WO2014160310A1 - Closed loop ice slurry refrigeration system - Google Patents
Closed loop ice slurry refrigeration system Download PDFInfo
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- WO2014160310A1 WO2014160310A1 PCT/US2014/026290 US2014026290W WO2014160310A1 WO 2014160310 A1 WO2014160310 A1 WO 2014160310A1 US 2014026290 W US2014026290 W US 2014026290W WO 2014160310 A1 WO2014160310 A1 WO 2014160310A1
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- WIPO (PCT)
- Prior art keywords
- ice
- storage device
- ice slurry
- slurry mixture
- heat load
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Classifications
-
- 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
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D17/00—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces
- F25D17/02—Arrangements for circulating cooling fluids; Arrangements for circulating gas, e.g. air, within refrigerated spaces for circulating liquids, e.g. brine
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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
Definitions
- the present disclosure relates to a new and improved closed loop refrigeration system using ice slurries.
- Refrigeration systems are commonly used to cool an air space, cool equipment, and to keep food or perishables at chilled temperatures.
- Conventional refrigeration systems typically consist of three components: a compressor, a condenser and an evaporator, as well as various piping, valves and controls that connect all the components. These components work together to cycle a refrigerant through the refrigeration system.
- the compressor compresses the refrigerant so that it turns from gas to liquid at a relatively high temperature.
- the condenser then transfers this heat to the atmosphere.
- the resulting cold liquid refrigerant is then sent to the evaporator, which removes the heat from the cabinet or space by turning the liquid refrigerant into a gas. That refrigerant gas is returned to the compressor and the refrigeration cycle is repeated.
- Such methods further include feeding the aqueous liquid-ice mixture from the freeze exchanger to an ice storage tank to provide an ice slurry and aqueous liquid therein, and removing cold aqueous liquid from the ice storage tank for feeding through a heat exchanger in indirect heat exchange with a fluid to be cooled and used for cooling purposes, with the now warmed aqueous liquid exiting from the heat exchanger and returning to the ice storage tank to be cooled by contact with the ice therein.
- An ice slurry mixture means "a phase changing refrigerant.”
- a multicomponent ice slurry mixture means "a phase changing refrigerant including micro-crystals formed and suspended within a solution of water and a freezing point depressant.” Slurry ice has greater heat absorption compared with single phase refrigerants because the melting enthalpy (latent heat) of the ice is also used.
- a freezing point depressant means “a solute to water which decreases the freezing point of the water, such as ethylene glycol, propylene glycol, various alcohols (Isobutyl, ethanol), salts (CaCl 2 , NaCl) and sugar (sucrose, glucose)."
- a closed loop refrigeration system means "a refrigeration system in which the coolant may be recycled continuously.”
- a heat load means "the amount of heat entering the area to be controlled by the refrigeration system.”
- An agitator means an apparatus for mixing a liquid or liquid solid mixture.
- a closed loop refrigeration system comprises an ice slurry mixture which comprises ice, water, and a freezing point depressant.
- the system also comprises a first storage device for storing the ice slurry mixture, and an agitator disposed in the first storage device. The agitator agitates the ice slurry mixture in at least an intermittent manner.
- the system further comprises a first conduit connecting the first storage device and a heat load, and a first pump disposed on the first conduit for pumping the ice slurry mixture through the first conduit from the first storage device to the heat load. At least some of the ice melts in the heat load.
- the system also comprises a second conduit connecting the heat load and a second storage device. The second storage device is connected to the first storage device.
- the system further comprises a second pump disposed on the second conduit for pumping the ice slurry mixture containing the melted ice through the second conduit from the heat load to the second storage device.
- a closed loop refrigeration system comprises an ice slurry mixture which comprises about 5 - 60% ice, about 20 - 95% water, and about 0- 50 % a freezing point depressant.
- the system also comprises a first storage device for storing the ice slurry mixture, and an agitator disposed in the first storage device. The agitator agitates the ice slurry mixture in at least an intermittent manner.
- the system further comprises a heat load, a first transporter for transporting the ice slurry mixture from the first storage device to the heat load, and a second transporter for transporting the ice slurry mixture from the heat load to a second storage device.
- the second storage device is connected to the first storage device.
- a method comprises providing an ice slurry mixture comprising about 5 - 60% ice, about 20 - 95% water, and about 0 - 50 % a freezing point depressant in a first storage device, and agitating the ice slurry mixture stored in the first storage device in at least an intermittent manner.
