CN113227681A - Method for controlling operation of ice maker - Google Patents
Method for controlling operation of ice maker Download PDFInfo
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- CN113227681A CN113227681A CN201980085900.1A CN201980085900A CN113227681A CN 113227681 A CN113227681 A CN 113227681A CN 201980085900 A CN201980085900 A CN 201980085900A CN 113227681 A CN113227681 A CN 113227681A
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- Prior art keywords
- ice
- ice maker
- refrigerant
- pressure
- seawater
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25C—PRODUCING, WORKING OR HANDLING ICE
- F25C5/00—Working or handling ice
- F25C5/02—Apparatus for disintegrating, removing or harvesting ice
- F25C5/04—Apparatus for disintegrating, removing or harvesting ice without the use of saws
- F25C5/12—Ice-shaving machines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25C—PRODUCING, WORKING OR HANDLING ICE
- F25C1/00—Producing ice
- F25C1/12—Producing ice by freezing water on cooled surfaces, e.g. to form slabs
- F25C1/14—Producing ice by freezing water on cooled surfaces, e.g. to form slabs to form thin sheets which are removed by scraping or wedging, e.g. in the form of flakes
- F25C1/145—Producing ice by freezing water on cooled surfaces, e.g. to form slabs to form thin sheets which are removed by scraping or wedging, e.g. in the form of flakes from the inner walls of cooled bodies
- F25C1/147—Producing ice by freezing water on cooled surfaces, e.g. to form slabs to form thin sheets which are removed by scraping or wedging, e.g. in the form of flakes from the inner walls of cooled bodies by using augers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
- F25B49/022—Compressor control arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25C—PRODUCING, WORKING OR HANDLING ICE
- F25C1/00—Producing ice
- F25C1/12—Producing ice by freezing water on cooled surfaces, e.g. to form slabs
- F25C1/14—Producing ice by freezing water on cooled surfaces, e.g. to form slabs to form thin sheets which are removed by scraping or wedging, e.g. in the form of flakes
- F25C1/145—Producing ice by freezing water on cooled surfaces, e.g. to form slabs to form thin sheets which are removed by scraping or wedging, e.g. in the form of flakes from the inner walls of cooled bodies
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25C—PRODUCING, WORKING OR HANDLING ICE
- F25C2301/00—Special arrangements or features for producing ice
- F25C2301/002—Producing ice slurries
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25C—PRODUCING, WORKING OR HANDLING ICE
- F25C2600/00—Control issues
- F25C2600/04—Control means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25C—PRODUCING, WORKING OR HANDLING ICE
- F25C2700/00—Sensing or detecting of parameters; Sensors therefor
- F25C2700/08—Power to drive the auger motor of an auger type ice making machine
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Production, Working, Storing, Or Distribution Of Ice (AREA)
Abstract
An operation control method for an ice maker (1) that cools a medium to be cooled so as to exchange heat with a refrigerant and generates ice. When the drive current of an ice scraping part (15) of the ice maker (1) exceeds a first current value, the evaporation temperature of the refrigerant supplied to the ice maker (1) is increased.
Description
Technical Field
The present disclosure relates to an operation control method of an ice maker. More specifically, the present invention relates to an operation control method for an ice maker that produces sherbet-like ice slurry.
Background
Sometimes, sherbet-like ice slurry is used to refrigerate fish and the like. As the above-described apparatus for producing ice slurry, for example, a double-pipe ice maker including an inner pipe and an outer pipe is known (for example, see patent document 1). An ice making system including the ice maker described above includes a tank that stores a medium to be cooled such as seawater, and the medium to be cooled supplied from the tank to an inner pipe of the ice maker exchanges heat with a refrigerant supplied to an annular space between an outer pipe and an inner pipe of the ice maker to generate ice slurry, and the generated ice slurry is returned to the tank.
