JP2021041977A - Beverage product production system - Google Patents

Abstract

To provide a beverage product production system capable of improving energy efficiency.SOLUTION: A beverage product production facility 1 is a facility 1 for producing a beverage product from raw water, and comprises: a high temperature side cooling part 10 for cooling raw water; a low temperature side cooling part 60 for cooling raw water cooled by the high temperature side cooling part 10; a deaerator 41 for dissolving a carbon dioxide gas to the raw water cooled by the low temperature side cooling part 60; and a deaerator 41 for deairing the raw water. The low temperature side cooling part 60 cools the raw water supplied to the deaerator 41.SELECTED DRAWING: Figure 4

Description

The present disclosure relates to a beverage product manufacturing system.

When manufacturing a beverage product containing carbon dioxide gas in a facility for manufacturing a beverage product, it is necessary to cool the raw water that is the source of the beverage product to a temperature at which carbon dioxide gas can be dissolved. Therefore, in a facility for manufacturing a beverage product containing carbon dioxide gas, a refrigerator is used to generate a refrigerant for cooling the raw water, and the raw water is cooled by this refrigerant. Further, in a facility for manufacturing a beverage product containing carbon dioxide gas, raw water in which carbon dioxide gas is dissolved is filled in a container in a low temperature state, so that the container itself is also cooled to a low temperature. Therefore, if the container is packed in a packing container such as corrugated cardboard as it is, the packing container may be damaged by dew condensation generated on the outer surface of the container. Therefore, in the equipment for manufacturing beverage products, the container filled with the product liquid is heated to about the atmospheric temperature by steam or the like.

Patent Document 1 describes a carbonate-containing beverage from a cooling step, a carbonation step of press-fitting carbon dioxide gas into cooling raw water, a bottling (or canning) step, a heating step after bottling or canning, and a packaging step. The carbonated beverage manufacturing plant to be manufactured is disclosed. Patent Document 1 includes a cooler that introduces heated drainage from the heating step to obtain cold brine, and the cooling step is performed by the cold brine obtained by this cooler.

Japanese Unexamined Patent Publication No. 11-13195

In the apparatus of Patent Document 1, the raw water is cooled (cooling step) by a cold brine having a low temperature (-1 ° C. to 1 ° C.) cooled by one refrigerator. In the cooling step, the temperature of the raw water may be significantly lowered (25 ° C to 5 ° C in the example of Patent Document 1). In such a case, if the raw water is cooled by the brine cooled by one refrigerator, the compression ratio of the compressor of the refrigerator increases, and the power of the compressor also increases accordingly. Therefore, there is a possibility that energy consumption will increase.

The present disclosure has been made in view of such circumstances, and an object of the present disclosure is to provide a beverage product manufacturing system capable of improving energy efficiency.

In order to solve the above problems, the beverage product manufacturing system of the present disclosure employs the following means.
The beverage product manufacturing system according to one aspect of the present disclosure is a beverage product manufacturing system that manufactures a beverage product from raw water, and cools a first cooling unit that cools the raw water and a raw water cooled by the first cooling unit. A second cooling unit is provided, and a first carbon dioxide gas dissolving unit that dissolves carbon dioxide gas in the raw water cooled by the second cooling unit is provided.

According to the present disclosure, the energy efficiency of the entire beverage product manufacturing system can be improved.

It is a figure which shows the process of manufacturing the beverage product containing carbon dioxide gas in the beverage product manufacturing facility which concerns on one Embodiment of this disclosure. It is a block diagram which shows the whole of the beverage product manufacturing equipment which concerns on one Embodiment of this disclosure. It is a block diagram which shows the high temperature side cooling part of the beverage product manufacturing facility of FIG. It is a block diagram which shows the main part of the beverage product manufacturing facility of FIG. It is a block diagram which shows the main part of the beverage product manufacturing facility of FIG. It is a block diagram which shows the main part of the beverage product manufacturing facility of FIG. It is a block diagram which shows the control device applied to the beverage product manufacturing equipment of FIG. It is a block diagram which shows the brine control part applied to the beverage product manufacturing equipment of FIG. It is a block diagram which shows the hot water control part applied to the beverage product manufacturing facility of FIG. It is a block diagram which shows the cold water control part applied to the beverage product manufacturing facility of FIG. It is a graph which shows the relationship between a hot water temperature and a low-stage refrigerator load factor. It is a graph which shows the relationship between the set temperature of the 1st temperature sensor, and the elapsed time after the start-up of a compressor. It is a graph which shows the relationship between the 2nd temperature sensor set temperature, and the elapsed time after the start-up of a compressor. It is a flowchart which shows the brine refrigerator operation process performed by the control device applied to the beverage product manufacturing equipment of FIG. FIG. 5 is a flowchart showing an operation process of a hot water tank and a heating unit performed by a control device applied to the beverage product manufacturing equipment of FIG. It is a flowchart which shows the operation process of the refrigerator system performed by the control device applied to the beverage product manufacturing equipment of FIG. It is a flowchart which shows the operation process of the refrigerator system performed by the control device applied to the beverage product manufacturing equipment of FIG. It is a flowchart which shows the operation process of the refrigerator system performed by the control device applied to the beverage product manufacturing equipment of FIG. It is a flowchart which shows the operation process of the refrigerator system performed by the control device applied to the beverage product manufacturing equipment of FIG. It is a graph which shows the relationship between the total load of a chilled water chiller and the number of operating chilled water chillers.

Hereinafter, an embodiment of the beverage product manufacturing system according to the present disclosure will be described with reference to the drawings.

The beverage product manufacturing facility (beverage product manufacturing system) 1 according to the present embodiment is capable of producing a beverage product containing carbon dioxide gas. The beverage product manufacturing facility 1 manufactures a beverage product containing carbon dioxide gas by the following steps.
As shown in FIG. 1, first, the raw water used as a raw material for a beverage product is cooled in the first cooling step. Next, the raw water cooled in the degassing step is degassed. Next, in the blending step, syrup or the like is blended with the degassed raw water. Next, in the second cooling step, the raw water containing the syrup or the like is cooled. Next, in the carbon dioxide injection step, carbon dioxide gas is injected into raw water containing cooled syrup or the like to generate a product liquid. Next, in the filling step, the product liquid is filled in a container such as a bottle. Next, in the heating step, the product liquid (hereinafter, referred to as “beverage product”) filled in the container is heated. Next, in the boxing process, the heated beverage product is packed in a packing container such as corrugated cardboard. Then, in the shipping process, the packaged beverage product is shipped.

The beverage product manufacturing facility 1 includes two lines for producing a beverage product containing carbon dioxide gas. In the following description, the two lines will be referred to as a first line and a second line. Further, the beverage product manufacturing facility 1 includes lines other than the first line and the second line. Examples of other lines include aseptic filling lines for extracting, blending, and liquid-treating raw materials.

The first line and the second line are mostly independent parallel lines, but share some devices. Specifically, the first line and the second line are a refrigerator (high-stage refrigerator 11 and low-stage refrigerator 12) provided in the high-temperature side cooling unit 10 described later, a cold water tank 13, and a low-temperature side cooling unit 60. The brine refrigerator 61, the brine tank 62, and the hot water tank 81 of the heating unit 80 are shared. Since the independent structures of the first line and the second line are substantially the same, the description of the first line will be mainly described below, and the description of the second line will be omitted as appropriate.

As shown in FIG. 2, the first line of the beverage product manufacturing facility 1 includes a high-temperature side cooling unit 10 that cools raw water in the first cooling step (P1), a degassing step (P2), a blending step (P3), and A DBS device 40 that performs a carbon dioxide injection step (P5), a low-temperature side cooling unit 60 that cools raw water in a second cooling step (P4), and a filling machine that fills a container with a product liquid in a filling step (P6) (not shown). ), A heating unit 80 that heats the beverage product in the heating step (P7), and a boxing machine (not shown) that packs the beverage product in the packing container in the boxing step (P8). Further, the beverage product manufacturing facility 1 is provided with a raw water tank 2 for storing raw water (see FIG. 4). The raw water tank 2 stores raw water that has been subjected to a predetermined treatment. The temperature of the raw water stored in the raw water tank 2 is substantially the same as the temperature of the atmosphere. The beverage product packed in the packing container is shipped in the shipping process (P9).

The high temperature side cooling unit 10 cools the raw water sent from the raw water tank 2 with cold water. The raw water cooled by the high temperature side cooling unit 10 is sent to the DBS device 40 via a pipe (see FIG. 3).
As shown in FIG. 2, the high-temperature side cooling unit 10 includes two high-stage refrigerators 11 that generate cold water, two low-stage refrigerators 12 that generate cold water, a high-stage refrigerator 11 and a low-stage refrigerator. It has a chilled water tank 13 for storing the chilled water generated by the chiller 12, and a high-temperature side heat exchanger 14 for cooling the raw water with the chilled water from the chilled water tank 13. Since the two high-stage refrigerators 11 are arranged in parallel and have substantially the same functions, they will be collectively referred to as the high-stage refrigerator 11 in the following description. Further, in the drawings other than FIG. 2, the two high-stage refrigerators 11 are shown together. Further, the two low-stage refrigerators 12 will also be collectively described as the low-stage refrigerator 12. Further, in the drawings other than FIG. 2, the two low-stage refrigerators 12 are shown together.

The high-stage refrigerator 11 and the low-stage refrigerator 12 are turbo-type refrigerators that can handle ultra-low loads that continue operation without stopping even when the load factor is 30% or less. Specifically, it is a refrigerator that can be operated without stopping even when the load factor is around 0%. Further, the high-stage refrigerator 11 and the low-stage refrigerator 12 each have a compressor, a condenser, an expansion valve and an evaporator (all not shown), and the refrigerant circulates in the circulation pipe connecting each device. doing. In the high-stage refrigerator 11 and the low-stage refrigerator 12, the electric motor that drives the compressor is controlled by an inverter, and the rotation speed of the compressor can be controlled.
The high-stage refrigerator 11 and the low-stage refrigerator 12 cool the cold water by exchanging heat between the refrigerant and the cold water with an evaporator. The cold water cooled by the evaporator is discharged from the high-stage refrigerator 11 and the low-stage refrigerator 12, and is guided to the cold water tank 13 as shown in FIGS. 2 and 3. The high-stage refrigerator 11 and the low-stage refrigerator 12 cool the refrigerant and heat the water by exchanging heat between the refrigerant and water in the condenser. The water heated by the condenser of the high-stage refrigerator 11 (hereinafter, the water heated by each refrigerator is referred to as "warm water") is sent to the first cooling tower 51 to be cooled. The hot water cooled by the first cooling tower 51 is returned to the high-stage refrigerator 11. Further, the hot water heated by the condenser of the low-stage refrigerator 12 is returned to the low-stage refrigerator 12 via the heating unit 80 and the second cooling tower 52. Details of the heating unit 80 and the second cooling tower 52 will be described later.

As shown in FIG. 3, the chilled water tank 13 stores the chilled water supplied from the high-stage chiller 11 and the low-stage chiller 12, and the stored chilled water is provided in the first line and the second line. It is supplied to the high temperature side heat exchanger 214. The cold water tank 13 has a low temperature tank 15 for storing low temperature cold water, a medium temperature tank 16 for storing medium temperature cold water, and a high temperature tank 17 for storing high temperature cold water. The low temperature tank 15 and the medium temperature tank 16 are separated by a first cold water partition wall 18. Further, the medium temperature tank 16 and the high temperature tank 17 are separated by a second cold water partition wall 19. The first cold water partition wall 18 is formed with a first weir portion 18a that connects the low temperature tank 15 and the medium temperature tank 16. The first weir portion 18a is a through hole penetrating the first chilled water partition wall 18, and is not provided with a valve or the like. The first weir portion 18a is formed on the upper portion of the first chilled water partition wall 18. The second cold water partition wall 19 is formed with a second weir portion 19a that connects the medium temperature tank 16 and the high temperature tank 17. The second weir portion 19a is a through hole penetrating the second chilled water partition wall 19, and is not provided with a valve or the like. The second weir portion 19a is formed on the upper portion of the second chilled water partition wall 19. The flow path area of each weir is such that even if cold water continues to be supplied from the refrigerator in a state where cold water is not discharged from each tank, cold water is moved from each tank to the adjacent tank via the weir. It is said that the area does not overflow with cold water. Further, the medium temperature tank 16 is provided with a medium temperature tank temperature sensor 16a for measuring the temperature of the cold water stored in the medium temperature tank 16.