- the method also comprises pumping the ice slurry mixture through a first conduit from the first storage device to a heat load. At least some of the ice melts in the heat load.
- the method also comprises pumping the ice slurry mixture containing the melted ice through a second conduit from the heat load to a second storage device.
- Figure 1 shows a system schematic of a preferred embodiment of a configuration of a closed loop refrigeration system operating in accord with the present invention during off peak power consumption hours.
- Figure 2 shows a system schematic of a preferred embodiment of a configuration of a closed loop refrigeration system operating in accord with the present invention during peak power consumption hours.
- Figures 3 a-b show cross sectional views of a standard elbow and a lead in chamfer el bow, respectively, with the chamfered lead in reducing steps in the ID size of the flow path for a conduit section in accord with the present invention.
- Figure 4 shows a system schematic of another preferred embodiment of a configuration of a closed loop refrigeration system operating in accord with the present invention during peak power consumption hours.
- Figure 5 shows a system schematic of a preferred embodiment of a configuration of a closed loop refrigeration system operating in accord with the present invention during off peak power consumption hours.
- Figure 6 shows an example thermocouple engagement for monitoring operation of a section of conduit during operation in accord with the present invention.
- Typical known refrigerants include water, ice, hydrocarbons, propane, butane, ammonia, chlorofluorocarbons, freon, hydrochlorofluorocarbon, hydrofluorocarbon, methyl formate, methyl chloride, sulfur dioxide, etc.
- Some of these refrigerants such as water and ice were found to be problematic, in part because ice tends to agglomerate and clog the refrigeration system. Furthermore, ice refrigeration systems can be quite expensive.
- a secondary loop refrigeration system has two refrigeration circuits: a primary refrigeration circuit and a secondary refrigeration circuit. Consequently, a secondary loop refrigeration system incorporates two different refrigerants to provide cooling: a primary refrigerant in the primary refrigeration circuit and a secondary refrigerant in the secondary refrigeration circuit.
- a secondary loop refrigeration system In a secondary loop refrigeration system, one circuit is used to cool the other circuit (which is used to cool the target air space or equipment). Thus, there may be multiple compressors and heat exchangers that link the two circuits.
- the configuration of secondary loop refrigeration systems is subject to various designs as known in the art.
- the primary refrigeration circuit remains in a machine room and is used to cool the secondary refrigeration circuit (which is used to cool the target air space such as the supermarket refrigerator or industrial equipment, etc.)
- the overall volume of the refrigerant needed to cool a target space is reduced compared to a conventional refrigeration system.
- the primary refrigerant may be a synthetic or natural chemical.
- the secondary refrigerant may be water when used above its freezing point. Many cooling functions require temperatures close to or below the freezing point of water, in which case substances are added to water to lower its freezing point, much like anti-freeze in an automobile.
- Sodium chloride, calcium chloride, low carbon glycols, such as ethylene glycol, propylene glycol, butylene glycol and polyglycols thereof, and alcohol are all examples of freezing point depressants that can be used in circulating water-based cooling solutions.
- salt solutions can be corrosive and glycol solutions may have increased viscosity if the concentration of glycol is high.
- Carbon dioxide can also be used as a secondary refrigerant.
- carbon dioxide systems operate at higher pressures than other refrigerants, which demands special piping and fittings.
- Brine (salt-based) or water solution refrigerants in secondary loop systems operate at relatively low pressures, but still require substantial pumps, valves and piping.
- Figure 1 shows a closed loop refrigeration system 1 0 according to one embodiment of the present invention that uses an ice slurry which comprises ice, water and propylene glycol. There is also present an ice slurry generator o r i c e m ake r l 2 for generating the ice slurry.
- a storage device 14 is provided for storing the ice slurry.
- the storage device includes an agitator 1 6 that agitates the ice slurry in an intermittent matter to prevent agglomeration. The agitation of the slurry can be further aided by the use of a mixer 18 which is also used to receive slurry supply from the storage device 14 for mixing with warmer ice slurry returning from the heat load 26.
- a peristaltic pump 20 is used to pump the ice slurry from the ice slurry generator along a first conduit 22 to the storage device and/or along a second conduit 24 to a heat load 26. At least some of the ice melts in the heat load.
- a vibration motor (n ot sh own ) is used for vibrating said first and/or second conduit to help prevent the ice from agglomerating.