Documents of the prior art
Patent document
Patent document 1: japanese patent No. 3888789
Disclosure of Invention
Technical problem to be solved by the invention
In the Ice making system including the Ice making machine as described above, when an Ice filling Factor IPF (Ice storage Factor), which is a ratio of Ice (Ice/(Ice + cooled medium)) stored in the container, is excessively large, clogging occurs in a pipe of the Ice making system, and the Ice filling Factor in the container is controlled within a certain range because Ice making efficiency is lowered. Therefore, conventionally, a water level sensor, an ultrasonic sensor, or the like provided in a container is used to estimate the amount of ice in the container, and the operation of the ice maker is controlled according to the estimated amount of ice.
However, the ice maker in the ice making system described above controls the operation of the ice maker, which is an element on the machine side, in accordance with an operation command from a sensor attached to a container, which is an element on the machine side. Therefore, the reliability of the operation control of the ice maker may be lowered due to a communication abnormality with the apparatus side or the like.
An object of the present disclosure is to provide an operation control method of an ice maker capable of improving reliability of operation control.
Technical scheme for solving technical problem
In the operation control method of the ice maker according to the first aspect of the present disclosure (hereinafter, also simply referred to as "operation control method"),
(1) an operation control method of an ice maker in which ice is generated by cooling a medium to be cooled in a heat exchange manner with a refrigerant,
when the driving current of the ice scraping part of the ice maker exceeds a first current value, the evaporation temperature of the refrigerant supplied to the ice maker is increased.
In the operation control method according to the first aspect of the present disclosure, the operation of the ice maker is controlled according to the current value of the ice scraping portion of the ice maker, which is the machine-side element. Therefore, the reliability of the operation control of the ice maker can be improved without causing a problem such as a communication abnormality with the device side as in the related art.
(2) In the operation control method of the above (1), the evaporation temperature can be increased stepwise according to the excess amount of the current. In this case, the evaporation temperature is increased step by step according to the amount of excess of the first current value in the ice scraping unit of the ice maker, and ice generation in the ice maker can be suppressed step by step.
(3) In the operation control method of (1) or (2), the operation of the ice maker may be stopped when the drive current exceeds a second current value that is larger than the first current value.
In the operation control method according to the second aspect of the present disclosure,
(4) an operation control method of an ice maker in which ice is generated by cooling a medium to be cooled in a heat exchange manner with a refrigerant,
in the case where a pressure difference between a pressure at an inlet portion and a pressure at an outlet portion of a cooled medium in the ice maker exceeds a first pressure value, an evaporation temperature of refrigerant supplied to the ice maker is increased.
In the operation control method of the second aspect of the present disclosure, the operation of the ice maker is controlled according to the pressure difference between the pressure at the inlet portion and the pressure at the outlet portion of the cooled medium in the ice maker, which is the element on the machine side. Therefore, the reliability of the operation control of the ice maker can be improved without causing a problem such as a communication abnormality with the device side as in the related art.
(5) In the operation control method of the above (4), the evaporation temperature can be increased stepwise according to the excess amount of the pressure difference. In this case, the evaporation temperature is increased step by step according to an amount by which the pressure difference between the pressure at the inlet portion and the pressure at the outlet portion of the medium to be cooled in the ice maker exceeds the first pressure value, and ice generation by the ice maker can be suppressed step by step.
(6) In the operation control method according to the above (4) or (5), the operation of the ice maker may be stopped when the pressure difference exceeds a second pressure value that is greater than the first pressure value.
Drawings
Fig. 1 is a schematic configuration diagram of an example of an ice making system including an ice maker to which the operation control method of the present disclosure is applied.
Fig. 2 is a side explanatory view of the ice maker shown in fig. 1.
Fig. 3 is a sectional explanatory view of an ice scraping portion in the ice maker shown in fig. 2.
Fig. 4 is a diagram of an example of control of the evaporation temperature in the operation control method according to the first embodiment.
Fig. 5 is a graph illustrating characteristics of a motor current according to the operation control method of the first embodiment.
Fig. 6 is a diagram showing an example of control of the evaporation temperature in the operation control method according to the second embodiment.
Detailed Description
The operation control method of the present disclosure will be described in detail below with reference to the drawings. In addition, the present disclosure is not limited to these examples, but is shown in the form of claims, and is intended to include meanings equivalent to the claims and all changes within the scope thereof.
