JP5800943B2 - Ice making equipment - Google Patents

Description

  The present invention maintains a high heat exchange efficiency of a heat exchange section for cooling a brine in an ice making apparatus that forms a circulation flow of brine in an ice making tank and immerses an ice making can filled with fresh water in the brine to produce ice blocks. In addition, the assembly of the heat exchange part is simplified.

  The ice making device is composed of an ice making tank filled with brine such as an aqueous calcium chloride solution. The ice making tank is provided with an ice making area and a heat exchange area, and brine is circulated with an agitator at a flow rate of about 1 m / sec. In the heat exchange zone, the brine is cooled to about −10 ° C. by a cooling device. In the ice making area, ice cans filled with fresh water are immersed in brine, and the fresh water in the ice cans is frozen for about 24 hours to produce ice cubes.

The cooling device includes a refrigeration device in which a refrigeration cycle constituent device including a compressor, a condenser, an expansion valve, and an evaporator is interposed in a refrigerant circuit, and the cooling coil constituting the evaporator is placed in a brine channel. It is installed in. A cooling fluid such as CO ₂ is supplied to the cooling coil to cool the brine flowing outside the coil while evaporating the cooling fluid.

  Conventionally, for example, a herringbone type cooling coil as shown in FIG. 12 is used as the cooling coil. Patent Document 1 discloses an ice making device using a herringbone type cooling coil. A herringbone type cooling coil 100 is a header arranged vertically by cutting a length steel pipe into 1/2 or 1/3 length and bending it to form a cooling pipe 102 as shown in FIG. It is welded to the tube 104. In the figure, a indicates the flow direction of brine.

JP-A-7-113562

The herringbone type cooling coil has the advantage of forming a complicated curve, forming a large heat transfer area with the brine, and increasing the heat exchange rate. However, a special bending process is required to manufacture the cooling pipe 102. Yes, the machining process becomes complicated.
Further, as shown in FIG. 13, since the bent cooling pipe 102 is obliquely inserted into the header pipe 104 and welded, the weld end of the cooling pipe 102 becomes elliptical. It is necessary to make a hole 106 having an elliptical complicated shape in the header pipe 104 in accordance with this elliptical shape. Therefore, the processing of the hole 106 becomes troublesome, and the welding line becomes a long and three-dimensional complicated curve, which makes the welding work troublesome. As a result, the quality of the welding may deteriorate, and refrigerant leakage may occur from the welding location due to pinholes or the like.

Therefore, in view of the problems of the prior art, the present invention cascades a NH ₃ circulation channel and a CO ₂ circulation channel using a secondary refrigerant system, for example, NH ₃ as a primary refrigerant and CO ₂ as a secondary refrigerant. An object of the present invention is to realize a heat exchanging unit capable of eliminating troublesome processing, eliminating refrigerant leakage, and maintaining a high heat exchange rate in a CO ₂ secondary refrigerant type ice making device connected by a capacitor.

In order to achieve this object, the ice making device of the present invention connects a primary refrigerant circulation channel and a secondary refrigerant circulation channel with a cascade condenser, and the primary refrigerant condenses the secondary refrigerant with the cascade condenser. Liquefied and stored in the receiver, and the stored secondary refrigerant liquid is supplied to the heat exchange area via the secondary refrigerant circulation flow path by a liquid pump, and exchanges heat with brine in the heat exchange area. A refrigeration cycle configured to evaporate and return from the secondary refrigerant circulation flow path to the receiver, and immerse an ice can filled with fresh water in the heat exchange zone and filled with fresh water. In an ice making apparatus comprising an ice making tank for making ice, and a heat exchanging unit that cools the brine by exchanging heat between the refrigerant of the refrigeration apparatus and the brine provided in the circulation path of the brine,
A plurality of linear refrigerant tubes arranged in the brine flow direction and inclined in the vertical direction with respect to a horizontal plane; and the plurality of linear refrigerant tubes spaced apart in the tube axis direction. Consisting of connected header tubes,
The gist of the present invention is that both ends of the linear refrigerant pipe are connected at an intersecting angle perpendicular to the header pipe, and a refrigerant supply pipe and a refrigerant return pipe are connected to the header pipe .
In addition to the gist of the first invention, the first invention connects the refrigerant supply pipe to the lower part of the header pipe, connects the refrigerant gas return pipe to the upper part of the header pipe, and connects the plurality of header pipes to the plurality of header pipes. The straight refrigerant pipe is alternately inclined in the opposite direction with respect to the horizontal plane for each header pipe .
Further, in the second invention, in addition to the gist, the heat transfer tube group including the refrigerant supply pipe and the refrigerant return pipe is tilted upward symmetrically with respect to the vertical center line e located at the brine flow direction center. It is arranged .