- a second pump 28 is used to pump the ice slurry from the heat load (thus containing melted ice) along a third conduit 30 to the ice slurry generator for regenerating the ice slurry in mixer 18 or in melt storage device 32, depending upon the system demands (e.g., heat load 26 demands or whether operation is occurring peak electricity hours).
- an embodiment of the present invention provides for interruption, decrease or stoppage of the ice maker 12 to accommodate for load demands (e.g., to decrease ice maker usage during more expensive electricity hours).
- the continuing generation of the ice slurry is provided by the extra ice slurry previously generated and stored in the storage device 14, which is combined with the warmed ice slurry returning from the heat load 26.
- the closed loop configurations system can maintain a ice slurry supply for heat load 26 in the absence of the constant operation of ice maker 12.
- this operation will also permit a reduced, as opposed to a stopped operation of the ice make 12 so as to lessen (rather than stopping) the draw of electricity during peak hours.
- This closed loop refrigeration system can be employed in a secondary loop refrigeration system as the secondary circuit.
- the various elements of the embodiments of the invention will be described in more detail below.
- Ice slurries are a type of phase change material that can transfer heat.
- a phase change occurs when ice melts, water boils or wax melts. Ittakes energy to cause such a change, called the heat of fusion or the heat of vaporization.
- 144 BTU/lb is required to melt ice as compared to 1 BTU/lb per degree Fahrenheit of so-called sensible heat for water.
- Sensible heat is the amount of heat that is added or lost by a substance due to a change in temperature.
- ice has a superior thermal capacity compared to water.
- ice in the form of an ice slurry can be circulated through a refrigeration system.
- the ice slurry comprises small, smooth ice crystals that are capable of flowing in a slurry through very small tubes; otherwise, it will aggregate easily and prevent circulation at high ice loading.
- Acceptable ice slurries include those described in U.S. Patent Nos.6,244,052;
- Ice slurries may also be generated using any conventional ice slurry generator known in the art, including the Lanikai frozen drink machine or other scraped surface heat exchangers..
- Ice slurries used in one embodiment of the present invention comprise a mixture of ice, water and propylene glycol.
- ice can be present in an amount up to 60% (e.g., ice loadings of 20-30%, 30- 40%, 40-50%, 50-60%, etc.).
- propylene glycol can be present in an amount up to 50%, and preferably no more than 50% or whatever is the eutectic composition of the freezing point depressdant. (The eutectic point is that temperature and composition at which a mixture freezes without separation into two phases.)
- water is present in the remaining amount (e.g., 40%, 50%, 60%, etc.).
- the ice is first formed as small, smooth crystals and stored as a concentrated slurry (e.g., 40-60%) ice loading) that is too thick to circulate by itself.
- a concentrated slurry e.g. 40-60% ice loading
- the stored concentrated ice slurry is diluted to about 20-30 % ice loading at the appropriate temperature by mixing with another medium (e.g., a return melted slurry).
- an ice slurry refrigerant in a secondary loop system has lower capital, maintenance and operating costs than does a brine or carbon dioxide system.
- the concentrated ice slurry is stored in a storage device 14, which may be any conventional storage container known in the art.
- the storage device includes an agitator 16, which can be any conventional mixing device known in the art. During storage, intermittent gentle agitation is applied to prevent aggregation of ice crystals.
- a peristaltic pump 20 can be used to pump the ice slurry from the ice slurry generator along a first conduit 22 to the storage device.
- a peristaltic pump or progressing cavity pump 28 can also be used to pump the ice slurry along a second conduit to a heat load. It has been discovered that the "pulsing" action of peristaltic pump (as opposed to a centrifugal pump) helps to prevent the ice in the ice slurries from aggregating and clogging the conduits.
- the heat load represents any device in which the target air space is being cooled (e.g. , refrigerator or jacketed vessel, etc.). At least some of the ice in the ice slurry will melt in the heat load.
- Any conventional pumps known in the art can be used to pump the ice slurry from the heat load (thus containing melted ice) along a third conduit to the ice slurry generator for regenerating the ice slurry.
- the advantage of reduction in energy when using the embodiments of the present invention can be realized by operating the disclosed technology in different modes (i.e., by coordinating the power requirements of the refrigeration system with the different electricity rates charged during the day and night).
- the power requirements of the refrigeration system can be operated in accordance with the daily fluctuations in energy prices (i.e., off peak vs. peak rates).