[ Ice making System ]
First, an example of an ice making system including an ice maker to which the operation control method of the present disclosure is applied will be described.
Fig. 1 is a schematic configuration diagram of an ice making system a including an ice maker 1 to which an operation control method of the present disclosure is applied, and fig. 2 is a side explanatory diagram of the ice maker 1 shown in fig. 1. The ice making system a is a system in which seawater stored in a seawater tank described later is used as a raw material, ice slurry is continuously generated by the ice making machine 1, and the generated ice slurry is returned to the seawater tank. Ice slurry refers to sherbet-like ice in which fine ice is mixed in water or an aqueous solution, and is also called slurry ice, ice slurry, slurry ice, crushed ice, or liquid ice. The ice making system a can continuously generate ice slurry based on seawater. Therefore, the ice making system a is installed in, for example, a fishing boat, a fishing port, or the like, and the ice slurry returned to the seawater container is used for keeping fresh fish cold. In the illustrated ice making system a, fresh seawater in an amount balanced with the amount of the ice slurry to be used (consumed) is replenished to the seawater tank by a replenishing pump (not shown).
The ice making system a includes an ice making machine 1 constituting a use-side heat exchanger, a compressor 2, a heat-source-side heat exchanger 3, a four-way selector valve 4, a use-side expansion valve 5, a heat-source-side expansion valve 6, a superheater 7, a tank 8, a seawater tank (storage tank) 9, and a pump 10, with seawater being used as a cooling medium. The refrigeration apparatus is constituted by the ice maker 1, the compressor 2, the heat source side heat exchanger 3, the four-way selector valve 4, the usage side expansion valve 5, the heat source side expansion valve 6, the superheater 7, and the accumulator 8, and these devices or components are connected by pipes to constitute a refrigerant circuit. The ice maker 1, the seawater tank 9, and the pump 10 are also connected by pipes to form a seawater circulation path. In the ice making system a, the ice maker 1, the compressor 2, the heat source side heat exchanger 3, the four-way selector valve 4, the usage side expansion valve 5, the heat source side expansion valve 6, the superheater 7, the accumulator 8, and the like are machine side elements, and the seawater tank 9, the pump 10, the piping, and the like are equipment side elements.
Further, the ice making system a includes a control device 30. The control device 30 includes a CPU and memories such as a RAM and a ROM. Control device 30 implements various controls related to the operation of ice making system a, including the operation control of the present disclosure, by the CPU executing a computer program stored in the memory.
During the normal ice making operation, the four-way selector valve 4 is maintained in the state shown by the solid line in fig. 1. The high-temperature and high-pressure gas-state refrigerant discharged from the compressor 2 flows into the heat source side heat exchanger 3 functioning as a condenser through the four-way selector valve 4, and is condensed and liquefied by heat exchange with air by the operation of the blower fan 11. The liquefied refrigerant flows into the usage-side expansion valve 5 via the heat-source-side expansion valve 6 and the accumulator 8 in the fully open state. The refrigerant is decompressed to a predetermined low pressure by the usage-side expansion valve 5, and is supplied from a refrigerant inlet pipe described later into an annular space 14 between an inner pipe 12 and an outer pipe 13 constituting an evaporator E of the ice maker 1.
The refrigerant discharged into the annular space 14 exchanges heat with the seawater flowing into the inner pipe 12 by the pump 10 and evaporates. The seawater cooled by the evaporation of the refrigerant flows out of the inner pipe 12 and returns to the seawater container 8. The refrigerant evaporated and gasified in the ice maker 1 is sucked into the compressor 2. At this time, if the refrigerant in a state of not being completely evaporated but containing liquid in the ice maker 1 enters the compressor 2, a sudden increase in the pressure inside the compressor cylinder (liquid compression) and a decrease in the viscosity of the refrigerator oil cause a failure of the compressor 2, and therefore, in order to protect the compressor 2, the refrigerant leaving the ice maker 1 is heated by the superheater 7 and returned to the compressor 2. The superheater 7 is a double-tube type superheater, and refrigerant leaving the ice maker 1 is superheated and returned to the compressor 2 while flowing through a space between an inner tube and an outer tube of the superheater 7.