Next, the connection between the high-stage refrigerator 11 and the low-stage refrigerator 12 and the cold water tank 13 will be described with reference to FIGS. 3 to 5. Note that, in FIGS. 4 and 5, for the sake of illustration, the low-stage refrigerator 12 and the high-stage refrigerator 11 are shown together, and a part of the piping connecting the refrigerator and the cold water tank 13 is omitted. Shown.
As shown in FIG. 3, the high-stage refrigerator 11 and the high-temperature tank 17 are connected by a high-temperature tank discharge pipe 20. The high temperature tank discharge pipe 20 guides the cold water discharged from the high temperature tank 17 to the high-stage refrigerator 11. Further, the first medium temperature tank discharge pipe 21 is connected to the intermediate position between the medium temperature tank 16 and the high temperature tank discharge pipe 20. The cold water discharged from the medium-temperature tank 16 joins the high-temperature tank discharge pipe 20 after flowing through the first medium-temperature tank discharge pipe 21, and is guided to the high-stage refrigerator 11 via the high-temperature tank discharge pipe 20. Further, the high temperature tank discharge pipe 20 is provided with a high temperature tank discharge pipe valve 20a on the upstream side (high temperature tank 17 side) of the confluence with the first medium temperature tank discharge pipe 21. Further, on the downstream side (high-stage refrigerator 11 side) from the confluence with the first medium-temperature tank discharge pipe 21, a first temperature sensor 20b and a high-stage pump 20c for measuring the temperature of the cold water flowing inside are located. It is provided. The first temperature sensor 20b is provided on the upstream side of the high-stage pump 20c. The first medium temperature tank discharge pipe 21 is provided with a first medium temperature tank discharge pipe valve 21a. By adjusting the opening degree of the high temperature tank discharge pipe valve 20a and the first medium temperature tank discharge pipe valve 21a, the flow rate of the cold water flowing through the high temperature tank discharge pipe 20 and the first medium temperature tank discharge pipe 21 can be adjusted. It is a valve. Further, a medium temperature tank supply pipe 22 is connected to the high stage refrigerator 11 and the medium temperature tank 16. The medium-temperature tank supply pipe 22 is cooled by the high-stage refrigerator 11 and guides the cold water discharged from the high-stage refrigerator 11 to the medium-temperature tank 16.

The low-stage refrigerator 12 and the medium-temperature tank 16 are connected by a second medium-temperature tank discharge pipe 23. The second medium-temperature tank discharge pipe 23 guides the cold water discharged from the medium-temperature tank 16 to the low-stage refrigerator 12. Further, the low temperature tank discharge pipe 24 is connected to the intermediate position between the low temperature tank 15 and the second medium temperature tank discharge pipe 23. The cold water discharged from the low-temperature tank 15 joins the second medium-temperature tank discharge pipe 23 after flowing through the low-temperature tank discharge pipe 24, and is guided to the low-stage refrigerator 12 via the second medium-temperature tank discharge pipe 23. Further, the second medium-temperature tank discharge pipe 23 is provided with a second medium-temperature tank discharge pipe valve 23a on the upstream side (medium-temperature tank 16 side) of the confluence with the low-temperature tank discharge pipe 24. Further, a second temperature sensor 23b and a low-stage pump 23c for measuring the temperature of the cold water flowing inside are provided on the downstream side (low-stage refrigerator 12 side) of the confluence with the low-temperature tank discharge pipe 24. ing. The second temperature sensor 23b is provided on the upstream side of the low-stage pump 23c. The low temperature tank discharge pipe 24 is provided with a low temperature tank discharge pipe valve 24a. The second medium temperature tank discharge pipe valve 23a and the low temperature tank discharge pipe valve 24a can adjust the flow rate of the cold water flowing through the second medium temperature tank discharge pipe 23 and the low temperature tank discharge pipe 24 by adjusting the opening degree. It is a valve. Further, the low temperature tank supply pipe 25 is connected to the low stage refrigerator 12 and the low temperature tank 15. The low-temperature tank supply pipe 25 is cooled by the low-stage refrigerator 12 and guides the cold water discharged from the low-stage refrigerator 12 to the low-temperature tank 15.

As shown in FIG. 4, the high-temperature side heat exchanger 14 is a plate heat exchanger that exchanges heat between the raw water led from the raw water tank 2 via the first raw water pipe 26 and the cold water guided from the cold water tank 13. Is. The high temperature side heat exchanger 14 cools the raw water and heats the cold water by exchanging heat between the raw water and the cold water. The raw water cooled by the high temperature side heat exchanger 14 is guided to the dearator 41 described later via the second raw water pipe 27. The second raw water pipe 27 is provided with a raw water temperature sensor 27a that measures the temperature of the raw water flowing inside.

Next, the connection between the cold water tank 13 and the high temperature side heat exchanger 14 will be described with reference to FIGS. 3 to 5. In FIG. 4, for the sake of illustration, the first line is shown and the second line is omitted. Further, in FIG. 5, for the sake of illustration, the first chilled water bypass pipe 33 and the second chilled water bypass pipe 34, which will be described later, are not shown.
As shown in FIG. 3, the low temperature tank 15 and the high temperature side heat exchanger 14 provided in the first line are connected by a first chilled water supply pipe 28. The first chilled water supply pipe 28 guides the chilled water discharged from the low temperature tank 15 to the high temperature side heat exchanger 14 of the first line. The first chilled water supply pipe 28 is provided with a first chilled water supply pump 28a, a first chilled water supply pipe opening / closing valve 28b, and a first chilled water supply pipe adjusting valve 28c in order from the upstream side. Further, the low temperature tank 15 and the high temperature side heat exchanger 214 provided in the second line are connected by a second chilled water supply pipe 29. The second chilled water supply pipe 29 guides the chilled water discharged from the low temperature tank 15 to the high temperature side heat exchanger 214 of the second line. The second chilled water supply pipe 29 is provided with a second chilled water supply pump 29a, a second chilled water supply pipe opening / closing valve 29b, and a second chilled water supply pipe adjusting valve 29c in order from the upstream side. Further, a third cold water supply pipe 30 connected to another line is connected to the low temperature tank 15. The cold water guided to another line through the third cold water supply pipe 30 is used in the other line.

The high temperature side heat exchanger 14 of the first line and the high temperature tank 17 are connected by the first high temperature tank supply pipe 31. The first high temperature tank supply pipe 31 guides the cold water that has completed heat exchange in the high temperature side heat exchanger 14 of the first line to the high temperature tank 17. Further, the high temperature side heat exchanger 214 of the second line and the intermediate position of the first high temperature tank supply pipe 31 are connected by the second high temperature tank supply pipe 32. The cold water discharged from the high temperature side heat exchanger 214 of the second line joins the first high temperature tank supply pipe 31 after flowing through the second high temperature tank supply pipe 32, and has a high temperature through the first high temperature tank supply pipe 31. It is guided to the tank 17. Further, cold water used in another line joins the first high temperature tank supply pipe 31. That is, the cold water used in the other lines is returned to the cold water tank 13 via the first high temperature tank supply pipe 31.

Further, the first chilled water bypass pipe 33 branches from an intermediate position of the first chilled water supply pipe 28 (specifically, a position between the first chilled water supply pump 28a and the first chilled water supply pipe on-off valve 28b). There is. The first chilled water bypass pipe 33 connects the first chilled water supply pipe 28 and the first high temperature tank supply pipe 31. That is, it is provided so as to bypass the high temperature side heat exchanger 14 of the first line. The first cold water bypass pipe 33 is provided with a first cold water bypass pipe on-off valve 33a. Further, the second chilled water bypass pipe 34 branches from an intermediate position of the second chilled water supply pipe 29 (specifically, a position between the second chilled water supply pump 29a and the second chilled water supply pipe on-off valve 29b). There is. The second chilled water bypass pipe 34 connects the second chilled water supply pipe 29 and the second high temperature tank supply pipe 32. That is, it is provided so as to bypass the high temperature side heat exchanger 214 of the second line. The second cold water bypass pipe 34 is provided with a second cold water bypass pipe on-off valve 34a.

The DBS device 40 includes a dearator 41 that performs a degassing step, a blender 42 that performs a blending step, and a saturator (first carbon dioxide gas dissolving section) 43 that performs a carbon dioxide injection step.
The dearator 41 degass the raw water by spraying the raw water cooled by the high temperature side heat exchanger 14 in the container and evacuating the inside of the container by the vacuum pump 44. The raw water degassed by the dearator 41 is guided to the blender 42 via the third raw water pipe 45. A raw water pump 45a is provided in the third raw water pipe 45. The blender 42 is a device that mixes raw water and syrup. Specifically, the blender 42 mixes the syrup supplied through the syrup pipe 46 with the raw water degassed by the dearator 41. The raw water prepared with the syrup in the blender 42 is guided to the low temperature side heat exchanger 63 via the fourth raw water pipe 47. In the saturator 43, the raw water cooled by the low temperature side heat exchanger 63 is supplied via the fifth raw water pipe 48. The saturator 43 injects carbon dioxide gas supplied through the carbon dioxide gas pipe 49 into the raw water cooled by the low temperature side heat exchanger 63. The raw water injected with carbon dioxide gas by the saturator 43 is guided to the filling machine as a product liquid through the product liquid pipe 50.

The dearator 41, the blender 42, the saturator 43, and the low temperature side heat exchanger 63 described later are unitized as a DBS unit including the piping connecting each device. That is, the devices are compactly arranged so that they are close to each other, and the piping for connecting the devices is short.

The low temperature side cooling unit 60 cools the raw water sent from the blender 42 by brine. The raw water cooled by the low temperature side cooling unit 60 is sent to the saturator 43 as described above.
As shown in FIGS. 4 and 5, the low temperature side cooling unit 60 includes a brine refrigerator (refrigerator) 61 for cooling the brine and a brine tank (storage unit) 62 for storing the brine generated by the brine refrigerator 61. And a low temperature side heat exchanger (first heat exchanger) 63 for cooling the raw water with the brine from the brine tank 62.

The brine refrigerator 61 is a turbo type refrigerator that can handle an ultra-low load that continues operation without stopping even if the load factor is 30% or less. Specifically, it is a refrigerator that can be operated without stopping even when the load factor is around 0%. Further, each of the brine refrigerator 61 has a compressor, a condenser, an expansion valve and an evaporator (all not shown), and the refrigerant circulates in the circulation pipe connecting each device. In the brine refrigerator 61, the electric motor that drives the compressor is controlled by an inverter, and the rotation speed of the compressor can be controlled.
The brine refrigerator 61 cools the brine by exchanging heat between the refrigerant and the brine in the evaporator. The brine cooled by the evaporator is discharged from the brine refrigerator 61 and guided to the brine tank 62 as shown in FIGS. 4 and 5. The brine refrigerator 61 cools the refrigerant and heats the brine by exchanging heat between the refrigerant and the brine in the condenser. The brine heated by the condenser of the brine refrigerator 61 is sent to the brine cooling tower for cooling. The brine cooled in the brine cooling tower is returned to the brine refrigerator 61. In FIG. 2, for the sake of illustration, the first cooling tower 51 and the brine cooling tower are shown together.

The brine tank 62 stores the brine supplied from the bran refrigerator and supplies the stored brine to the low temperature side heat exchangers 263 provided in the first line and the second line. The brine tank 62 includes a low-temperature brine tank 64 in which low-temperature brine is stored and a high-temperature brine tank 65 in which high-temperature cold water is stored. The low temperature brine tank 64 and the high temperature brine tank 65 are separated by a brine partition wall 66. The brine partition wall 66 is formed with a weir portion (not shown) that connects the low temperature brine tank 64 and the high temperature brine tank 65. The weir portion is a through hole penetrating the brine partition wall 66, and is not provided with a valve or the like. The weir portion is formed on the upper part of the brine partition wall 66. The flow path area of the weir section is such that even if the brine is continuously supplied from the refrigerator in a state where the brine is not discharged from each tank, the brine is moved from each tank to the adjacent tank via the weir. It is said that the area does not overflow.