- Making ice is one way to store the cold temperature and is used in ice-making units, where water is typically frozen around metal coils filled with refrigerant. The cold temperature is recovered when needed by circulating water past the coils, melting the ice and cooling the water, which then circulates as a heat transfer medium to where it is needed (i.e., air coolers, heat exchangers or process chillers).
- ice slush was straight from a Lanikai machine 12. Ice slurry was processed with the intent to increase the ability to flow and be pumped. ID: inside diameter. OD: outside diameter.
- Setup includes a Lanikai frozen drink machine; a MasterFlex peristaltic pump; an Electric drill, 0-550RPM; Variac; a tile saw pump; a heated water bath; Coleman coolers (2); thermocouples, T type, Omega 5TC-TT-T-36-72 (8); a measurement computing USB -Temp ID:02; a digital thermometer, Digisense ID:428763; a graduated cylinder; a stopwatch; a stir rod; and a paint mixer.
- An aqueous solution of a freezing point depressant, such as propylene glycol is mixed in a large container.
- a Lanikai is filled with the mixed solution until there is approximately 1 cm of standing solution in the Lanikai holding tank.
- the fill pump fills the holding tank up to the proper level. All three tubes are set in the peristaltic pump heads. The smaller diameter tubing should be on a separate pump from the two larger tubes.
- the mixed output tube is directed at the heat exchanger cooler and the pure ice is sent to the ice storage cooler.
- the heat exchanger cooler is filled with solution and the circulation pump is turned on.
- the heat load source is then turned on and the load pump is heated. Subsequently, the Lanikai output valve is opened and all peristaltic pumps are turned on and control knobs adjusted to desired settings.
- the tubing from the head #2 (the tubing going to ice storage) on peristaltic pump # 1 is removed. Head # 1 is kept intact. The tubing in ice storage is moved to a location it will not touch the mixer, but is adequate enough to extract uniform slurry. The output nozzle on Lanikai faceplate is closed. The direction of peristaltic pump # 1 is reversed, and the flow of peristaltic pump #2 is readjusted to desired thickness.
- the closed loop slurry system requires a controlled flow of ice slush throughout the system.
- Initial experiments were performed to evaluate different methods of ice slush flow control from the Lanikai frozen drink machine. The following experiments were performed with a 10% by volume concentration solution of propylene glycol mixed with tap water.
- the Lanikai machine features a main valve on the front face plate that allows dispensing of the ice slush.
- the main valve consists of a sliding cylinder sealed by o-rings that can be infinitely adjusted between fully open and fully closed. When fully opened, the diameter of the orifice is approximately 1" in diameter.
- the valve position that generates approximately 300 mL/min output flow was found to jam and stop flowing after approximately 2-3 minutes of flow at 300 mL/min through the orifice. The flow rate was found to gradually decrease until flow became essentially zero or 'jammed".
- the ice slush just inside the outlet of the Lanikai is visible due to the clear front plate.
- the ice slush visually appeared to be a high concentration of ice which likely caused the stoppage of flow or an "ice jam".
- the flow can be restarted by opening the valve and in effect creating a larger orifice.
- the opening below the main valve on the front plate of the Lanikai can be fitted with a section of 1" ID rigid tubing, bonded to the opening and then connected to a piece of 1 " ID flexible tubing. Placing the flexible over the rigid tubing is intended to increase the ability of the ice slush to flow by eliminating the step which would otherwise be created when using certain standard fluid fitting connectors.
- Flow through the flexible tubing can be controlled by varying the height of the opening and overall length of the tube relative to the Lanikai and therefore varying the static fluidic pressure differential and amount of friction.
- a vibrator motor was connected to the flexible tubing to vibrate the ice slush along the tubing.
- the vibration was found to have two effects: both to increase the flow rate and to increase the consistency of the output flow rate over time.
- the Lanikai machine with a flexible tube was connected and coupled to a vibrator motor as described above
- the closed loop system requires controlled flow of ice slush at various locations. Depending on the final closed loop configuration . changing the relative height of the ice slush output may not always be feasible or easily controlled.
- the ice slush flow can be controlled by connecting a peristaltic pump to the outlet spout of the Lanikai faceplate and then fully opening the main valve on the Lanikai.
- a MasterFlex peristaltic pump (7523-10 drive with 75 18- 00 head) with W OO x 0.375" ID (McMaster 5554K 16) was connected to the outlet of the Lanikai via a if' push to connect fitting (McMaster 51055 22) and run continuously for over an hour successfully.