  In the present invention, a standard steel pipe can be used as it is for the straight refrigerant pipe without bending, and the machining process can be simplified. In addition, since the straight refrigerant pipe and the header pipe are connected at a right-angled crossing angle, the hole drilled in the header pipe for welding may be a simple circular hole, and the drilling process becomes easy. The shape of the connecting end of the straight refrigerant pipe is also a simple circle, which makes it easy to process. Further, the welding length is shortened, and the joining work is facilitated.

  Moreover, since the linear refrigerant pipe is inclined with respect to the horizontal plane, the axial length immersed in the brine can be increased and the heat transfer area can be increased as compared with the case where there is no inclination. Therefore, the heat transfer amount between the refrigerant and the brine can be increased. From the viewpoint of increasing the heat transfer area with the brine without increasing the depth of the ice making tank, the inclination angle is preferably 2 to 4 degrees.

Further, since the straight refrigerant pipes are arranged in the brine flow direction and spaced apart from each other, the flow resistance with respect to the brine can be reduced, and the power required for the flow of the brine can be reduced.
If the refrigerant supply pipe is connected to the lower part of the header pipe and the refrigerant gas return pipe is connected to the upper part of the header pipe, the refrigerant vaporized by heat exchange with the brine smoothly returns to the refrigeration cycle through the refrigerant return pipe. be able to.

In the present invention, the plurality of header pipes are arranged in parallel at intervals in the transverse direction of the brine flow path, and a plurality of linear refrigerant pipes are connected to each of the header pipes, and end portions of the plurality of header pipes Is connected to a second header pipe arranged in the transverse direction of the brine flow path, and the refrigerant supply pipe and the refrigerant return pipe are connected to the second header pipe.
Thereby, since the linear refrigerant pipe can be arranged in the vertical direction and the transverse direction of the brine flow path, a large number of linear refrigerant pipes can be arranged in the brine flow path. Therefore, the amount of heat exchange between the refrigerant and the brine can be increased. In addition, since the header pipes are arranged in parallel at intervals in the transverse direction of the brine flow path, the brine flow resistance by the header pipes can be minimized.

In addition to the above-described configuration, in this case, a plurality of linear refrigerant tubes respectively connected to the plurality of header tubes may be alternately inclined in the opposite direction with respect to the horizontal plane for each header tube.
As a result, the brine flow formed along the outer surface of the linear refrigerant pipe collides with the adjacent linear refrigerant pipe to generate a stirring flow, so that the heat exchange amount between the refrigerant and the brine is increased by the stirring flow. As a result, the cooling effect of brine can be improved.

Further, in addition to the above configuration, a plurality of linear refrigerant tubes are arranged at equal intervals in the vertical direction, and the linear refrigerant tubes are arranged in a line at the same height in the transverse direction of the brine flow path. A support frame may be inserted between the tubes in the transverse direction of the brine flow path so that the support frame supports linear refrigerant tubes adjacent above and below the support frame.
As a result, the straight refrigerant pipe can be fixed in the brine flow path, and only the support frame is required, so that the brine flow resistance can be minimized.

The refrigeration system, secondary coolant system, the NH ₃ as the primary refrigerant example, using CO ₂ as a secondary refrigerant, CO ₂ two made a NH ₃ circulation passage and CO ₂ circulation flow path connected in cascade condenser It is effective for secondary refrigerant type refrigeration equipment.