Further, if the flow of seawater in the inner pipe 12 of the ice maker 1 is stopped and ice is accumulated (accumulated ice) in the inner pipe 12, the ice maker 1 cannot be operated. In this case, a defrosting operation (heating operation) is performed to melt the ice in the inner tube 12. At this time, the four-way selector valve 4 is held in the state shown by the broken line in fig. 1. The high-temperature and high-pressure gas-state refrigerant discharged from the compressor 2 flows into an annular space 14 between an inner tube 12 and an outer tube 13 of the ice maker 1 via the four-way selector valve 4, exchanges heat with seawater containing ice in the inner tube 12, and is condensed and liquefied. The liquefied refrigerant flows into the heat-source-side expansion valve 6 through the fully-opened usage-side expansion valve 5 and the accumulator 8, is reduced in pressure to a predetermined low pressure by the heat-source-side expansion valve 6, and flows into the heat-source-side heat exchanger 3 functioning as an evaporator. During the defrosting operation, the refrigerant flowing into the heat source side heat exchanger 3 functioning as an evaporator is gasified by heat exchange with air by the operation of the blower fan 11, and is sucked into the compressor 2.
The ice maker 1 includes an evaporator E including an inner tube 12 and an outer tube 13 and an ice scraping unit described later, and is a double-tube ice maker of a horizontal type in which respective axes of the inner tube 12 and the outer tube 13 are disposed horizontally. The evaporator E is a flooded evaporator in which most of the annular space 14 between the inner tube 12 and the outer tube 13 is liquid refrigerant, and can improve the heat exchange efficiency between the refrigerant and the seawater. Further, by making most of the annular space 14 be the liquid refrigerant, the refrigerating machine oil in the flooded evaporator can be easily discharged from the flooded evaporator, and by returning the discharged refrigerating machine oil to the compressor 2, lubrication shortage of the compressor 2 can be suppressed, and reliability can be improved.
The inner pipe 12 is an element through which a cooling medium, i.e., seawater, flows, and is made of a metal material such as stainless steel or iron. The inner tube 12 is cylindrical and is disposed inside the outer tube 13. Both ends of the inner tube 12 are closed, and an ice scraping portion 15 is disposed inside the inner tube, wherein the ice scraping portion 15 scrapes and disperses an ice slurry in a fruit-dew shape generated on an inner circumferential surface of the inner tube 12 into the inner tube 12. A seawater inlet pipe 16 for supplying seawater into the inner pipe 12 is provided on one axial end side (right side in fig. 2) of the inner pipe 12, and a seawater outlet pipe 17 for discharging seawater from the inner pipe 12 is provided on the other axial end side (left side in fig. 2) of the inner pipe 12.
The outer tube 13 has a cylindrical shape and is made of a metal material such as stainless steel or iron, as in the inner tube 12. A plurality of (three in the illustrated example) refrigerant inlet pipes 18 are provided at a lower portion of the outer pipe 13, and a plurality of (two in the illustrated example) refrigerant outlet pipes 19 are provided at an upper portion of the outer pipe 13. A refrigerant supply port 20 for supplying refrigerant into the annular space 14 is formed at an upper end of the refrigerant inlet pipe 18, and a refrigerant discharge port 21 for discharging refrigerant in the annular space 14 is formed at a lower end of the refrigerant outlet pipe 19.
As shown in fig. 2 to 3, the ice scraping unit 15 includes a rotary shaft 22, a support rod 23, a blade 24, and a motor 26. The other end of the shaft 22 in the axial direction is provided to extend outward from a flange 25 provided at the other end of the inner tube 12 in the axial direction, and is connected to a motor 26 constituting a driving section for driving the shaft 22. The motor 26 includes an ammeter 31, and the drive current of the motor 26 detected by the ammeter 31 is sent to the control device 30. Support rods 23 are erected on the circumferential surface of the rotating shaft 22 at predetermined intervals, and blades 24 are attached to the tips of the support rods 23. The vane 24 is formed of a band-plate-like member made of, for example, synthetic resin, and the side edge on the front side in the rotational direction thereof is tapered.