The brine refrigerator 61 and the high temperature brine tank 65 are connected by a pipe 67 on the refrigerator supply side. The refrigerator supply side pipe 67 guides the brine discharged from the high temperature brine tank 65 to the brine refrigerator 61. A third brine pump 67a is provided in the refrigerator supply side pipe 67. Further, a refrigerator discharge side pipe 68 is connected to the brine refrigerator 61 and the low temperature tank 15. The refrigerator discharge side pipe 68 is cooled by the brine refrigerator 61, and guides the brine discharged from the brine refrigerator 61 to the low temperature tank 15.

The low temperature side heat exchanger 63 is a plate heat exchanger that exchanges heat between the raw water led from the blender 42 via the fourth raw water pipe 47 and the brine led from the brine tank 62. The low temperature side heat exchanger 63 cools the raw water and heats the brine by exchanging heat between the raw water and the brine.

Next, the connection between the brine tank 62 and the low temperature side heat exchanger 63 will be described with reference to FIGS. 4 and 5. In FIG. 4, for the sake of illustration, the first line is shown and the second line is omitted. Further, in FIG. 5, for the sake of illustration, the illustration of the brine bypass pipe described later is omitted.
As shown in FIGS. 4 and 5, the low temperature brine tank 64 and the low temperature side heat exchanger 63 provided in the first line are connected by a first brine supply pipe 69. The first brine supply pipe 69 guides the brine discharged from the low temperature brine tank 64 to the low temperature side heat exchanger 63 of the first line. The first brine supply pipe 69 is provided with a first brine temperature sensor 69a and a first brine pump 69b in order from the upstream side. Further, the low temperature brine tank 64 and the low temperature side heat exchanger 263 provided in the second line are connected by a second brine supply pipe 70. The second brine supply pipe 70 guides the brine discharged from the low temperature brine tank 64 to the low temperature side heat exchanger 263 of the second line. The second brine supply pipe 70 is provided with a second brine temperature sensor 70a and a second brine pump 70b in order from the upstream side.

The low temperature side heat exchanger 63 of the first line and the high temperature brine tank 65 are connected by the first brine discharge pipe 71. The first brine discharge pipe 71 guides the brine that has completed heat exchange in the low temperature side heat exchanger 63 of the first line to the high temperature tank 17. The first brine discharge pipe 71 is provided with a first brine discharge pipe valve (first temperature adjusting means) 71a for adjusting the flow rate of the brine flowing through the inside. Further, the low temperature side heat exchanger 263 of the second line and the intermediate position of the first brine discharge pipe 71 are connected by the second brine discharge pipe 72. The brine discharged from the low temperature side heat exchanger 263 of the second line joins the first brine discharge pipe 71 after flowing through the second brine discharge pipe 72, and joins the high temperature brine tank 65 via the first brine discharge pipe 71. Guided to. The second brine discharge pipe 72 is provided with a second brine discharge pipe valve (second temperature adjusting means) 72a that adjusts the flow rate of the brine flowing through the inside.

Further, the first brine bypass pipe 73 branches from an intermediate position of the first brine discharge pipe 71 (specifically, a position on the upstream side of the flow rate adjusting valve of the first brine discharge pipe 71). The first brine bypass pipe 73 connects the first brine discharge pipe 71 and the first brine supply pipe 69. That is, it is provided so as to bypass the brine tank 62. The first brine bypass pipe 73 is provided with a first brine bypass pipe valve (first temperature adjusting means) 73a for adjusting the flow rate of the brine flowing through the inside. Further, a second brine bypass pipe (not shown) is branched from an intermediate position of the second brine discharge pipe 72 (specifically, a position on the upstream side of the flow rate adjusting valve of the second brine discharge pipe 72). The second brine bypass pipe is provided with a second brine bypass pipe valve (second temperature adjusting means) 74a for adjusting the flow rate of the brine flowing through the inside.

As shown in FIG. 5, in the second line as well, the raw water heat-exchanged by the high temperature side heat exchanger 14 is guided to the dearator 41 and degassed by the dearator 41 as in the first line. Further, the raw water degassed by the dialator 41 is guided to the blender 42, and the syrup is mixed with the blender 42. After that, the raw water cooled again by the low temperature side heat exchanger 63 is guided to the saturator 43.
As described above, the first line and the second line share the high-stage refrigerator 11, the low-stage refrigerator 12, the cold water tank 13, the brine refrigerator 61, and the brine tank 62.

The heating unit 80 heats the beverage product by utilizing the exhaust heat from the low-stage refrigerator 12. The heating unit 80 is provided by a hot water tank 81 for storing hot water heated in the condensing unit of the low-stage refrigerator 12, a warmer heat exchanger 82 for heat exchange between the hot water from the hot water tank 81 and the heated water, and the heated water. It is provided with a heating tank 83 for heating a beverage product. The hot water that has been heat-exchanged by the warmer heat exchanger 82 is cooled by the second cooling tower 52 and then returned to the low-stage refrigerator 12. The second cooling tower 52 has a cooling tower heat exchanger 53 and a fan 54.

The hot water tank 81 stores the hot water supplied from the low-stage refrigerator 12, and supplies the stored hot water to the warmer heat exchangers (not shown) provided in the first line and the second line. The hot water tank 81 includes a low-temperature hot water tank 84 in which low-temperature hot water is stored, and a high-temperature hot water tank 85 in which high-temperature hot water is stored. The low-temperature hot water tank 84 and the high-temperature hot water tank 85 are separated by a hot water partition wall 86. The hot water partition wall 86 is formed with a weir portion (not shown) that connects the low temperature hot water tank 84 and the high temperature hot water tank 85. The weir portion is a through hole penetrating the hot water partition wall 86, and is not provided with a valve or the like. The weir portion is formed on the upper part of the hot water partition wall 86. In the flow path area of the weir, even if hot water continues to be supplied from the refrigerator in a state where hot water is not discharged from each tank, hot water is moved from each tank to the adjacent tank via the weir. It is said that the area does not overflow. Further, the high temperature hot water tank 85 is provided with a first hot water temperature sensor 85a for measuring the temperature of the hot water stored in the high temperature hot water tank 85.

The low-stage refrigerator 12 and the high-temperature hot water tank 85 are connected by a high-temperature hot water tank supply pipe 87. The high temperature hot water tank supply pipe 87 is provided with a high temperature hot water tank supply pipe valve 87a. The low-temperature hot water tank supply pipe 88 branches off from the middle position of the high-temperature hot water tank supply pipe 87. Specifically, the low-temperature hot water tank supply pipe 88 is branched on the upstream side of the high-temperature hot water tank supply pipe valve 87a. The low-temperature hot water tank supply pipe 88 connects the high-temperature hot water tank supply pipe 87 and the low-temperature hot water tank 84. The low-temperature hot water tank supply pipe 88 is provided with a low-temperature hot water tank supply pipe valve 88a.

Further, the low-stage refrigerator 12 and the cooling tower heat exchanger 53 are connected by a first hot water return pipe 89. A hot water discharge pump 89a is provided in the first hot water return pipe 89. The cooling tower heat exchanger 53 cools the hot water by exchanging heat between the hot water and the outside air sent by the fan 54 provided in the second cooling tower 52. Further, the cooling tower heat exchanger 53 and the low-stage refrigerator 12 are connected by a second hot water return pipe 90. The second hot water return pipe 90 is provided with a second hot water temperature sensor 90a that measures the temperature of the hot water flowing inside.

The warmer heat exchanger 82 is a plate heat exchanger that exchanges heat between the hot water from the high-temperature hot water tank 85 and the heated water. The warmer heat exchanger 82 cools the hot water and heats the heated water by exchanging heat between the hot water and the heated water.
The high-temperature hot water tank 85 and the warmer heat exchanger 82 provided in the first line are connected by a first hot water supply pipe 91. A hot water supply pump 91a is provided in the first hot water supply pipe 91. The warmer heat exchanger 82 and the low temperature hot water tank 84 are connected by a hot water discharge pipe 93. Further, the high temperature hot water tank 85 and the warmer heat exchanger (not shown) provided in the second line are connected by a second hot water supply pipe 92.

The heating tank 83 has a plurality of tanks (first tank to nth tank). Heating water is stored in each of the plurality of tanks. The heating unit 80 heats the beverage product by spraying the heated water stored in each tank into a container (beverage product) filled with the product liquid by a filling machine. Of the plurality of tanks, only the third tank 83c is connected to the warmer heat exchanger 82. Specifically, the warmer heat exchanger 82 and the third tank 83c are connected by a heated water supply pipe 94 and a heated water discharge pipe 95. The heated water discharge pipe 95 is provided with a heated water pump 95a. Further, the third tank 83c is provided with a heated water temperature sensor 97 that measures the temperature of the heated water stored in the third tank 83c. Further, steam is supplied to the third tank 83c via the steam supply pipe 96.

Further, the beverage product manufacturing equipment 1 is provided with a control device 100. The control device 100 receives the measurement results measured by each temperature sensor and controls each refrigerator, each pump, each valve, and the like.
The control device 100 is composed of, for example, a CPU (Central Processing Unit), a RAM (Random Access Memory), a ROM (Read Only Memory), a computer-readable storage medium, and the like. Then, as an example, a series of processes for realizing various functions are stored in a storage medium or the like in the form of a program, and the CPU reads this program into a RAM or the like to execute information processing / arithmetic processing. As a result, various functions are realized. The program is installed in a ROM or other storage medium in advance, is provided in a state of being stored in a computer-readable storage medium, or is distributed via a wired or wireless communication means. Etc. may be applied. Computer-readable storage media include magnetic disks, magneto-optical disks, CD-ROMs, DVD-ROMs, semiconductor memories, and the like.

As shown in FIG. 7, the control device 100 includes a brine control unit 101, a raw water temperature control unit 108, a hot water control unit 110, and a cold water control unit 120.

As shown in FIG. 8, the brine control unit 101 includes a first temperature determination unit 102, a second temperature determination unit 103, a refrigerator temperature determination unit 104, a first brine temperature control unit 105, and a second brine temperature. It has a control unit 106 and a refrigerator control unit 107.
The first temperature determining unit 102 determines the temperature of the brine supplied to the low temperature side heat exchanger 63 of the first line. The second temperature determining unit 103 determines the temperature of the brine supplied to the low temperature side heat exchanger 263 of the second line. The refrigerator temperature determination unit 104 determines the temperature of the brine discharged from the brine refrigerator 61 based on the temperature determined by the first temperature determination unit 102 and the temperature determined by the second temperature determination unit 103. The first brine temperature control unit 105 discharges the first brine so that the temperature of the brine guided from the brine tank 62 to the low temperature side heat exchanger 63 of the first line becomes the temperature determined by the first temperature determination unit 102. The opening degree of the piping valve 71a and the first brine bypass piping valve 73a is controlled. The second brine temperature control unit 106 discharges the second brine so that the temperature of the brine guided from the brine tank 62 to the low temperature side heat exchanger 263 of the second line becomes the temperature determined by the second temperature determination unit 103. The opening degree of the piping valve 72a and the second brine bypass piping valve 74a is controlled. The refrigerator control unit 107 controls the brine refrigerator 61 so that the temperature of the brine discharged from the brine refrigerator 61 becomes the temperature determined by the refrigerator temperature determination unit 104.