  According to the ice making device of the present invention, an ice making tank in which an ice making can filled with fresh water formed with a brine circulation flow is immersed in the brine, and a compressor, a condenser, an expansion valve and a cascade are provided in the refrigerant circulation path. A secondary refrigerant type refrigeration apparatus including a condenser, and a heat exchanging unit provided in a circulation flow path of the brine to exchange heat between the refrigerant of the refrigeration apparatus and the brine to cool the brine. In the ice making device, the heat exchange section includes a plurality of linear refrigerant tubes arranged in a vertical direction with respect to a horizontal plane along the flow direction of the brine, and the plurality of linear refrigerant tubes in the tube axis direction. A header pipe connected at an interval, and both ends of the linear refrigerant pipe are connected at an intersection angle perpendicular to the header pipe, and a refrigerant supply pipe and a refrigerant return pipe are connected to the header pipe. Easy to process It is possible to improve the cooling effect of the brine increases the heat exchange rate between the refrigerant and the brine can be realized heat exchange unit which can reduce the power required to flow brine suppressing the flow resistance against brine.

It is a top view which shows one Embodiment of the ice making apparatus of this invention. It is a top view of the heat exchange area 18a of the said ice making apparatus. FIG. 3 is a front sectional view taken along line BB in FIG. 2. FIG. 4 is a side sectional view taken along the line CC in FIG. 3. FIG. 4 is a side sectional view taken along line DD in FIG. 3. FIG. 4 is a side view sectional view taken along line EE in FIG. 3. FIG. 5 is a side sectional view taken along line FF in FIG. 3. FIG. 4 is a side sectional view taken along line GG in FIG. 3. FIG. 4 is a side sectional view taken along line HH in FIG. 3. It is a perspective view which shows the connection part of the heat exchanger tube of the said ice making apparatus. It is a diagram which shows the heat transfer rate of the heat exchanger tube of the said ice making apparatus. (A) is a front view of a herringbone type heat exchanger, and (B) is an I direction arrow view in (A). It is a perspective view which shows the connection part of the herringbone type heat exchanger shown in FIG.

  Hereinafter, the present invention will be described in detail with reference to embodiments shown in the drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the component parts described in this embodiment are not intended to limit the scope of the present invention to that unless otherwise specified.

  One embodiment of the ice making device of the present invention will be described with reference to FIGS. FIG. 1 is an overall configuration diagram of an ice making device 10 according to the present embodiment. In FIG. 1, the inside of the ice making tank 12 is divided into ice making areas 16 a and 16 b disposed on both sides by a partition wall 14 and a heat exchange area 18 disposed between the ice making areas 16 a and 16 b. The inside of the ice making tank 12 is filled with brine made of an aqueous calcium chloride solution, and a circulating flow is formed by the agitator 20 to circulate between the ice making areas 16a and 16b and the heat exchange area 18 in the direction of arrow a at a flow rate of about 1 m / s. Yes.

The brine is cooled to about −10 ° C. by the refrigerant in the heat exchange area 18. In the ice making units 16a and 16b, a large number of ice making cans 22 filled with fresh water are immersed in brine, and the fresh water is cooled by the brine, and transparent ice cubes are produced over a period of about 24 hours.
The ice making can 22 on which the ice cubes have been formed is transferred by a transfer device and transferred to an ice bath (not shown), and the ice making can 22 is heated in the ice melting bath to melt the outer surface of the ice cubes. Thereafter, the ice making crane is transported to a deicing machine (not shown) where the ice making can 22 is tilted to slide the ice cubes out of the ice making can 22. In FIG. 1, only a part of the ice making can 22 immersed in the ice making regions 16a and 16b is shown, and the others are omitted.