- the output of the Lanikai was connected to the peristaltic pump via the Yi" tubing and a push to connect connector.
- Ice slush flow can also be controlled using a rotating auger similar to a setup found in a food processing feeder bin.
- An auger drive system was prototyped and evaluated experimentally by driving the 1 " x 17" auger drill bit (Menards 2423429) inside a section of 1 " ID rigid PVC tubing (McMaster 49035K25). With approximately 60% ice concentration, the ice flow can be controlled by varying the rotation speed of the auger down to zero RPM which corresponds to zero mL/min. If ice concentration drops below a critical value, the ice slush can flow through the pipe even with zero auger rotation. The critical value of ice concentration is dependent in part to the location of the auger relative to the outlet spout on the Lanikai machine.
- the non-rotating auger can control ice slush flow.
- the maximum flow created by the auger is limited and is less than proportional to theoretical rate calculated by multiplying the linear speed at which the helix translates axially through the tube by the cross sectional volume of the void in the auger.
- the ice slush will be constantly mixed by the helix of the rotating auger as the ice slush translates along the tube.
- the system evaluated featured two ice slush flow control mechanisms (a driven auger and a peristaltic pump) as well as a submersible pump.
- the ice slush from the Lanikai machine was driven at
- Table 1 below shows the temperature versus time plot for the various locations during an initial closed loop evaluation from May 12, 2012 (non calibrated values reported).
- the variation in the "Out of Heat Exchanger" temperature is a result of the configuration used to refill the Lanikai reservoir.
- the submersible pump used to refill the reservoir is only turned on when the reservoir is below a minimum level.
- Flow rate of the slush into the heat exchange cooler was recorded and measured manually with a stopwatch and graduated cylinder throughout the test. Temperature was also monitored via thermocouple at various locations.At approximately data point 7500 the peristaltic pump was turned off in an attempt to create an 'ice jam' at the outlet of the Lanikai. After 20 minutes, the peristaltic pump was turned on again with no evidence of irregular ice slush flow. The heat exchanger was not fully melting the ice slush and therefore the melted slush being pumped back into the Lanikai continued to decrease in temperature.
- ice slush temperature being pumped into the heat exchanger also continued to decrease as evident by the three temperature traces (RESERVOIR, LANK CLOSE, INTO HEAT EXCH) decreasing between approximately 0 and 4500.
- the flow rate was measured 5 times and varied between 140 and 152 mL/min.
- Table 2 shows the temperatures versus time throughout the test:
- Bench testing was performed to evaluate the effect of storing ice slush overnight.
- a 48 Qt (45.4 L) size Colman cooler (Sears 8052971 1) filled with approximately half way with ice slush was stored for approximately 8 hours in the ambient lab environment.
- the cooler used incidentally had four 2" diameter holes in the cover that remained unsealed during the test and the cooler lid was also slightly propped open.
- Some kind of mild agitation will be needed to prevent icebergs from forming in the stored slush.
- using an intennittent agitation method should also be considered to prevent adding too much energy into stored ice and therefore reducing the cooling capacity.
- thermocouples placed inside the tubing at various locations.
- Figures 4 and 5 show a block diagram of the system flow path in this configuration, as well as the thermocouple location and ID numbers.
- thermocouples were placed in the following locations identified by their location in the schematics:
- This system was first run in night mode for 2 hrs 45 min, followed by day mode operation for 1 hr.
- Peristaltic Pump One was set to 100 mL/min such that the two pump heads combined were pumping 200 mL/min of ice slush from the Lanikai machine.
- the mixing drill with a rectangular mixing head was set to a slow, constant speed.
- Peristaltic Pump Two was set to 50 mL/min creating a lower ice concentration ice slurry mix flowing into the heat exchanger.
- the tubing from Head One on Peristaltic Pump One was removed to allow free ice slush flow through that segment.
- the main valve of the Lanikai was closed to prevent back flow and Peristaltic Pump Two was slowed to 30 mL/min given that the ice concentration of the ice slush in storage had decreased slightly due to melting (this was detected by an increase in thermocouple #4 temperature as well as a visual assessment of the ice slush flowing into the heat exchanger.
- the plot of Table 3 below shows the resulting temperatures from the two modes of operation.