A refrigerant path from a refrigerant supply port 20 formed in a lower portion of the outer tube 13 to a refrigerant discharge port 21 formed in an upper portion of the outer tube 13 is formed by an annular space 14 formed between an outer peripheral surface of the inner tube 12 and an inner peripheral surface of the outer tube 13.
[ operation control method ]
Next, a method of controlling the operation of the ice maker 1 in the ice making system a will be described. More specifically, an operation control method for changing, stopping, or restarting the operation condition of the ice maker 1 according to the ice filling rate in the seawater tank 9 will be described.
< first embodiment >
In the ice making system a, when the ice filling rate IPF in the seawater tank 9 increases due to the operation of the ice making machine 1, the amount of ice discharged from the seawater tank 9 increases, and along with this, the amount of ice in the inner pipe 12 of the ice making machine 1 also increases. When the amount of ice in the inner tube 12 increases, the driving torque of the motor 26 of the ice scraping portion 15 that scrapes the dew-like ice slurry generated on the inner circumferential surface of the inner tube 12 increases, and the driving current of the motor 26 increases. In the first embodiment, the drive current value of the motor 26 of the ice scraping unit 15 is detected by the ammeter 31, and the operation of the ice maker 1 is controlled by the current value sent from the ammeter 31 to the control device 30.
As described above, when the ice filling rate IPF of the seawater in the seawater tank 9 is increased and the ice is excessively stored in the seawater tank 9, the seawater containing a large amount of ice flows into the ice maker 1, and the current value of the motor 26 of the ice scraping portion 15 is increased as compared with the conventional value. In the first embodiment, when the current of the motor 26 exceeds the first current value, the evaporation temperature of the refrigerant supplied to the ice maker 1 is increased.
Fig. 4 is a diagram showing an example of control of the evaporation temperature in the operation control method according to the first embodiment. In fig. 4, the ordinate represents the magnification of the evaporation temperature of the refrigerant in the evaporator E, and represents the ratio to the normal evaporation temperature described later. In this control example, the evaporation temperature was set to a normal set temperature t0 (e.g., -15 ℃) until the current value detected by the ammeter 31 reached 6A. In the present embodiment, when the current value exceeds 6A, which is the first current value, the evaporation temperature of the refrigerant supplied to the evaporator E is increased. More specifically, in the present embodiment, the evaporation temperature is set higher in stages according to the amount of excess current. For example, if the current value exceeds 6A and is within 7A, the operation control is performed so that the evaporation temperature becomes 0.9 times the normal evaporation temperature t0, and if the current value further exceeds 7A and is within 8A, the operation control is performed so that the evaporation temperature becomes 0.8 times the normal evaporation temperature t 0. In this way, by setting the evaporation temperature higher than that in the normal time according to the rise of the current value, the ice making amount of the ice maker 1 is reduced.
In the present embodiment, when the current value further increases and exceeds a second current value (11A in the present example) larger than the first current value, the forced heat shutoff is performed to stop the operation of the ice maker 1. That is, the operation of the compressor 2 is stopped to stop the circulation of the refrigerant in the refrigerant circuit. In addition, even at the time of the forced heat-off, the operation of the ice scraping portion 15 is continued. After the forcible heat shutoff, the forcible heat shutoff is released and the operation of the compressor 2 is resumed at a timing when the current value of the motor 26 is reduced to a predetermined value, for example, 9A.
Fig. 5 is a graph illustrating characteristics of a current value in a case where the operation control of the first embodiment is performed and a case where the operation control is not performed (conventional technique). In fig. 5, the horizontal axis represents time (t), and the vertical axis represents the current value (a) of the motor 26 of the ice scraping unit 15.