The brine control unit 101 operates as follows. The first temperature determining unit 102 determines the temperature of the brine supplied to the low temperature side heat exchanger 63 of the first line based on the request from the DBS device 40 provided in the first line. Further, the second temperature determining unit 103 supplies the low temperature side heat exchanger 63 of the first line based on the request from the DBS device (diarator 241, blender 242, etc. shown in FIG. 5) provided in the second line. Determine the temperature of the brine to be made. Further, the refrigerator temperature determining unit 104 discharges the lower temperature from the brine refrigerator 61 as compared with the temperature determined by the first temperature determining unit 102 and the temperature determined by the second temperature determining unit 103. It is determined as the temperature of the brine (hereinafter, referred to as "brine refrigerator 61 outlet temperature"). At this time, the brine control unit 101 determines the set temperature of the outlet temperature of the brine refrigerator 61. Specifically, the current outlet temperature of the brine refrigerator 61 and the newly determined outlet temperature of the brine refrigerator 61 are compared. If the newly determined temperature of the brine refrigerator 61 is the same as the current outlet temperature of the brine refrigerator 61, nothing is performed as it is. On the other hand, when the newly determined brine refrigerator 61 temperature is different from the current brine refrigerator 61 outlet temperature, the setting of the brine refrigerator 61 outlet temperature is changed. Then, the refrigerator control unit 107 controls the brine refrigerator 61 so that the temperature of the brine discharged from the brine refrigerator 61 becomes the temperature determined by the refrigerator temperature determination unit 104. Specifically, the rotation speed of the compressor provided in the brine refrigerator 61 is adjusted. As described above, since the outlet temperature of the brine refrigerator 61 is constant, hunting can be prevented.

Further, in the first brine temperature control unit 105, the temperature of the brine guided from the brine tank 62 to the low temperature side heat exchanger 63 of the first line is the temperature determined by the first temperature determination unit 102 (in this embodiment, an example). The opening degree of the first brine discharge pipe valve 71a and the first brine bypass pipe valve 73a is controlled so as to be -1 ° C.). That is, by adjusting the mixing ratio of the low-temperature brine from the low-temperature tank 15 flowing through the first brine discharge pipe 71 and the high-temperature brine discharged from the heat exchanger flowing through the first brine bypass pipe 73, The temperature of the brine led to the low temperature side heat exchanger 63 of the first line is adjusted. The first brine temperature control unit 105 may control the opening degree of the first brine discharge pipe valve 71a and the opening degree of the first brine bypass pipe valve 73a to be 100%.
Further, the second brine temperature control unit 106 is provided with a second brine temperature control unit 106 so that the temperature of the brine guided from the brine tank 62 to the low temperature side heat exchanger 263 of the second line is the temperature determined by the second temperature determination unit 103. The opening degree of the brine discharge pipe valve 72a and the second brine bypass pipe valve 74a is controlled. Since the method of adjusting the temperature of the brine by the second brine temperature control unit 106 is substantially the same as that of the first brine temperature control unit 105, detailed description thereof will be omitted.

Further, the raw water temperature control unit 108 adjusts the opening degree of the flow rate adjusting valve of the first cold water supply pipe 28 based on the temperature measured by the raw water temperature sensor 27a. Specifically, the temperature measured by the raw water temperature sensor 27a is transmitted to the raw water temperature control unit 108, and the raw water temperature control unit 108 has a predetermined temperature measured by the raw water temperature sensor 27a (10 as an example in the present embodiment). The opening degree of the first chilled water supply pipe 28 flow control valve is adjusted so as to be (° C.). The predetermined temperature is not limited to the above example. It is suitable if it is between 10 ° C. and 20 ° C.

Further, as shown in FIG. 9, the hot water control unit 110 includes a switching control unit 111, a fan control unit 112, and a hot water supply pump control unit 113. The hot water control unit 110 has a heating mode in which the heating unit 80 heats the beverage product, and a cooling mode in which the temperature of the brine supplied to the low-stage refrigerator 12 is lowered. When the load factor of the low-stage refrigerator 12 is 30% or more, the operation is performed in the heating mode. Further, when the load factor of the low-stage refrigerator 12 is lower than 30% (in the case of ultra-low load operation), the operation is performed in the cooling mode.

The switching control unit 111 switches the destination of the hot water by controlling the opening degree of the high temperature hot water tank supply pipe valve 87a and the low temperature hot water tank supply pipe valve 88a so that the hot water is guided to the low temperature hot water tank 84. Specifically, in the heating mode, hot water is supplied to the high-temperature hot water tank 85, and in the cooling mode, hot water is supplied to the low-temperature hot water tank 84.

In the cooling mode, the switching control unit 111 puts the high-temperature hot water tank supply pipe valve 87a in a fully closed state and the low-temperature hot water tank supply pipe valve 88a in a fully open state. Further, in the cooling mode, the fan control unit 112 sets the temperature of the hot water measured by the second hot water temperature sensor 90a (in other words, the inlet temperature of the low-stage refrigerator 12) to a predetermined hot water temperature (about 25 ° C.). As described above, the rotation speed of the fan 54 of the second cooling tower 52 is adjusted. In the cooling mode, the hot water supply pump 91a is stopped.

In the heating mode, the switching control unit 111 sets the high-temperature hot water tank supply pipe valve 87a in the fully open state and the low-temperature hot water tank supply pipe valve 88a in the fully closed state. Further, in the cooling mode, the fan control unit 112 rotates the fan 54 of the second cooling tower 52 so that the temperature of the hot water measured by the second hot water temperature sensor 90a becomes a predetermined hot water temperature (about 33 ° C.). To adjust. Further, in the heating mode, when the temperature measured by the first hot water sensor provided in the high temperature hot water tank 85 by the hot water supply pump control unit 113 is larger than the temperature measured by the heated water temperature sensor 97 by a predetermined value or more. (In the present embodiment, for example, when the temperature is higher than 1.5 ° C.), the hot water supply pump 91a is driven to guide the hot water stored in the high temperature hot water tank 85 to the warmer heat exchanger 82.
As shown by the solid line in FIG. 11, the set value of the hot water temperature is changed to 25 ° C. (cooling mode) or 33 ° C. (heating mode) when the load factor of the low-stage refrigerator 12 is 30%. However, as shown by the broken line in FIG. 11, the fan control unit 112 adjusts the rotation speed of the fan 54 of the cooling tower so that the actual hot water temperature rises or falls at a pace of 0.5 ° C. per minute.

Further, as shown in FIG. 10, the cold water control unit 120 includes a high-stage refrigerator inlet temperature control unit 121, a low-stage refrigerator inlet temperature control unit 122, a first temperature range changing unit 123, and a second temperature range. It has a changing unit 124 and an outlet temperature control unit 125.
The high-stage refrigerator inlet temperature control unit 121 opens the opening degree of the high-temperature tank discharge pipe valve 20a and the first medium-temperature tank discharge pipe valve 21a so that the temperature measured by the first temperature sensor 20b falls within a predetermined first temperature range. To control. The low-stage refrigerator inlet temperature control unit 122 opens the second medium-temperature tank discharge pipe valve 23a and the low-temperature tank discharge pipe valve 24a so that the temperature measured by the second temperature sensor 23b falls within a predetermined second temperature range. To control. The first temperature range changing unit 123 changes the first temperature range according to the load factor of the high-stage refrigerator 11. Further, the second temperature range changing unit 124 changes the second temperature range according to the load factor of the low-stage refrigerator 12. The outlet temperature control unit 125 controls the high-stage refrigerator 11 so that the temperature of the cold water discharged from the high-stage refrigerator 11 is based on the temperature detected by the medium-temperature tank temperature sensor 16a.

The cold water control unit 120 operates as follows. In the high-stage refrigerator inlet temperature control unit 121, the temperature measured by the first temperature sensor 20b (hereinafter, referred to as “high-stage refrigerator 11 inlet temperature”) is a predetermined first temperature range (in this embodiment, an example). The opening degree of the high temperature tank discharge pipe valve 20a and the first medium temperature tank discharge pipe valve 21a is controlled so as to be about 17 ° C.). That is, the temperature of the cold water led to the high-stage refrigerator 11 is adjusted by adjusting the mixing ratio of the cold water from the high temperature tank 17 and the cold water from the medium temperature tank 16. The high-stage refrigerator inlet temperature control unit 121 controls so that the opening degree obtained by adding the opening degree of the high-temperature tank discharge pipe valve 20a and the opening degree of the first medium-temperature tank discharge pipe valve 21a is 100%. May be good.

Further, in the low-stage refrigerator inlet temperature control unit 122, the temperature measured by the second temperature sensor 23b (hereinafter, referred to as “low-stage refrigerator 12 inlet temperature”) is a predetermined second temperature range (in the present embodiment). , As an example, about 11.5 ° C.), the opening degree of the second medium temperature tank discharge pipe valve 23a and the low temperature tank discharge pipe valve 24a is controlled. That is, the temperature of the cold water led to the low-stage refrigerator 12 is adjusted by adjusting the mixing ratio of the cold water from the medium-temperature tank 16 and the cold water from the low-temperature tank 15. The low-stage refrigerator inlet temperature control unit 122 controls the opening degree of the sum of the opening degree of the second medium temperature tank discharge pipe valve 23a and the opening degree of the low temperature tank discharge pipe valve 24a to be 100%. May be good. Further, the first temperature range and the second temperature range may be set automatically, or may be set manually by the operator.

Further, the first temperature range changing unit 123 changes the first temperature range according to the load factor of the high-stage refrigerator 11. Specifically, as shown in FIG. 12, when the high-stage refrigerator 11 is started (when the entire first line is started or when the high-stage refrigerator 11 is increased from one to two), as shown in FIG. After a lapse of a predetermined time from the start of the compressor, the first temperature range is changed from about 11.5 ° C to about 17 ° C. The high-stage refrigerator 11 does not reach a predetermined load factor immediately after being started, and the load factor increases with time. Therefore, when the temperature at the inlet of the high-stage refrigerator 11 is higher than the temperature of the cold water stored in the medium-temperature tank 16 at the time of starting, the cold water cannot be cooled by the high-stage refrigerator 11 and remains at a high temperature. It may be led to the medium temperature bath 16. In order to suppress such a situation, when the high-stage refrigerator 11 is started, the first temperature range is raised so as to respond to the increase in the load factor of the high-stage refrigerator 11. When raising the first temperature range, the temperature is raised at a pace of 0.5 ° C. per minute.
Further, the second temperature range changing unit 124 changes the second temperature range according to the load factor of the low-stage refrigerator 12. Specifically, when the low-stage refrigerator 12 is started, as shown in FIG. 13, the second temperature range is changed from about 5 ° C. to about 11.5 ° C. after a predetermined time has elapsed since the compressor was started. .. When raising the rise in the second temperature range, the rise is made at a pace of 0.5 ° C. per minute.

The outlet temperature control unit 125 receives the measurement result transmitted by the medium temperature tank temperature sensor 16a, and determines the temperature of the cold water discharged from the high-stage refrigerator 11 (hereinafter, referred to as “high-stage refrigerator 11 outlet temperature”). , The high-stage refrigerator 11 is controlled so that the temperature becomes the temperature measured by the middle tank temperature sensor. Specifically, the rotation speed of the compressor is adjusted.

Next, the operation process of the brine refrigerator 61 performed by the control device 100 will be described with reference to the flowchart of FIG.
First, when the operation button of the brine refrigerator 61 is changed from "OFF" to "ON" in step S1, the control device 100 activates the brine refrigerator 61 in step S2. Next, in step S3, the control device 100 waits for a predetermined time (t2) until the brine refrigerator 61 starts up. Next, the control device 100 waits for a predetermined time (t1) of the control determination cycle of the brine refrigerator 61 in step S4.
Next, the control device 100 determines the refrigerator set temperature in step S5. Specifically, the refrigerator temperature determining unit 104 sets the lower temperature of the temperature determined by the first temperature determining unit 102 and the temperature determined by the second temperature determining unit 103 to the outlet of the brine refrigerator 61. Determined as temperature. At this time, the brine control unit 101 determines whether or not the set temperature at the outlet of the brine refrigerator 61 has been changed. Specifically, when the current outlet temperature of the brine refrigerator 61 and the newly determined outlet temperature of the brine refrigerator 61 are the same, it is determined that the set temperature has not been changed. Further, when the current outlet temperature of the brine refrigerator 61 and the newly determined outlet temperature of the brine refrigerator 61 are different, it is determined that the set temperature has been changed.
If it is determined in step S5 that the set temperature has not been changed, the control device 100 proceeds to step S6. On the other hand, if it is determined that the set temperature has not been changed, the control device 100 proceeds to step S8. In step S8, the setting of the outlet temperature of the brine refrigerator 61 is changed to the newly determined temperature. Then, the refrigerator control unit 107 controls the brine refrigerator 61 so that the temperature of the brine discharged from the brine refrigerator 61 becomes the temperature determined by the refrigerator temperature determination unit 104. Next, the control device 100 proceeds to step S9, waits for a predetermined time (t2) until the change in the set temperature is reflected, and proceeds to step S6.
In step S6, it is determined whether the operation button of the brine refrigerator 61 is changed from "ON" to "OFF". If it is determined that the "ON" has not been changed to "OFF", the process returns to step S5. If it is determined that the change has been made from "ON" to "OFF", the process proceeds to step S7, the brine refrigerator 61 is stopped, and this process is completed.