Next, the configuration of the cooling device that cools the brine in the heat exchange area 18 will be described. In FIG. 2, the refrigeration apparatus 24 constitutes an NH ₃ refrigeration cycle in which an NH ₃ circulation channel 26 and a circulation channel 28 using CO ₂ as a secondary refrigerant are connected by a cascade capacitor 30.
In the NH ₃ circulation flow path 26, a compressor 32, a condenser 34, an expansion valve 36, and a cascade condenser 30 are interposed. The NH ₃ refrigerant used as the primary refrigerant condenses and vaporizes the CO ₂ refrigerant used as the secondary refrigerant in the cascade condenser 30. The CO ₂ refrigerant is cooled and liquefied and dropped into the liquid receiver 38.

As for the CO ₂ refrigerant, the gas phase part in the liquid receiver 38 is sent to the cascade condenser 30, and the liquid phase part liquefied by the cascade condenser 30 returns to the liquid receiver 38. The CO ₂ refrigerant liquid stored in the liquid receiver 38 is supplied to the heat exchange area 18 via the circulation flow path 40a by the liquid pump 42, exchanges heat with brine in the heat exchange area 18, and is vaporized to be circulated in the circulation flow path 40b. To the receiver 38.

Next, the structure of the heat exchange area 18 is demonstrated based on FIGS. The heat exchange area 18 is formed with an elongated brine flow path, and two heat exchange portions 18a and 18b are arranged in order from the upstream side along the flow direction a of the brine. Of these, the heat exchange section 18a will be described as an example.
2 to 9, a CO ₂ liquid pipe 44 and a CO ₂ gas pipe 46 are parallel to each other along the longitudinal direction of the heat exchange zone 18 and below the brine liquid surface level L in the vicinity of both ends in the transverse direction of the brine flow path. It is arranged. Connected to the CO ₂ liquid pipe 44 are connecting pipes 48 and 50 that are suspended downward at both ends of the heat exchange section 18a in the brine flow direction.

The communication pipe 48 is connected to a liquid header pipe 52 disposed in the transverse direction near the upstream bottom of the heat exchange section 18a, and the communication pipe 50 is disposed in the transverse direction near the bottom on the downstream side of the heat exchange section 18a. Connected to the liquid header pipe 54.
Seven liquid header branch pipes 56a to 56g are connected to the liquid header pipe 52 in the vertical direction at equal intervals. Similarly, seven liquid header branch pipes 58a to 58g are also connected to the liquid header pipe 54 at equal intervals. Connected vertically.

On the other hand, the CO ₂ gas pipe 46 is connected to gas header pipes 60 and 62 arranged horizontally in the transverse direction at both ends of the heat exchange section 18a. Seven gas header branch pipes 64a to 64g are connected to the gas header pipe 60 in the vertical direction at equal intervals, and the gas header pipe 62 is similarly connected to seven gas header branch pipes 66a to 66g at equal intervals. Connected vertically.

  As shown in FIG. 4, the gas header branch pipes 64a to 64g are arranged such that the gas header branch pipes are positioned between the liquid header branch pipes in a direction transverse to the liquid header branch pipes 56a to 56g. Yes. As shown in FIG. 9, the gas header branch pipes 66a to 66g are also arranged so that the gas header branch pipes are located between the liquid header branch pipes in the transverse direction with respect to the liquid header branch pipes 58a to 58g. Has been.

Between the liquid header branch pipes 56a to 56g and the gas header branch pipes 66a to 66g, nine heat transfer pipe groups 68 are installed for each header branch pipe. The individual heat transfer tubes constituting the heat transfer tube group 68 are linear and are arranged at equal intervals so as to rise twice with respect to the horizontal plane (brine flow direction a).
In addition, nine heat transfer tube groups 70 are installed for each header branch pipe between the liquid header branch pipes 58a to 58g and the gas header branch pipes 60a to 60g. The individual heat transfer tubes constituting the heat transfer tube group 70 are linear and are arranged at equal intervals so as to descend twice with respect to the horizontal plane (brine flow direction a).