In the conventional technique, since the operation control is not performed, if the ice filling rate IPF increases with the lapse of time and the amount of ice in the inner tube 12 becomes a certain amount or more, the drive current of the motor 26 rapidly increases. When the drive current exceeds a predetermined value a1, the overcurrent protection device operates, and the operation of the motor 26 is stopped. In this case, since the motor 26 is continuously operated in a high torque state before the operation of the motor 26 is stopped, the blade 24, the support rod 23, and the like of the ice scraping portion 15 may be damaged.
On the other hand, in the operation control of the first embodiment, the current value of the motor 26 until the time t1 when the amount of ice in the inner tube 12 reaches the predetermined amount is the same as in the conventional art, but when the time t1 elapses, the current value of the motor 26 gradually increases. However, as described above, the ice making amount is reduced by setting the evaporation temperature higher than that in the normal case according to the increase in the current value, and therefore, the increase in the current value is gentle compared to the related art.
After that, when the current value of the motor 26 exceeds the second current value, that is, 11A at time t2, the forced thermal shutdown is performed, and the operation of the ice maker 1 is stopped. Accordingly, no new ice is generated regardless of whether or not the ice slurry in the seawater vessel 9 is used, and therefore, the amount of ice in the inner pipe 12 gradually decreases, and the drive current of the motor 26 gradually decreases. When the current value of the motor 26 reaches 9A or less at time t3, the forced thermal shutdown is released, and the operation of the ice maker 1 is restarted. When the ice amount in the inner tube 12 increases again and the current value of the motor 26 exceeds 11A at time t4 after the operation of the ice maker 1 is restarted, the forced thermal shutdown is performed again, and the operation of the ice maker 1 is stopped.
In the present embodiment, the operation of the ice maker 1 is controlled according to the current value of the motor 26 of the ice scraping unit 15 of the ice maker 1, which is an element on the machine side. Therefore, the reliability of the operation control of the ice maker 1 can be improved regardless of the occurrence of a problem such as a communication abnormality with the appliance side as in the related art. This can further reduce the risk of damage to the blades 24 and the support rods 23 of the ice scraping section 15 due to excessive ice making, and can improve the reliability of the ice making system a as a system.
In the present embodiment, the evaporation temperature is increased stepwise according to the amount by which the current exceeds the first current value, and thus ice production by the ice maker 1 can be suppressed stepwise.
< second embodiment >
In the present embodiment, the operation control of the ice maker 1 is performed focusing on the point that the pressure loss of the seawater moving from the inlet portion to the outlet portion in the inner pipe 12 increases as the amount of ice in the inner pipe 12 of the ice maker 1 increases. Specifically, in the present embodiment, when the pressure difference between the pressure at the inlet of the seawater (cooled medium) of ice maker 1 and the pressure at the outlet of ice maker 1 exceeds the first pressure value, the evaporation temperature of the refrigerant supplied to ice maker 1 is increased. In the second embodiment, the pressure of the seawater in the seawater inlet pipe 16 and the seawater outlet pipe 17 of the ice maker 1 is detected by the pressure sensor 32 and the pressure sensor 33 (see fig. 2), respectively, and the operation of the ice maker 1 is controlled by the pressure values sent from the pressure sensors 32 and 33 to the control device 30.
Fig. 6 is a diagram showing an example of control of the evaporation temperature in the operation control method according to the second embodiment. In fig. 6, the ordinate represents the magnification of the evaporation temperature of the refrigerant in the evaporator E, and represents the ratio to the normal evaporation temperature described later. In this control example, the evaporation temperature was set to a normal set temperature t0 (e.g., -15 ℃) until the pressure difference between the pressure of the seawater in the seawater inlet pipe 16 detected by the pressure sensor 32 and the pressure of the seawater in the seawater outlet pipe 17 detected by the pressure sensor 33 reached 0.03 MPa. In the present embodiment, if the pressure difference exceeds 0.03MPa, which is the first pressure value, the evaporation temperature of the refrigerant supplied to the evaporator E is increased. More specifically, in the present embodiment, the evaporation temperature is set higher in stages in accordance with the excess of the pressure difference. For example, if the pressure difference exceeds 0.03MPa and is in the range of 0.04MPa or less, the operation control is performed so that the evaporation temperature becomes 0.9 times the ordinary evaporation temperature t0, and if the pressure difference further exceeds 0.04MPa and is in the range of 0.05MPa or less, the operation control is performed so that the evaporation temperature becomes 0.8 times the ordinary evaporation temperature t 0. In this way, the evaporation temperature is set higher than that in the normal case according to the increase in the pressure difference, and the ice making amount is reduced.