Next, the operation processing of the hot water tank 81 and the heating unit 80 performed by the control device 100 will be described with reference to the flowchart of FIG.
First, in step S11, the hot water control unit 110 sets the operation of the hot water tank 81 and the heating unit 80 to the automatic mode. The automatic mode is a mode in which the cooling mode and the heating mode are automatically switched according to the load factor of the low-stage refrigerator 12. Next, in step S12, it is determined whether or not the load factor of the low-stage refrigerator 12 is 30% or more. If it is determined that the load factor is not 30% or more, the process proceeds to step S17 and the operation in the cooling mode is started. After starting the operation in the cooling mode, the process returns to step S12.

If it is determined in step S12 that the load factor is 30% or more, the process proceeds to step S13, and the operation in the heating mode is started. Next, the control device 100 proceeds to step S14 and sends an operation command to the DBS device 40. Next, the process proceeds to step S15, and it is determined whether or not the temperature of the hot water stored in the high-temperature hot water tank 85 is 1.5 ° C. or more higher than the temperature of the heated water. If it is determined that the temperature is 1.5 ° C. or higher, the process proceeds to step S16, the hot water supply pump 91a is operated, and hot water is guided to the warmer heat exchanger 82. If it is determined that the temperature is not higher than 1.5 ° C., the process proceeds to step S18, and the hot water supply pump 91a is stopped or the stopped state is maintained.

Next, the operation processing of the refrigerator system performed by the control device 100 will be described with reference to the flowcharts of FIGS. 16 to 19. The refrigerator system refers to a system in which a cold / hot cooling unit, a high temperature cooling unit, and a heating unit 80 are combined.

First, as shown in FIG. 16, when this process is started, the refrigerator system is started in step S21. Next, in step S23, an operation command is sent to the low-stage refrigerator 12. In parallel, in step S22, the setting of the outlet temperature of the high-stage refrigerator 11 is started. Specifically, the outlet temperature of the high-stage refrigerator 11 is set to the temperature measured by the middle tank temperature sensor. Next, in step S24, the low-stage side pump 23c, the hot water supply pump 91a, and the like are driven. Next, the operation of the low-stage refrigerator 12 is started in step S25. At this time, in parallel, in step S26, the control of the inlet temperature of the low-stage refrigerator 12 is started. Next, in step S27, it is determined whether or not the refrigerator system stop command has been issued. If it is determined that the stop command has not been issued, the process proceeds to step S28 and the number control determination is performed.

As shown in FIG. 20, the number control determination in step S28 is performed based on the total load value of the cold water refrigerators (low-stage refrigerator 12 and high-stage refrigerator 11). The hatched portion in FIG. 20 means the high-stage refrigerator 11. Further, the shaded portion indicates the ultra-low load operation of the low-stage refrigerator 12. As shown in FIG. 20, the low-stage refrigerator 12 is operated by one unit when the total load is from 0 kW to 1000 kW. When the total load becomes 1000 kW or more, the number of stages is increased, and the low-stage refrigerator 12 is operated by two units. When the total load becomes 2000 kW or more, the number of stages is further increased, and the low-stage refrigerator 12 is operated by two units and the high-stage refrigerator 11 is operated by one unit (that is, a total of three units). When the total load becomes 3000 kW or more, the number of stages is further increased, and two low-stage refrigerators 12 and two high-stage refrigerators 11 (that is, a total of four units) are operated. On the contrary, when the total load is reduced to 2700 kW or less, the number of low-stage refrigerators 12 is reduced to two and the number of high-stage refrigerators 11 is reduced to one (that is, a total of three). When the total load is 1700 kW or less, the number of low-stage refrigerators 12 is reduced to two. When the total load is 800 kW or less, the number of low-stage refrigerators 12 is reduced to one. If it does not cross each threshold, it is judged that the status quo is maintained.
The threshold value of the total load of the refrigerator is an example and is not limited to the numerical value described above. The total load threshold is set according to the capacity of the refrigerator and the like. The above example describes an example in the case of a 1100 kW refrigerator, for example.

As shown in FIG. 16, if it is determined in step S28 that the number of steps is increased, the process proceeds to step S29. If it is determined in step S28 that the number of steps is reduced, the process proceeds to step S30. If it is determined in step S28 that the status quo is to be maintained, the process proceeds to step S31. When the process proceeds to step S31, the process returns to step S27.

When the process proceeds to step S29, the process proceeds to step S32 next, as shown in FIG. In step S32, an operation command is sent to the increasing-stage refrigerator (high-stage refrigerator 11 and / or low-stage refrigerator 12). Next, in step S33, the operation of various pumps attached to the increasing number of refrigerators is started. Next, in step S34, the operation of the refrigerator for increasing the number of stages is started. At this time, in parallel, the control of the inlet temperature of the refrigerator, which is increased in step S35, is started. Next, the process returns to step S27.

When the process proceeds to step S30, the process proceeds to step S36 as shown in FIG. In step S36, a stop command is sent to the decrementing refrigerator (high-stage refrigerator 11 and / or low-stage refrigerator 12). Next, in step S37, the operation of various pumps attached to the decrementing refrigerator is stopped. Next, in step S38, the operation of the refrigerator for increasing the number of stages is stopped. At this time, in parallel, the control of the inlet temperature of the refrigerator whose stage is reduced in step S39 is stopped. Next, the process returns to step S27.

If it is determined in step S27 that a stop command has been issued, the process proceeds to step S40 as shown in FIG. In step S40, a stop command is sent to all the refrigerators (high-stage refrigerator 11 and / or low-stage refrigerator 12). Next, in step S41, the operation of various pumps attached to all the refrigerators is stopped. Next, in step S42, the operation of all the refrigerators is stopped. At this time, in parallel, the control of the inlet temperature of all the refrigerators is stopped in step S43. This process ends when the operation of all refrigerators is stopped.

Next, the flow of the fluid or the like in the beverage product manufacturing facility 1 according to the present embodiment will be described. In the following description, the temperature of each fluid is described, but the temperature given in the following description is an example and may be another temperature.

[Raw water, product liquids and beverage products]
The raw water stored in the raw water tank 2 is stored at a temperature similar to the temperature of the atmosphere (in this embodiment, about 30 ° C. as an example). As shown in FIG. 4, the raw water stored in the raw water tank 2 is guided to the high temperature side heat exchanger 14 via the first raw water pipe 26. The raw water is cooled to about 10 ° C. by exchanging heat with cold water in the high temperature side heat exchanger 14. The raw water cooled by the high temperature side heat exchanger 14 is guided to the dearator 41 via the second raw water pipe 27 and degassed. The degassed raw water is guided to the blender 42 via the third raw water pipe 45, and the syrup liquid is prepared by the blender 42. The raw water prepared with the syrup liquid is discharged from the blender 42 and guided to the low temperature side heat exchanger 63 via the fourth raw water pipe 47. The raw water is cooled to about 3 ° C. by exchanging heat with the brine in the low temperature side heat exchanger 63. The raw water cooled by the low temperature side heat exchanger 63 is guided to the saturator 43 via the fifth raw water pipe 48 and is injected with carbon dioxide gas to become a product liquid. The product liquid discharged from the saturator 43 is guided to the filling machine via the product liquid pipe 50 and filled in a container to become a beverage product. The beverage product is guided to the heating tank 83 (see FIG. 6) and heated to about 30 ° C. in the heating tank 83. It is packed in a packing container with a heated boxing machine. The packaged beverage product is then shipped.

[Cold water]
The temperature of the cold water stored in the cold water tank 13 differs depending on each tank. Specifically, cold water of about 5 ° C. is stored in the low temperature tank 15, cold water of about 11.5 ° C. is stored in the medium temperature tank 16, and cold water of about 17.5 ° C. is stored in the high temperature tank 17. ing. As shown in FIGS. 2 and 3, cold water stored in the high temperature tank 17 and / or the medium temperature tank 16 of the cold water tank 13 is guided to the high-stage refrigerator 11. The cold water guided to the high-stage refrigerator 11 is cooled to about 11.5 ° C. by exchanging heat with the refrigerant circulating in the high-stage refrigerator 11. The cold water cooled by the high-stage refrigerator 11 is discharged from the high-stage refrigerator 11 and guided to the medium-temperature tank 16 via the medium-temperature tank supply pipe 22. Cold water stored in the medium temperature tank 16 and / or the low temperature tank 15 is guided to the low stage refrigerator 12. The cold water guided to the low-stage refrigerator 12 is cooled to about 5 ° C. by exchanging heat with the refrigerant circulating in the low-stage refrigerator 12. The cold water cooled by the low-stage refrigerator 12 is discharged from the low-stage refrigerator 12 and guided to the low-temperature tank 15 via the low-temperature tank supply pipe 25.

The cold water stored in the low temperature tank 15 is sent to each line and used via the first chilled water supply pipe 28, the second chilled water supply pipe 29, and the third chilled water supply pipe 30. The cold water sent through the first cold water supply pipe 28 is guided to the high temperature side heat exchanger 14 of the first line. The cold water guided to the high temperature side heat exchanger 14 cools the raw water by exchanging heat with the raw water, and is heated to about 25 ° C. by the raw water. The cold water heated by the high temperature side heat exchanger 14 is guided to the high temperature tank 17 via the first high temperature tank supply pipe 31. The cold water guided to the high temperature side heat exchanger 214 of the second line is also heated by the high temperature side heat exchanger 14 and guided to the high temperature tank 17 via the second high temperature tank supply pipe 32 in substantially the same manner as the first line. Further, water is sent to another line via the third cold water supply pipe 30 and used in the other line. Cold water used in other lines is also guided to the high temperature tank 17. Examples of other lines include aseptic filling lines for extracting, blending, and liquid-treating raw materials. In this way, cold water circulates in the beverage product manufacturing facility 1.

In addition, since the partition wall that separates each tank is provided with a weir, even if cold water is unevenly supplied to a specific tank, the weir guides the cold water to another adjacent tank. The storage capacity of each tank is averaged.

[Brine]
The temperature of the cold water stored in the brine tank 62 differs depending on the tank. Specifically, the low temperature brine tank 64 stores brine at about −2 ° C., and the high temperature brine tank 65 stores brine at about 6 ° C. As shown in FIGS. 4 and 5, the brine stored in the high temperature brine tank 65 is guided to the brine refrigerator 61 via the refrigerator supply side pipe 67. The brine led to the brine refrigerator 61 is cooled to about -2 ° C. by exchanging heat with the refrigerant circulating in the brine refrigerator 61. The brine cooled by the brine refrigerator 61 is discharged from the brine refrigerator 61 and guided to the low temperature brine tank 64 via the refrigerator discharge side pipe 68.

The brine stored in the low temperature brine tank 64 is supplied to each line via the first brine supply pipe 69 and the second brine supply pipe 70. The brine supplied through the first brine supply pipe 69 is guided to the low temperature side heat exchanger 63 of the first line. The brine guided to the low temperature side heat exchanger 63 cools the raw water by exchanging heat with the raw water, and is heated to about 6 ° C. by the raw water. The brine heated by the low temperature side heat exchanger 63 is guided to the high temperature brine tank 65 via the first brine discharge pipe 71. The brine led to the low temperature side heat exchanger 263 of the second line is also heated by the low temperature side heat exchanger 63 and guided to the high temperature brine tank 65 via the second brine discharge pipe 72 in substantially the same manner as the first line. In this way, the brine circulates in the beverage product manufacturing facility 1.