Due to the above-described arrangement relationship of the header branch pipes in the transverse direction, the heat transfer tube group 68 and the heat transfer tube group 70 are alternately arranged at equal intervals in the brine flow passage transverse direction.
Further, the liquid header branch pipes 56a to 56g and the gas header branch pipes 66a to 66g connected to both ends of the heat transfer pipe group 68 are connected so as to intersect the heat transfer pipe group 68 in a direction perpendicular to the heat transfer pipe group 68. The liquid header branch pipes 58 a to 58 g and the gas header branch pipes 64 a to 64 g connected to both ends of the heat pipe group 70 are connected so as to intersect with the heat transfer pipe group 68 in a perpendicular direction.

This connecting portion is shown in FIG. In FIG. 10, a circular hole 72 is formed in a direction perpendicular to the liquid header branch pipes 56 a to 56 g, 58 a to g, or the gas header branch pipes 64 a to 64 g, 66 a to 66 g, and the heat transfer pipe fitted into the circular hole 72. The tips of the heat transfer tubes constituting the group 68 or 70 have a cut surface 73 perpendicular to the tube axis. The tip is fitted into the circular hole 72 and welded.
The liquid header branch pipes 56a-g, 58a-g or the gas header branch pipes 64a-g, 66a-g are also 2 degrees with respect to the vertical direction by the amount of the heat transfer tube group 68 or 70 inclined by 2 degrees with respect to the horizontal direction. Just tilted.

In this configuration, the CO ₂ refrigerant liquid supplied from the circulation flow path 40 a to the heat exchange area 18 by the liquid pump 42 is supplied to the liquid header pipes 52 and 54 through the CO ₂ liquid pipe 44 and the communication pipes 48 and 50. The The CO ₂ refrigerant liquid flows from the liquid header pipe 52 or 54 to the heat transfer pipe group 68 or 70 via the liquid header branch pipes 56a to 56g or 58a to g. The CO ₂ refrigerant liquid exchanges heat with brine in the heat transfer tube group 68 or 70, and evaporates by obtaining latent heat of evaporation from the brine.

The CO ₂ refrigerant gas vaporized by the heat transfer tube group 68 or 70 flows from the gas header pipe 60 or 62 to the CO ₂ gas pipe 46 via the gas header branch pipes 64a to 66g or 66a to g, and is received via the circulation flow path 40b. Return to fluid container 38.
Note that the CO ₂ liquid pipe 44 and the CO ₂ gas pipe 46 extend to the heat exchanging portion 18b. The heat exchanging part 18b has the same configuration as the heat exchanging part 18a, and the heat exchanging part 18b also exchanges heat between the CO ₂ refrigerant and brine, and the vaporized CO ₂ refrigerant passes through the circulation flow path 40b to receive the liquid. Return to 38.

  As shown in FIG. 3, the heat transfer tube groups 68 and 70 are arranged symmetrically with respect to the vertical center line e located at the center of the brine flow direction. Then, the heat transfer tube groups 68 and 70 are arranged in a line at the same height in the brine flow path transverse direction at the center line e and the position g located on both sides of the center line e.

As shown in FIGS. 6 and 8, a support device 74 for supporting the heat transfer tube groups 68 and 70 is provided at the position of the center line e and the position of g. The support device 74 includes a column 76 standing on both sides in the transverse direction of the brine channel, and a linear horizontal frame 78 that is installed between the columns 76 in a horizontal direction between the columns 76 and arranged in a row. , And a steel material 80 having a U-shaped cross section laid between the upper end and the lower end of the column 76, and heat transfer tubes are fixed to the upper and lower surfaces of the horizontal frame 78. A steel material 80 installed on the upper end of the column 76 supports the CO ₂ liquid pipe 44 and the CO 2 gas pipe 46.

According to this embodiment, a regular steel pipe can be used as it is as a heat transfer tube constituting the heat transfer tube group 68 or 70 without requiring complicated bending, and the manufacturing process can be simplified.
Further, since the liquid header branch pipes 56a to 56g and 58a to g or the gas header branch pipes 64a to 64g and 66a to g connected to the heat transfer pipe group 68 or 70 are connected at right angles, Therefore, the hole to be drilled in the header branch pipe may be a simple circular hole, and the drilling process is facilitated, and the shape of the connection end of the heat transfer tube group is not complicated. Further, the welding length is shortened, and the joining work is facilitated.