In the present embodiment, when the pressure difference is further increased and exceeds the second pressure value that is larger than the first pressure value, the forced thermal shutdown is performed to stop the operation of the ice maker 1. That is, the operation of the compressor 2 is stopped to stop the circulation of the refrigerant in the refrigerant circuit. In addition, even at the time of the forced heat-off, the operation of the ice scraping portion 15 is continued. After the forced thermal shutdown, the forced thermal shutdown is released and the operation of the compressor 2 is resumed when the pressure difference decreases to a predetermined value, for example, 0.06 Mpa.
In the present embodiment, the operation of the ice maker 1 is controlled by the pressure difference between the pressure of the seawater (cooled medium) in the seawater inlet pipe 16 and the pressure of the seawater in the seawater outlet pipe 17 in the ice maker 1, which is an element on the machine side. Therefore, the reliability of the operation control of the ice maker 1 can be improved regardless of the occurrence of a problem such as a communication abnormality with the appliance side as in the related art. This can further reduce the risk of damage to the blades 24 and the support rods 23 of the ice scraping section 15 due to excessive ice making, and can improve the reliability of the ice making system a as a system.
In addition, in the present embodiment, the evaporation temperature is increased step by step according to the amount by which the pressure difference exceeds the first pressure value, whereby the ice maker 1 can be suppressed from generating ice step by step.
[ other modifications ]
The present disclosure is not limited to the above embodiments, and various modifications can be made within the scope of the claims.
For example, in the above-described embodiment (first embodiment), the first current value of the motor and the second current value larger than the first current value are set to 6A and 11A, respectively, but these are merely examples, and the present disclosure is not limited to these current values. The first current value and the second current value can be appropriately selected according to the scale of the ice scraping portion, the characteristics of the motor, and the like.
Similarly, in the above-described embodiment (second embodiment), the first pressure value and the second pressure value larger than the first pressure value are set to 0.03MPa and 0.08MPa, respectively, but these are merely examples, and the present disclosure is not limited to these pressure values. The first pressure value and the second pressure value can be appropriately selected according to the scale of the ice scraping portion, the characteristics of the pump, and the like.
In the above-described embodiment (first embodiment), when the current value of the motor is decreased to 9A, the forcible thermal shutdown is released and the operation of the compressor is resumed, but the current value for releasing the forcible thermal shutdown is not limited thereto, and can be appropriately selected according to the scale of the ice scraping portion, the characteristics of the motor, and the like.
Similarly, in the above-described embodiment (second embodiment), when the pressure difference between the inlet and outlet of the ice maker is reduced to 0.06Mpa, the forcible thermal shutdown is released and the operation of the compressor is restarted, but the pressure difference for releasing the forcible thermal shutdown is not limited thereto and can be appropriately selected according to the scale of the ice scraping portion, the characteristics of the pump, and the like.
In the above embodiment, the evaporation temperature is increased stepwise in accordance with the amount of excess of the current or the pressure difference, but the evaporation temperature may be increased linearly in accordance with the amount of excess. In the above embodiment, the evaporation temperature is increased stepwise in accordance with the amount of excess of the current or the pressure difference, but the evaporation temperature may be increased by a preset temperature when the current or the pressure difference exceeds the first current value or the first pressure value.
In the above-described embodiment (second embodiment), the pressure sensor 32 for detecting the pressure of the seawater at the inlet of the ice maker 1 is provided in the seawater inlet pipe 16, but the pressure sensor 32 may be provided at a portion S1 (inside the inner pipe 12) shown by a two-dot chain line in fig. 2, for example, as long as it can detect the pressure of the seawater before heat exchange with the refrigerant in the evaporator E. The same applies to the pressure sensor 33 for detecting the pressure of the seawater at the outlet of the ice maker 1, and the pressure sensor 33 may be provided at a location S2 (inside the inner tube 12) indicated by a two-dot chain line in fig. 2, for example.