[Hot water]
The temperature of the hot water stored in the hot water tank 81 differs depending on each tank. Specifically, the low-temperature hot water tank 84 stores hot water at about 33 ° C., and the high-temperature hot water tank 85 stores hot water at about 38 ° C.
In the low-stage refrigerator 12, hot water is heated to about 38 ° C. by exchanging heat with the refrigerant circulating in the low-stage refrigerator 12. As shown in FIG. 6, the hot water heated by the low-stage refrigerator 12 is discharged from the low-stage refrigerator 12 and passes through the high-temperature hot water tank supply pipe 87 and / or the low-temperature hot water tank supply pipe 88. It is led to 85 or a low temperature hot water tank 84. Specifically, in the heating mode in which the heating unit 80 heats the beverage product, the beverage product is guided to the high-temperature hot water tank 85. Further, in the cooling mode in which the temperature of the brine supplied to the low-stage refrigerator 12 is lowered, the water is guided to the low-temperature hot water tank 84.

First, the heating mode will be described.
In the heating mode, the hot water stored in the high-temperature hot water tank 85 is guided to the warmer heat exchanger 82 via the hot water supply pipe. The hot water guided to the warmer heat exchanger 82 heats the heated water by exchanging heat with the heated water, and is cooled to about 33 ° C. by the heated water. The hot water cooled by the warmer heat exchanger 82 is guided to the low temperature hot water tank 84 via the hot water discharge pipe 93. The hot water guided to the warmer heat exchanger of the second line is also cooled by the warmer heat exchanger 82 and guided to the low temperature hot water tank 84 in substantially the same manner as in the first line.
The hot water led to the low-temperature hot water tank 84 is guided to the cooling tower heat exchanger 53 via the first hot water return pipe 89. The hot water guided to the cooling tower heat exchanger 53 is cooled to about 33 ° C. by exchanging heat between the hot water and the outside air sent by the fan 54 provided in the second cooling tower 52. The hot water cooled by the cooling tower heat exchanger 53 is guided to the low-stage refrigerator 12 via the second hot water return pipe 90.

Next, the cooling mode will be described.
In the cooling mode, the hot water stored in the low temperature tank 15 is guided to the cooling tower heat exchanger 53 via the first hot water return pipe 89. The hot water guided to the cooling tower heat exchanger 53 is cooled to about 25 ° C. by exchanging heat between the hot water and the outside air sent by the fan 54 provided in the second cooling tower 52. The hot water cooled by the cooling tower heat exchanger 53 is guided to the low-stage refrigerator 12 via the second hot water return pipe 90.
In this way, hot water circulates in the beverage product manufacturing facility 1.

[Heating water]
In the warmer heat exchanger 82, the heated water is heated to about 35 ° C. by exchanging heat with the hot water. The heated water heated by the warmer heat exchanger 82 is guided to the heating tank 83 (specifically, the third tank 83c) via the heated water supply pipe 94. In the heating tank 83, the beverage product is heated. By heating the beverage product, the heated water is cooled to about 30 ° C. The heated water obtained by heating the beverage product is discharged from the heating tank 83 and guided to the warmer heat exchanger 82 via the heated water discharge pipe 95. In this way, the heated water circulates in the beverage product manufacturing facility 1.

According to this embodiment, the following effects are exhibited.
In the present embodiment, the raw water guided to the saturator 43 is cooled by the high temperature side cooling unit 10 and then cooled by the low temperature side cooling unit 60. That is, the raw water is cooled in two stages. By cooling the raw water by the two cooling units in this way, the amount of heat cooled by each cooling unit can be reduced as compared with the case where the raw water is cooled by one cooling unit. As a result, the power required for each cooling unit can be reduced, so that the raw water can be efficiently cooled at each cooling unit. Therefore, the energy efficiency of the entire beverage product manufacturing facility 1 can be improved.

In this embodiment, the saturator 43, the blender 42, and the dearator 41 are unitized. Since the dearator 41 and the saturator 43 are in close proximity to each other, it is difficult to provide a new cooling unit between the dearator 41 and the saturator 43. In the present embodiment, the high temperature side cooling unit 10 is provided on the upstream side in the raw water flow from the dearator 41. That is, since the high temperature side cooling unit 10 is provided on the upstream side outside the unit, the unit is not affected when the high temperature side cooling unit 10 is installed. Therefore, the high temperature side cooling unit 10 can be easily provided.

In the dearator 41, the higher the temperature of the supplied raw water, the more suitable the degassing can be performed. In the present embodiment, the raw water is cooled to 10 ° C. or higher and 20 ° C. or lower by the high temperature side cooling unit 10. In this way, the raw water supplied to the dialator 41 is set to 10 ° C. or higher. Therefore, since the temperature of the raw water supplied to the dearator 41 does not become too low, the dearator 41 can be suitably degassed.
Further, the raw water is cooled to 20 ° C. or lower by the high temperature side cooling unit 10. As a result, since the raw water is suitably cooled in the high temperature side cooling unit 10, the amount of heat to be cooled by the low temperature side cooling unit 60 provided on the downstream side of the high temperature side cooling unit 10 does not increase excessively. Therefore, since the increase in power required by the low temperature side cooling unit 60 can be suppressed, the energy efficiency of the entire beverage product manufacturing equipment 1 can be improved.
Further, since the temperature of the raw water is set in a predetermined temperature range in front of the dearator 41, stable operation is performed in the dearator 41 and the device downstream of the dearator 41 (for example, the low temperature side cooling unit 60, the saturator 43, etc.). Can be done.

In the present embodiment, the brine cooled by the brine refrigerator 61 is guided to the low temperature side heat exchanger 63 of the first line and the low temperature side heat exchanger 263 of the second line via the brine tank 62. As a result, the brine tank 62 functions as a buffer even when the amount or temperature of the raw water supplied by the low temperature side heat exchanger 63 of the first line or the low temperature side heat exchanger 263 of the second line changes. Therefore, the changes generated in each heat exchanger do not directly affect the brine refrigerator 61. Therefore, the influence of the change generated in each heat exchanger can be made difficult to reach the brine refrigerator 61, so that the operating efficiency of the brine refrigerator 61 can be improved.
Further, in the present embodiment, the low temperature side heat exchanger 63 of the first line and the low temperature side heat exchanger 263 of the second line supply raw water to different saturators 43. Further, the brine is led from one brine tank 62 to the low temperature side heat exchanger 63 of the first line and the low temperature side heat exchanger 263 of the second line. This means that the heat sources of the low temperature side heat exchanger 63 of the first line and the low temperature side heat exchanger 263 of the second line can be integrated.
For example, when the product manufactured by the saturator 43 of the first line and / or the saturator of the second line (not shown) is changed, the amount of raw water supplied to the saturator 43 is changed in the long term. In such a case, the amount of raw water guided to the heat exchanger that cools the raw water supplied to the saturator 43 is also changed in the long term.
In such a case, a brine refrigerator 61 for cooling the brine used in the low temperature side heat exchanger 63 of the first line and a brine refrigerator 61 for cooling the brine used in the low temperature side heat exchanger 263 of the second line. When is different (that is, when the heat sources are not integrated), it is necessary to change the load of the brine refrigerator 61 according to the amount of raw water guided to each heat exchanger.
On the other hand, in the present embodiment, since the heat sources of the low temperature side heat exchanger 63 of the first line and the low temperature side heat exchanger 263 of the second line are integrated as described above, the low temperature side heat exchange of the first line Even if the amount of raw water supplied in the vessel 63 or the low temperature side heat exchanger 263 of the second line changes, the amount of brine corresponding to the amount of raw water supplied to each heat exchanger is added to the brine tank. It can be led from 62 to each heat exchanger. As a result, the influence of the change generated in each heat exchanger can be made less likely to reach the brine refrigerator 61, so that the operating efficiency of the brine refrigerator 61 can be improved.

In the present embodiment, the first brine discharge pipe valve 71a and the first brine discharge pipe valve 71a and the like so that the temperature of the brine led from the brine tank 62 to the low temperature side heat exchanger 63 of the first line becomes the temperature determined by the first temperature determining unit 102. The opening degree of the first brine bypass piping valve 73a is controlled. Further, the second brine discharge pipe valve 72a and the second brine so that the temperature of the brine guided from the brine tank 62 to the low temperature side heat exchanger 263 of the second line becomes the temperature determined by the second temperature determining unit 103. The opening degree of the bypass piping valve 74a is controlled. As a result, the temperature of the brine guided to the low temperature side heat exchanger 63 of the first line and the low temperature side heat exchanger 263 of the second line can be set to a desired temperature. Therefore, the temperature of the raw water guided to the saturator 43 of the first line and the saturator of the second line can be set to a desired temperature.
Further, in the present embodiment, the temperature of the brine discharged from the brine refrigerator 61 is determined based on the temperature determined by the first temperature determining unit 102 and the temperature determined by the second temperature determining unit 103. As a result, for example, when the temperature determined by the refrigerator temperature determining unit 104 is close to the temperature determined by the first temperature determining unit 102 and the temperature determined by the second temperature determining unit 103, the low temperature side heat of each line is obtained. The adjustment range of the temperature of the brine led to the exchanger 63 is reduced. Therefore, it is possible to reduce the energy required for adjustment or suppress the energy loss required for adjustment. Therefore, the energy efficiency of the entire beverage product manufacturing equipment 1 can be improved.

In the present embodiment, the heat of the hot water heated by the exhaust heat of the low-stage refrigerator 12 is used to heat the container (hereinafter, referred to as “beverage product”) filled with raw water at the filling portion. .. As a result, the beverage product can be heated by utilizing the exhaust heat of the low-stage refrigerator 12. Therefore, the energy efficiency of the entire beverage product manufacturing facility 1 can be improved as compared with the case where an independent device for heating the beverage product is provided.

In the present embodiment, when the load factor of the low-stage refrigerator 12 is equal to or less than a predetermined value, the hot water discharged from the low-stage refrigerator 12 is guided to the low-temperature hot water tank 84. Further, the hot water guided to the low-temperature hot water tank 84 is discharged from the low-temperature hot water tank 84 and cooled by the second cooling tower 52. Then, the hot water cooled by the second cooling tower 52 is returned to the low-stage refrigerator 12 via the second hot water return pipe 90. Since the hot water circulates in this way, the temperature of the hot water guided to the low-stage refrigerator 12 can be reduced.
When the load factor of the low-stage refrigerator 12 is low, surging is likely to occur due to factors such as a decrease in the rotation speed of the compressor provided in the low-stage refrigerator 12. In the present embodiment, as described above, when the load factor is equal to or less than a predetermined value, the temperature of the hot water guided to the low-stage refrigerator 12 can be reduced. As a result, even when the load factor is low, the pressure difference of the circulating refrigerant can be reduced by reducing the temperature of the hot water, so that surging can be suppressed.
Further, the hot water cooled by the second cooling tower 52 passes through the low-stage refrigerator 12 and is guided to the low-temperature hot water tank 84 of the hot water tank 81. That is, the hot water circulates without passing through the high temperature hot water tank 85. As a result, the cooled hot water is not supplied to the high temperature hot water tank 85 in which the hot water leading to the heating unit 80 is stored. Therefore, it is possible to suppress a decrease in the temperature of the hot water stored in the high temperature hot water tank 85.
Further, in the present embodiment, the exhaust heat of the low-stage refrigerator 12 can be utilized in the heating unit 80 depending on whether the hot water discharged from the low-stage refrigerator 12 is guided to the high-temperature hot water tank 85 or the low-temperature hot water tank 84. The state is switched between the state and the state in which the exhaust heat of the low-stage refrigerator 12 is not used. Therefore, it is possible to switch whether or not to utilize the exhaust heat in the heating unit 80 without stopping the low-stage refrigerator 12.