In addition, since the heat transfer tube groups 68 and 70 are arranged so as to be inclined in the brine flow direction, the length of the heat transfer tube immersed in the brine can be increased and the heat transfer area can be increased as compared with the case where there is no inclination. Therefore, the heat transfer amount between the refrigerant and the brine can be increased.
In addition, since the heat transfer tube groups 68 and 70 are spaced apart from each other and arranged in the brine flow direction, the flow resistance of the brine can be reduced, and the power required for the flow of the brine can be reduced.
Further, with arranging the liquid header branch pipe 56a~g and 58a~g the bottom of the brine flow path, since the arrangement of the gas header branch pipe 64a~g and 66a~g the top of the brine flow path, CO ₂ Due to the gravity acting on the refrigerant liquid and the rising force of the CO ₂ refrigerant gas, the supply of the CO ₂ refrigerant liquid to the heat transfer tube groups 68 and 70 and the circulation flow path of the CO ₂ refrigerant gas vaporized by the heat transfer tube groups 68 and 70 The return to 40b can be performed smoothly.

  Also, a plurality of liquid header branch pipes 56a-g, 58a-g or a plurality of gas header branch pipes 64a-g, 66a-g are arranged in parallel at intervals in the transverse direction of the brine flow path. Since the pipe is connected to the liquid header pipes 52, 54 or the gas header pipes 60, 62 arranged in the transverse direction of the brine flow path, a large number of heat transfer tube groups 68, 70 can be regularly arranged in the brine flow path, The amount of heat exchange between the refrigerant and the brine can be increased, and the brine flow resistance due to the header pipe and the header branch pipe can be minimized.

Further, since the individual heat transfer tubes constituting the heat transfer tube groups 68 and 70 are alternately inclined in the reverse direction in the brine flow path crossing direction, the brine flows directed along the outer surface of each heat transfer tube are adjacent to each other. A collision flow that collides with the heat transfer tube can be generated. Therefore, the amount of heat exchange between the CO ₂ refrigerant and the brine can be increased, and the collision flow can stir the brine, so that the heat exchange efficiency can be further improved.

  Further, since the heat transfer tube groups 68 and 70 are inserted between the heat transfer tubes at positions aligned in the vertical direction, a support device 74 including a lateral frame 78 for fixing and supporting each heat transfer tube is provided. 70 can be simplified and the brine flow resistance by the support device 74 can be minimized.

FIG. 11 is an experiment showing the external heat transfer coefficient of the heat transfer tube group 68 or 70 when the heat exchange area 18 of the present embodiment is provided (A) and when the heat transfer tube is not inclined as a comparative example (B) It is a result.
From the figure, it can be seen that the heat transfer coefficient outside the heat transfer tube of this embodiment is improved.

As the refrigeration apparatus 24, a direct expansion type refrigeration apparatus that vaporizes the primary refrigerant by the heat transfer tube groups 68 and 70 without using a secondary refrigerant such as CO ₂ or a refrigerant circulation path downstream of the expansion valve 36 is used. A low pressure liquid receiver is interposed between the low pressure liquid receiver and the heat transfer tube groups 68 and 70, and the primary refrigerant liquid is circulated by a liquid pump, and the primary refrigerant liquid is vaporized to cool the brine. A liquid circulation type refrigeration apparatus may be used.

According to the present invention, the secondary refrigerant system, the NH ₃ as the primary refrigerant example, using CO ₂ as a secondary refrigerant, comprising a NH ₃ circulation passage and CO ₂ circulation flow path connected in cascade condenser CO ₂ An object of the present invention is to realize a heat exchanging unit that eliminates troublesome processing, eliminates refrigerant leakage, and maintains a high heat exchange rate in a secondary refrigerant type ice making device.
The manufacturing process of the heat exchange part of the ice making device can be simplified, and a heat exchange part that can maintain high heat exchange efficiency without refrigerant leakage can be realized.

