination portion can be removed. It is possible to prevent the blockage of the pipeline.

[Brief description of drawings]

FIG. 1A is a block diagram showing a basic configuration of the inventions of claims 1 to 3, and FIG. 1B is a block diagram showing a basic configuration of the inventions of claims 4 to 6.

FIG. 2 is a refrigerant piping system diagram showing the configuration of the air conditioning apparatus according to the first embodiment.

FIG. 3 is a side view showing, in a vertical cross-section, a part of the configuration of the return conduit from the water heat exchanger to the recooler, showing the first embodiment.

FIG. 4 is a vertical cross-sectional view showing structures of a recooler and a heater in a second embodiment.

FIG. 5 is a vertical sectional view showing a first modification of the second embodiment.

FIG. 6 is a vertical cross-sectional view showing a first modified example of the second embodiment and showing the structure in the vicinity of the conduit shown in FIG. 5;

FIG. 7 is a vertical sectional view showing a second modification of the second embodiment.

FIG. 8 is a side view showing a partial vertical cross-section of the configuration of the return conduit from the water heat exchanger to the recooler in the third embodiment.

FIG. 9 is a refrigerant piping system diagram of the air conditioning apparatus according to the fourth embodiment.

FIG. 10 is a characteristic diagram showing the time variation of the temperature of the refrigerant flowing through the sub heat exchanger according to the fourth embodiment.

FIG. 11 is a refrigerant piping system diagram showing the configuration of the air conditioning apparatus according to the fifth embodiment.

FIG. 12 is a longitudinal sectional view showing the structure of the sub heat exchanger according to the fifth embodiment.

FIG. 13 is a characteristic diagram showing a time change of the temperature of the refrigerant flowing through each sub heat exchanger according to the fifth embodiment.

FIG. 14 is a vertical cross-sectional view showing a throttle portion provided in a supercooling elimination portion according to a seventh embodiment.

FIG. 15 is a vertical sectional view showing a modified example of the seventh embodiment.

FIG. 16 is a vertical sectional view showing a conventional example in a seventh embodiment.

[Explanation of symbols]

 1 Refrigerant circuit 5 Ice storage tank 8 Recooler (supercooling elimination part) 9 Heater (freezing prevention part) 10 Sub heat exchanger 22 Water heat exchanger (main heat exchanger) 51A Forward line 51B Return line 75 Flow rate increasing member 75A Throttling part (flow rate increasing member) 75B Flow path changing plate (flow rate increasing member) 93 Open / close valve (switching valve) 94 Three-way switching valve F Pressure reducing part F1 Pressure reducing valve (pressure reducing part) F2 Pore (pressure reducing part) F3 Capillary tube (decompression section)

 ─────────────────────────────────────────────────── ─── Continuation of front page (72) Inventor Yuji Nakazawa 1304 Kanaoka-machi, Sakai-shi, Osaka Daikin Industries, Ltd. Sakai Works Kanaoka factory (56) References: Kaikaihei 2-34925 (JP, U)

Claims (7)

[Claims] 1. An ice storage tank (5) for storing a slurry of iced water or an aqueous solution, and a main heat exchanger (22) connected to a cooling device for supercooling the water or aqueous solution. A forward conduit (51A) and a return conduit (51B) for forcibly circulating water or an aqueous solution between the ice storage tank (5) and the main heat exchanger (22), and the main heat exchanger (22) A supercooling elimination section which is provided in the downstream return conduit (51B) and eliminates the supercooled state of the water or aqueous solution supercooled by the main heat exchanger (22) to form a slurry-like iced substance. (8) and a return conduit (51B) provided in the vicinity of the supercooling elimination section (8) so as to dissociate the adhesion of the iced substance generated in the supercooling elimination section (8) to the tube wall. An ice making device, comprising: an antifreezing part (9). 2. The cooling device is a refrigerating device having a refrigerant circuit (1) in which a compressor, an evaporator, a pressure reducing valve and a condenser are sequentially connected, and the supercooling elimination section (8) is the refrigerant circuit. The water or the aqueous solution is cooled by heat exchange with the refrigerant of (1), and the antifreezing section (9) heats the water or the aqueous solution by heat exchange with the refrigerant of the refrigerant circuit (1). These supercooling elimination section (8) and antifreezing section (9) have their refrigerant flow paths connected in series, and the refrigerant is introduced into the antifreezing section (9) from the downstream side of the condenser, and the supercooling elimination section ( 8)
From the freezing prevention section (9) and the supercooling elimination section (8) to the pressure reducing section (F).
The ice making device according to claim 1, wherein the ice making device is provided. 3. The antifreezing portion (9) is a supercooling elimination portion (8).
To the main heat exchanger (22), and prevents the progress of freezing to the main heat exchanger (22). 4. An ice storage tank (5) for storing a slurry of iced water or an aqueous solution, and a main heat exchanger (22) connected to a cooling device for supercooling the water or aqueous solution. A forward conduit (51A) and a return conduit (51B) for forcibly circulating water or an aqueous solution between the ice storage tank (5) and the main heat exchanger (22), and the main heat exchanger (22) A sub heat exchanger (10) that is provided in the downstream return pipe (51B) and that repeats a cycle of heating water or an aqueous solution supercooled by the main heat exchanger (22) and a cycle of cooling it. An ice making device characterized by being provided. 5. The ice making device according to claim 4, wherein a plurality of sub heat exchangers (10) are provided, and each has a different heating and cooling cycle. 6. The cooling device is a refrigerating device having a refrigerant circuit (1) in which a compressor, an evaporator, a pressure reducing valve and a condenser are sequentially connected, and the auxiliary heat exchanger (10) is the refrigerant circuit. Heat exchange between the refrigerant (1) and water or an aqueous solution is performed, and the refrigerant inlet end of the sub heat exchanger (10) is connected to the liquid pipe and the discharge pipe of the refrigerant circuit (1) via the switching valve. The ice making device according to claim 4 or 5, wherein the ice-making devices are connected so as to alternately communicate with each other, and the refrigerant outlet end of the auxiliary heat exchanger (10) is connected so as to communicate with the suction pipe of the refrigerant circuit (1). . 7. In order to remove ice formation on the surface of the subcooling elimination section (8) by increasing the flow velocity of water or aqueous solution in the subcooling elimination section (8) in the return conduit (51B). The ice-making device according to any one of claims 1 to 6, further comprising a flow velocity increasing member (75).