In the present embodiment, the rotation speed of the fan 54 of the second cooling tower 52 is controlled so that the temperature of the hot water detected by the second hot water temperature sensor 90a falls within a predetermined temperature range. As a result, the temperature of the hot water supplied to the low-stage refrigerator 12 can be set within a predetermined temperature range. Therefore, the temperature of the hot water led to the low-stage refrigerator 12 can be reduced more accurately. Therefore, even when the load factor is low, the pressure difference of the circulating refrigerant can be reduced more reliably by reducing the temperature of the hot water, so that surging can be suppressed.

In the present embodiment, when the temperature of the hot water stored in the hot water tank 81 is higher than the temperature of the heated water provided for heating by the heating unit 80 by a predetermined value or more, the hot water is guided to the heat exchanger. There is. As a result, it is possible to suppress the occurrence of a situation in which the heated water is cooled by exchanging heat in a state where the temperature of the hot water is lower than that of the heated water. Therefore, since the beverage product can be heated more reliably by utilizing the exhaust heat of the low-stage refrigerator 12, the energy efficiency of the entire beverage product manufacturing facility 1 can be improved.

In the present embodiment, the hot water heated by the exhaust heat of the low-stage refrigerator 12 is separately guided to the heating unit 80 of the first line and the heating unit of the second line via the hot water tank 81. As a result, even when the load of the low-stage refrigerator 12 changes and the temperature of the hot water changes, the hot water tank 81 functions as a buffer, so that the change generated in the low-stage refrigerator 12 directly occurs. It does not affect the heating unit 80. Therefore, each heating unit 80 can preferably heat the beverage product.
Further, in the present embodiment, hot water is guided from one hot water tank 81 to the heating section 80 of the first line and the heating section of the second line. As a result, the heat sources of the heating unit 80 of the first line and the heating unit of the second line can be integrated.
For example, when the product to be heated by the heating unit 80 of the first line and / or the heating unit of the second line is changed, the amount of heat heated by the heating unit 80 is changed in the long term. In such a case, the amount of hot water supplied to the heating unit 80 is also changed in the long term.
In such a case, the low-stage refrigerator 12 that heats the hot water used for heating in the heating unit 80 of the first line and the low-stage refrigerator 12 that heats the hot water used for heating in the heating unit of the second line. When they are different (that is, when the heat sources are not integrated), it is necessary to change the load of the low-stage refrigerator 12 according to the amount of hot water led to each heating unit 80.
On the other hand, in the present embodiment, since the heat sources of the heating unit 80 of the first line and the heating unit of the second line are integrated as described above, the heating unit 80 of the first line or the heating unit of the second line Even when the amount of hot water required changes, the amount of hot water required by each heating unit 80 can be guided from the hot water tank 81 to each heating unit 80. As a result, the influence of the change generated in each heating unit 80 can be made difficult to reach the low-stage refrigerator 12, so that the operating efficiency of the low-stage refrigerator 12 can be improved.

In the present embodiment, the cold water returned from the high-temperature side heat exchanger 14 is guided to the high-stage refrigerator 11 after passing through the high-temperature tank 17. As a result, even if the temperature of the cold water returned to the high temperature tank 17 changes due to the load in the high temperature side heat exchanger 14, the high temperature tank 17 functions as a buffer, so that the high temperature side heat exchanger The influence of the load fluctuation in 14 can be made difficult to reach the high-stage refrigerator 11. Therefore, the temperature of the cold water guided to the high-stage refrigerator 11 can be stabilized. Further, in the present embodiment, the cold water discharged from the high-stage refrigerator 11 is guided to the low-stage refrigerator 12 via the medium-temperature tank 16. Therefore, when the temperature of the cold water returned to the high temperature tank 17 changes due to the fluctuation of the load on the high temperature side heat exchanger 14, the low stage refrigerator 12 may also be affected. Even in such a case, since the medium temperature tank 16 functions as a buffer, the influence of the load fluctuation on the high temperature side heat exchanger 14 can be made less likely to reach the low stage refrigerator 12. Therefore, the temperature of the cold water led to the low-stage refrigerator 12 can be stabilized.
Further, in the present embodiment, cold water is guided from the high temperature tank 17 and the medium temperature tank 16 to the high-stage refrigerator 11. In this way, cold water is guided from the high temperature tank 17 which is greatly affected when the load on the high temperature side heat exchanger 14 fluctuates and the medium temperature tank 16 which is less affected than the high temperature tank 17 to the high stage refrigerator 11. There is. This makes it easier to stabilize the temperature of the cold water guided to the high-stage refrigerator 11 as compared with the configuration in which the cold water is guided to the high-stage refrigerator 11 only from the high-temperature tank 17. Further, in the present embodiment, cold water is guided from the medium temperature tank 16 and the low temperature tank 15 to the low stage refrigerator 12. In this way, cold water is guided from the medium temperature tank 16 which is easily affected when the load on the high temperature side heat exchanger 14 fluctuates and the low temperature tank 15 which is less affected than the medium temperature tank 16 to the low stage refrigerator 12. There is. As a result, the temperature of the cold water guided to the low-stage refrigerator 12 can be easily stabilized as compared with the configuration in which the cold water is guided to the low-stage refrigerator 12 only from the medium-temperature tank 16.
When the load on the high temperature side heat exchanger 14 fluctuates, the temperature of the cold water returning to the high-stage refrigerator 11 changes. On the other hand, the return temperature to the refrigerator can be gradually changed through the high temperature tank 17.

In the present embodiment, the opening degrees of the high temperature tank discharge pipe valve 20a and the first medium temperature tank discharge pipe valve 21a are controlled so that the temperature detected by the first temperature sensor 20b is within a predetermined temperature range. In other words, by changing the mixing ratio of cold water having different temperatures, the temperature detected by the first temperature sensor 20b is within a predetermined temperature range. As a result, the temperature of the cold water supplied to the high-stage refrigerator can be set within a predetermined temperature range. Similarly, the temperature of the cold water supplied to the low-stage refrigerator 12 can be set within a predetermined temperature range. Therefore, the operating efficiency of each refrigerator can be improved.

In the present embodiment, the first temperature range is changed according to the load of the high-stage refrigerator 11, and the second temperature range is changed according to the load of the low-stage refrigerator 12. Thereby, the temperature of the cold water discharged from the high-stage refrigerator 11 and the low-stage refrigerator 12 can be stabilized. In particular, cold water discharged from the high-stage refrigerator 11 and the low-stage refrigerator 12 even when the load of each refrigerator is likely to fluctuate, for example, when the high-stage refrigerator 11 and the low-stage refrigerator 12 are started. The temperature can be stabilized.

When the temperature of the cold water discharged from the high-stage refrigerator 11 changes, the temperature of the cold water stored in the medium-temperature tank 16 also changes accordingly. Further, if the temperature of the cold water in the medium temperature tank 16 changes, the temperature also changes on the downstream side of the medium temperature tank 16, and the temperature of the cold water supplied to the high temperature side heat exchanger 14 may also change. is there.
In the present embodiment, the high-stage refrigerator 11 is controlled so that the temperature of the cold water discharged from the high-stage refrigerator 11 becomes a temperature based on the temperature detected by the medium-temperature tank temperature sensor 16a. As a result, the temperature of the cold water stored in the medium temperature tank 16 can be maintained at a predetermined temperature. Therefore, the temperature of the cold water can be stabilized even on the downstream side of the medium temperature tank 16.

In the present embodiment, the low temperature tank 15 and the medium temperature tank 16 communicate with each other at the first weir portion 18a. As a result, for example, even when the cold water is unevenly supplied to the low temperature tank 15 or the medium temperature tank 16, the cold water can be delivered via the first weir portion 18a, so that the cold water is stored in the low temperature tank 15 and the medium temperature tank 16. It is possible to suppress the unevenness of the amount of cold water.

In the present embodiment, the medium temperature tank 16 and the low temperature tank 15 communicate with each other at the second weir portion 19a. As a result, for example, even when the cold water is unevenly supplied to the medium temperature tank 16 or the low temperature tank 15, the cold water can be delivered via the second weir portion 19a, so that the cold water is stored in the medium temperature tank 16 and the low temperature tank 15. It is possible to suppress the unevenness of the amount of cold water.

In this embodiment, cold water is guided from one low temperature tank 15 to each high temperature side heat exchanger 14. That is, a refrigerator that cools the cold water supplied to each high-temperature side heat exchanger 14 is common.
For example, when the amount of cold water used in each high temperature side heat exchanger 14 is changed, the refrigerators for cooling the cold water used in each high temperature side heat exchanger 14 are different (that is, the heat sources are integrated). If not), it is necessary to change the load of the refrigerator according to the amount of cold water guided to each high temperature side heat exchanger 14.
On the other hand, in the present embodiment, since the refrigerator that cools the cold water supplied to each high temperature side heat exchanger 14 is common, the amount of cold water used in each high temperature side heat exchanger 14 changes. However, the amount of cold water used in each high temperature side heat exchanger 14 can be guided from the low temperature tank 15 to each high temperature side heat exchanger 14. As a result, the influence of the change in the amount of cold water used in each high-temperature side heat exchanger 14 can be made difficult to reach the low-stage refrigerator 12 and the high-stage refrigerator 11, so that the low-stage refrigerator 12 and the high-stage freezer can be easily affected. The operating efficiency of the machine 11 can be improved.

The present disclosure is not limited to the above embodiment, and can be appropriately modified without departing from the gist thereof.
For example, in the above embodiment, the line for producing a beverage product containing carbon dioxide gas has described two examples, but the present disclosure is not limited to this. The number of lines for producing a beverage product containing carbon dioxide gas may be one, or may be three or more.

The beverage product manufacturing system described in the present embodiment described above is grasped as follows, for example.
The beverage product manufacturing system according to one aspect of the present disclosure is a beverage product manufacturing system (1) that manufactures a beverage product from raw water, and has a first cooling unit (10) for cooling the raw water and the first cooling unit (1). A second cooling unit (60) for cooling the raw water cooled in 10) and a first carbon dioxide gas dissolving unit (43) for dissolving carbon dioxide in the raw water cooled by the second cooling unit (60). Be prepared.

In the above configuration, the raw water guided to the first carbon dioxide gas dissolving section is cooled by the first cooling section and then cooled by the second cooling section. That is, the raw water is cooled in two stages. By cooling the raw water by the two cooling units in this way, the amount of heat cooled by each cooling unit can be reduced as compared with the case where the raw water is cooled by one cooling unit. As a result, the power required for each cooling unit can be reduced, so that the raw water can be efficiently cooled at each cooling unit. Therefore, the energy efficiency of the entire beverage product manufacturing system can be improved.

Further, the beverage product manufacturing system according to one aspect of the present disclosure includes a degassing unit (41) for degassing raw water, and the first cooling unit (10) is supplied to the degassing unit (41). Cool the raw water.

The carbon dioxide gas dissolving part and the degassing part may be unitized. In such a case, since the degassing portion and the carbon dioxide gas are close to each other, it is difficult to provide a new cooling portion between the degassing portion and the carbon dioxide gas dissolving portion. In the above configuration, the first cooling unit is provided on the upstream side of the raw water flow from the degassing unit. As a result, for example, even when the degassing unit and the first carbon dioxide gas dissolving unit are unitized, the first cooling unit may be provided on the upstream side of this unit, so that the first cooling unit is installed. It is not affected by the unit when doing so. Therefore, the first cooling unit can be easily provided.

Further, in the beverage product manufacturing system according to one aspect of the present disclosure, the first cooling unit cools the supplied raw water to 10 ° C. or higher and 20 ° C. or lower.

In the degassing section, the higher the temperature of the supplied raw water, the more suitable the degassing can be performed. In the above configuration, the raw water is cooled to 10 ° C. or higher and 20 ° C. or lower in the first cooling unit. In this way, the raw water supplied to the degassing part is set to 10 ° C. or higher. Therefore, since the temperature of the raw water supplied to the degassing portion does not become too low, the degassing portion can be suitably degassed.
In addition, the raw water is cooled to 20 ° C. or lower in the first cooling unit. As a result, since the raw water is suitably cooled in the first cooling unit, the amount of heat cooled by the second cooling unit provided on the downstream side of the first cooling unit does not increase excessively. Therefore, it is possible to suppress an increase in the power required for the second cooling unit, so that the energy efficiency of the entire beverage product manufacturing system can be improved.
Further, since the temperature of the raw water is set in a predetermined temperature range in front of the degassing part, it is stable in the degassing part and the device on the downstream side of the degassing part (for example, the second cooling part, the carbon dioxide gas dissolving part, etc.). Can drive.