In the above embodiment, the flooded evaporator in which most of the annular space 14 between the inner tube 12 and the outer tube 13 is liquid refrigerant was exemplified as the evaporator E, but an evaporator of a type in which refrigerant is discharged into the annular space 14 between the inner tube 12 and the outer tube 13 through a nozzle may be provided.
Description of the symbols
1: ice making machine
2: compressor with a compressor housing having a plurality of compressor blades
3: heat source side heat exchanger
4: four-way reversing valve
5: using side expansion valves
6: heat source side expansion valve
7: superheater
8: storage tank
9: seawater container
10: pump and method of operating the same
11: air supply fan
12: inner pipe
13: outer tube
14: annular space
15: ice scraping part
16: seawater inlet pipe
17: seawater outlet pipe
18: refrigerant inlet pipe
19: refrigerant outlet pipe
20: refrigerant supply port
21: refrigerant discharge port
22: rotating shaft
23: support rod
24: blade
25: flange
26: motor with a stator having a stator core
30: control device
31: current meter
32: pressure sensor
33: pressure sensor
A: ice making system
E: an evaporator.
Claims (6)
1. A method for controlling the operation of an ice maker (1), in which ice maker (1) cools a medium to be cooled so as to exchange heat with a refrigerant to generate ice, characterized in that,
when the drive current of an ice scraping part (15) of the ice maker (1) exceeds a first current value, the evaporation temperature of the refrigerant supplied to the ice maker (1) is increased.
2. The operation control method according to claim 1,
the evaporation temperature is increased stepwise according to the excess amount of the current.
3. The operation control method according to claim 1 or 2,
when the drive current exceeds a second current value that is larger than the first current value, the operation of the ice maker (1) is stopped.
4. A method for controlling the operation of an ice maker (1), in which ice maker (1) cools a medium to be cooled so as to exchange heat with a refrigerant to generate ice, characterized in that,
in the case where the pressure difference between the pressure at the inlet portion and the pressure at the outlet portion of the cooled medium in the ice maker (1) exceeds a first pressure value, the evaporation temperature of the refrigerant supplied to the ice maker (1) is increased.
5. The operation control method according to claim 4,
the evaporation temperature is increased stepwise according to the excess amount of the pressure difference.
6. The operation control method according to claim 4 or 5,
and stopping the operation of the ice maker (1) when the pressure difference exceeds a second pressure value which is larger than the first pressure value.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018-245322 | 2018-12-27 | ||
| JP2018245322A JP6760361B2 (en) | 2018-12-27 | 2018-12-27 | Operation control method of ice machine |
| PCT/JP2019/033661 WO2020136997A1 (en) | 2018-12-27 | 2019-08-28 | Operation control method for ice maker |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN113227681A true CN113227681A (en) | 2021-08-06 |
Family
ID=71127091
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201980085900.1A Pending CN113227681A (en) | 2018-12-27 | 2019-08-28 | Method for controlling operation of ice maker |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20220057130A1 (en) |
| EP (1) | EP3904789B1 (en) |
| JP (1) | JP6760361B2 (en) |
| CN (1) | CN113227681A (en) |
| WO (1) | WO2020136997A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2024041230A1 (en) * | 2022-08-23 | 2024-02-29 | 广东美的白色家电技术创新中心有限公司 | Ice making module and ice making apparatus |
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Also Published As
| Publication number | Publication date |
|---|---|
| EP3904789A4 (en) | 2022-03-09 |
| EP3904789B1 (en) | 2023-04-26 |
| WO2020136997A1 (en) | 2020-07-02 |
| EP3904789A1 (en) | 2021-11-03 |
| JP6760361B2 (en) | 2020-09-23 |
| US20220057130A1 (en) | 2022-02-24 |
| JP2020106212A (en) | 2020-07-09 |
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