10 ice making device 12 ice bath 16a, 16b ice zone 18 heat exchange zone 18a, 18b heat exchange section 20 agitator 22 ice can 24 refrigeration system 26 NH ₃ circulation passage 28,40a, 40b CO ₂ circulation flow path 30 cascade condenser 32 compress Machine 34 Condenser 36 Expansion valve 38 Liquid receiver 42 Liquid pump 44 CO ₂ liquid pipe 46 CO ₂ gas pipe 52, 54 Liquid header pipe 56a-g, 58a-g Liquid header branch pipe 60, 62 Gas header pipe 64a-g , 66a-g Gas header branch pipe 68, 70 Heat transfer tube group 74 Support device 78 Horizontal frame a Brine flow direction L Brine liquid level

Claims (3)

The primary refrigerant circulation flow path and the secondary refrigerant circulation flow path are connected by a cascade capacitor, and the primary refrigerant is condensed and liquefied by condensing the secondary refrigerant in the cascade condenser, and stored in the liquid receiver. The secondary refrigerant liquid is supplied to the heat exchange area by the liquid pump via the secondary refrigerant circulation flow path, exchanges heat with brine in the heat exchange area, vaporizes, and receives liquid from the secondary refrigerant circulation flow path. An ice making tank having a refrigeration cycle configured to return to the vessel, wherein a brine circulation flow is formed in the heat exchange area and a fresh water filled ice making can is immersed in the brine to make ice, and a brine circulation channel In an ice making device provided with a heat exchanging unit that cools the brine by exchanging heat between the refrigerant of the refrigeration apparatus and the brine,
A plurality of linear refrigerant tubes arranged in the brine flow direction and inclined in the vertical direction with respect to a horizontal plane; and the plurality of linear refrigerant tubes spaced apart in the tube axis direction. Consisting of connected header tubes,
Both ends of the linear refrigerant pipe are connected at a crossing angle perpendicular to the header pipe, and a refrigerant supply pipe and a refrigerant return pipe are connected to the header pipe.
The refrigerant supply pipe is connected to the lower part of the header pipe, the refrigerant gas return pipe is connected to the upper part of the header pipe, and a plurality of linear refrigerant pipes respectively connected to the plurality of header pipes are horizontal for each header pipe. An ice making device characterized by alternately tilting in the opposite direction . The primary refrigerant circulation flow path and the secondary refrigerant circulation flow path are connected by a cascade capacitor, and the primary refrigerant is condensed and liquefied by condensing the secondary refrigerant in the cascade condenser, and stored in the liquid receiver. The secondary refrigerant liquid is supplied to the heat exchange area by the liquid pump via the secondary refrigerant circulation flow path, exchanges heat with brine in the heat exchange area, vaporizes, and receives liquid from the secondary refrigerant circulation flow path. An ice making tank having a refrigeration cycle configured to return to the vessel, wherein a brine circulation flow is formed in the heat exchange area and a fresh water filled ice making can is immersed in the brine to make ice, and a brine circulation channel In an ice making device provided with a heat exchanging unit that cools the brine by exchanging heat between the refrigerant of the refrigeration apparatus and the brine,
A plurality of linear refrigerant tubes arranged in the brine flow direction and inclined in the vertical direction with respect to a horizontal plane; and the plurality of linear refrigerant tubes spaced apart in the tube axis direction. Consisting of connected header tubes,
Both ends of the linear refrigerant pipe are connected at a crossing angle perpendicular to the header pipe, and a refrigerant supply pipe and a refrigerant return pipe are connected to the header pipe.
The ice making device, wherein the heat transfer tube group including the refrigerant supply pipe and the refrigerant return pipe is disposed so as to be symmetrically inclined upward with respect to a vertical center line e located in the brine flow direction center . A plurality of front header tubes are arranged in parallel at intervals in the transverse direction of the brine flow path, and a plurality of linear refrigerant tubes are connected to each of the header tubes,
The ends of the plurality of header pipes are connected to a second header pipe disposed in the transverse direction of the brine flow path, and the refrigerant supply pipe and the refrigerant return pipe are connected to the second header pipe. The ice making device according to claim 1.

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