Further, the beverage product manufacturing system according to one aspect of the present disclosure includes a second carbon dioxide gas dissolving unit which is a carbon dioxide gas dissolving unit different from the first carbon dioxide gas dissolving unit (43), and the second cooling unit (60). ) Is a refrigerator (61) having a refrigerant circuit and cooling the cooling refrigerant by the circulating refrigerant circulating in the refrigerant circuit, and a storage unit (62) for storing the cooling refrigerant cooled by the refrigerator (61). ), The cooling refrigerant derived from the storage unit (62), and the raw water supplied to the first carbon dioxide gas melting unit (43) exchange heat with the first heat exchanger (63) to cool the raw water. ), And a second heat exchanger (263) that cools the raw water by exchanging heat between the cooling refrigerant derived from the storage unit (62) and the raw water supplied to the second carbon dioxide gas dissolving unit. Has.

In the above configuration, the cooling refrigerant cooled by the refrigerator is guided to the first heat exchanger and the second heat exchanger via the storage unit. As a result, even if the amount or temperature of the raw water supplied in the first heat exchanger or the second heat exchanger changes, the storage unit functions as a buffer, so that it occurs in each heat exchanger. The change does not directly affect the refrigerator. Therefore, the influence of the change generated in each heat exchanger can be made difficult to reach the refrigerator, and the operating efficiency of the refrigerator can be improved.
Further, in the above configuration, the first heat exchanger and the second heat exchanger supply raw water to different carbon dioxide gas dissolving portions. Further, the cooling refrigerant is guided from one storage unit to the first heat exchanger and the second heat exchanger. This means that the heat sources of the first heat exchanger and the second heat exchanger can be integrated.
For example, when the product produced in the first carbon dioxide gas dissolving part and / or the second carbon dioxide gas dissolving part is changed, the amount of raw water supplied to the carbon dioxide gas dissolving part is changed in a long term. In such a case, the amount of raw water guided to the heat exchanger that cools the raw water supplied to the carbon dioxide gas dissolving portion is also changed in the long term.
In such a case, the refrigerator that cools the cooling refrigerant used in the first heat exchanger and the refrigerator that cools the cooling refrigerant used in the second carbon dioxide gas melting unit are different (that is,). If the heat sources are not integrated), it is necessary to change the load of the chiller according to the amount of raw water guided to each heat exchanger.
On the other hand, in the above configuration, since the heat sources of the first heat exchanger and the second heat exchanger are integrated as described above, the amount of raw water supplied in the first heat exchanger or the second heat exchanger is increased. Even if it changes, an amount of cooling refrigerant corresponding to the amount of raw water supplied to each heat exchanger can be guided from the storage unit to each heat exchanger. As a result, the influence of changes generated in each heat exchanger can be made less likely to affect the refrigerator, so that the operating efficiency of the refrigerator can be improved.

Further, in the beverage product manufacturing system according to one aspect of the present disclosure, the first temperature adjusting means (71a,) for adjusting the temperature of the cooling refrigerant led from the storage unit (62) to the first heat exchanger (62). 73a), second temperature adjusting means (72a, 74a) for adjusting the temperature of the cooling refrigerant led from the storage unit (62) to the second heat exchanger (263), and the first heat exchanger ( A first temperature determining unit (102) that determines the temperature of the cooling refrigerant supplied to 63) and a second temperature determining unit that determines the temperature of the cooling refrigerant supplied to the second heat exchanger (263). (103), the cooling refrigerant discharged from the refrigerating machine (61) based on the temperature determined by the first temperature determining unit (102) and the temperature determined by the second temperature determining unit (103). The refrigerator temperature determination unit (104) for determining the temperature of the refrigerator is provided.

In the above configuration, the first temperature adjusting means is controlled so that the temperature of the cooling refrigerant led from the storage unit to the first heat exchanger becomes the temperature determined by the first temperature determining unit. Further, the second temperature adjusting means is controlled so that the temperature of the cooling refrigerant led from the storage unit to the second heat exchanger becomes the temperature determined by the second temperature determining unit. As a result, the temperature of the cooling refrigerant guided to the first heat exchanger and the second heat exchanger can be set to a desired temperature. Therefore, the temperature of the raw water guided to the first carbon dioxide gas dissolving portion and the second carbon dioxide gas dissolving portion can be set to a desired temperature.
Further, in the above configuration, the temperature of the cooling refrigerant discharged from the low temperature side refrigerator is determined based on the temperature determined by the first temperature determining unit and the temperature determined by the second temperature determining unit. As a result, for example, when the temperature determined by the refrigerator temperature determining unit is close to the temperature determined by the first temperature determining unit and the temperature determined by the second temperature determining unit, the first temperature adjusting means and the second temperature The temperature adjustment range of the cooling refrigerant in the adjusting means becomes smaller. Therefore, it is possible to reduce the energy required for adjustment or suppress the energy loss required for adjustment. Therefore, the energy efficiency of the entire beverage product manufacturing system can be improved.

1: Beverage product manufacturing equipment (beverage product manufacturing system)
2: Raw water tank 10: High temperature side cooling unit (first cooling unit)
11: High-stage refrigerating machine 12: Low-stage refrigerating machine 13: Cold water tank 14: High-temperature side heat exchanger 15: Low-temperature tank 16: Medium-temperature tank 16a: Medium-temperature tank temperature sensor 17: High-temperature tank 18: First cold water partition 18a: No. 1 dam portion 19: second chilled water partition 19a: second dam portion 20: high temperature tank discharge pipe 20a: high temperature tank discharge pipe valve 20b: first temperature sensor 20c: high stage side pump 21: first medium temperature tank discharge pipe 21a: 1st medium temperature tank discharge pipe valve 22: Medium temperature tank supply pipe 23: 2nd medium temperature tank discharge pipe 23a: 2nd medium temperature tank discharge pipe valve 23b: 2nd temperature sensor 23c: Low stage side pump 24: Low temperature tank discharge pipe 24a: Low temperature tank discharge pipe valve 25: Low temperature tank supply pipe 26: 1st raw water pipe 27: 2nd raw water pipe 27a: Raw water temperature sensor 28: 1st cold water supply pipe 28a: 1st cold water supply pump 28b: 1st cold water supply pipe opening / closing Valve 28c: 1st chilled water supply pipe adjusting valve 29: 2nd chilled water supply pipe 29a: 2nd chilled water supply pump 29b: 2nd chilled water supply pipe opening / closing valve 29c: 2nd chilled water supply pipe adjusting valve 30: 3rd chilled water supply pipe 31 : 1st high temperature tank supply pipe 32: 2nd high temperature tank supply pipe 33: 1st chilled water bypass pipe 33a: 1st chilled water bypass pipe on-off valve 34: 2nd chilled water bypass pipe 34a: 2nd chilled water bypass pipe on-off valve 40: DBS Device 41: Dearator (first carbon dioxide gas dissolving part)
42: Brenda 43: Saturator 44: Vacuum pump 45: Third raw water pipe 45a: Raw water pump 46: Syrup pipe 47: Fourth raw water pipe 48: Fifth raw water pipe 49: Carbon dioxide gas pipe 50: Product liquid pipe 51: First Cooling tower 52: Second cooling tower 53: Cooling tower heat exchanger 54: Fan 60: Low temperature side cooling unit (second cooling unit)
61: Brine freezer (freezer)
62: Brine tank 63: Low temperature side heat exchanger (first heat exchanger)
64: Low temperature brine tank 65: High temperature brine tank 66: Brine partition 67: Refrigerator supply side piping 67a: Third brine pump 68: Refrigerator discharge side piping 69: First brine supply piping 69a: First brine temperature sensor 69b: 1st brine pump 70: 2nd brine supply pipe 70a: 2nd brine temperature sensor 70b: 2nd brine pump 71: 1st brine discharge pipe 71a: 1st brine discharge pipe valve (1st temperature adjusting means)
72: Second brine discharge pipe 72a: Second brine discharge pipe valve (second temperature adjusting means)
73: First brine bypass piping 73a: First brine bypass piping valve (first temperature adjusting means)
74a: Second brine bypass piping valve (second temperature adjusting means)
80: Heating unit 81: Hot water tank 82: Warmer heat exchanger 83: Heating tank 83c: Third tank 84: Low temperature hot water tank 85: High temperature hot water tank 85a: First hot water temperature sensor 86: Hot water partition 87: High temperature hot water tank supply Pipe 87a: High temperature hot water tank supply pipe valve 88: Low temperature hot water tank supply pipe 88a: Low temperature hot water tank supply pipe valve 89: First hot water return pipe 89a: Hot water discharge pump 90: Second hot water return pipe 90a: Second hot water temperature sensor 91: 1st hot water supply pipe 91a: hot water supply pump 92: 2nd hot water supply pipe 93: hot water discharge pipe 94: heated water supply pipe 95: heated water discharge pipe 95a: heated water pump 96: steam supply pipe 97: heated water Temperature sensor 100: Control device 101: Brine control unit 102: First temperature determination unit 103: Second temperature determination unit 104: Refrigerator temperature determination unit 105: First brine temperature control unit 106: Second brine temperature control unit 107: Refrigerator control unit 108: Raw water temperature control unit 110: Hot water control unit 111: Switching control unit 112: Fan control unit 113: Hot water supply pump control unit 120: Cold water control unit 121: High-stage refrigerator inlet temperature control unit 122: Low Stage refrigerator inlet temperature control unit 123: 1st temperature range change unit 124: 2nd temperature range change unit 125: Outlet temperature control unit 214: 2nd line high temperature side heat exchanger 263: 2nd line low temperature side heat exchange vessel

Claims (5)

A beverage product manufacturing system that manufactures beverage products from raw water.
The first cooling unit that cools the raw water and
A second cooling unit that cools the raw water cooled by the first cooling unit, and
A beverage product manufacturing system including a first carbon dioxide gas dissolving unit that dissolves carbon dioxide gas in raw water cooled by the second cooling unit. Equipped with a degassing part to degas raw water
The beverage product manufacturing system according to claim 1, wherein the first cooling unit cools the raw water supplied to the degassing unit. The beverage product manufacturing system according to claim 2, wherein the first cooling unit cools the supplied raw water to 10 ° C. or higher and 20 ° C. or lower. A second carbon dioxide gas dissolving unit, which is a carbon dioxide gas dissolving unit different from the first carbon dioxide gas dissolving unit, is provided.
The second cooling unit includes a refrigerator having a refrigerant circuit and cooling the cooling refrigerant with a circulating refrigerant circulating in the refrigerant circuit, a storage unit for storing the cooling refrigerant cooled by the refrigerator, and the storage unit. A first heat exchanger that cools the raw water by exchanging heat between the cooling refrigerant derived from the unit and the raw water supplied to the first carbon dioxide gas melting unit, and the cooling refrigerant guided from the storage unit. The beverage product manufacturing system according to any one of claims 1 to 3, further comprising a second heat exchanger that cools the raw water by exchanging heat with the raw water supplied to the second carbon dioxide gas melting unit. A first temperature adjusting means for adjusting the temperature of the cooling refrigerant led from the storage unit to the first heat exchanger, and
A second temperature adjusting means for adjusting the temperature of the cooling refrigerant led from the storage unit to the second heat exchanger, and
A first temperature determining unit that determines the temperature of the cooling refrigerant supplied to the first heat exchanger, and
A second temperature determining unit that determines the temperature of the cooling refrigerant supplied to the second heat exchanger, and
A refrigerator temperature determining unit that determines the temperature of the cooling refrigerant discharged from the refrigerator based on the temperature determined by the first temperature determining unit and the temperature determined by the second temperature determining unit is provided. The beverage product manufacturing system according to claim 4.

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