- the ice slush temperature flowing into the heat exchanger varied between approximately -4°C and -2.6°C throughout the test. Excluding the brief period during the transition between the two modes, the ice slush temperature remained constant during the transition to day mode.
- Both a peristaltic pump and an auger drive were found to successfully control the flow of ice slush in the system. Both the peristaltic pump and auger drive appear to allow precise flow control; however, the auger requires a certain minimum ice concentration to maintain control of the flow rate. Use of the main valve or addition of a gate valve after the auger could prevent ice concentrations from dropping below the critical valve. Additionally, when an auger drive is used, the vertical distance between the auger and the ice slush distance should be considered and minimized where possible to prevent fluid separation in the ice slush along the vertical distance.
- F i gure 6 shows how a thermocouple can be inserted into a section of flexible tubing
Abstract
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Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
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JP2016502097A JP2016516171A (en) | 2013-03-14 | 2014-03-13 | Closed loop ice slurry refrigeration system |
AU2014243954A AU2014243954A1 (en) | 2013-03-14 | 2014-03-13 | Closed loop ice slurry refrigeration system |
CA2906040A CA2906040A1 (en) | 2013-03-14 | 2014-03-13 | Closed loop ice slurry refrigeration system |
EP14773455.2A EP2972020A4 (en) | 2013-03-14 | 2014-03-13 | Closed loop ice slurry refrigeration system |
BR112015022837A BR112015022837A2 (en) | 2013-03-14 | 2014-03-13 | closed-loop cooling system and method |
SG11201507530TA SG11201507530TA (en) | 2013-03-14 | 2014-03-13 | Closed loop ice slurry refrigeration system |
MX2015012761A MX2015012761A (en) | 2013-03-14 | 2014-03-13 | Closed loop ice slurry refrigeration system. |
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US201361851921P | 2013-03-14 | 2013-03-14 | |
US61/851,921 | 2013-03-14 |
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US (1) | US20150083374A1 (en) |
EP (1) | EP2972020A4 (en) |
JP (1) | JP2016516171A (en) |
AU (1) | AU2014243954A1 (en) |
BR (1) | BR112015022837A2 (en) |
CA (1) | CA2906040A1 (en) |
MX (1) | MX2015012761A (en) |
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US10578369B1 (en) * | 2018-02-23 | 2020-03-03 | United States Of America As Represented By The Secretary Of The Air Force | Thermal management using endothermic heat sink |
CN109665323B (en) * | 2018-12-07 | 2024-02-13 | 深圳市兄弟制冰系统有限公司 | Ice conveying system with low-temperature water as carrier |
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KR101135987B1 (en) * | 2009-11-25 | 2012-04-17 | 한국지역난방공사 | Ice slurry delivery system with mixing tank |
-
2014
- 2014-03-13 WO PCT/US2014/026290 patent/WO2014160310A1/en active Application Filing
- 2014-03-13 SG SG11201507530TA patent/SG11201507530TA/en unknown
- 2014-03-13 AU AU2014243954A patent/AU2014243954A1/en not_active Abandoned
- 2014-03-13 EP EP14773455.2A patent/EP2972020A4/en not_active Withdrawn
- 2014-03-13 CA CA2906040A patent/CA2906040A1/en not_active Abandoned
- 2014-03-13 MX MX2015012761A patent/MX2015012761A/en unknown
- 2014-03-13 BR BR112015022837A patent/BR112015022837A2/en not_active IP Right Cessation
- 2014-03-13 JP JP2016502097A patent/JP2016516171A/en active Pending
- 2014-03-13 US US14/209,387 patent/US20150083374A1/en not_active Abandoned
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Publication number | Priority date | Publication date | Assignee | Title |
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US10518361B2 (en) | 2014-11-21 | 2019-12-31 | Siemens Aktiengesellschaft | Method of manufacturing a component and component |
WO2016107709A1 (en) * | 2014-12-30 | 2016-07-07 | Siemens Aktiengesellschaft | Cooling apparatus for electrical equipment |
Also Published As
Publication number | Publication date |
---|---|
CA2906040A1 (en) | 2014-10-02 |
EP2972020A4 (en) | 2017-04-19 |
BR112015022837A2 (en) | 2017-07-18 |
SG11201507530TA (en) | 2015-10-29 |
AU2014243954A1 (en) | 2015-11-05 |
MX2015012761A (en) | 2016-11-25 |
JP2016516171A (en) | 2016-06-02 |
US20150083374A1 (en) | 2015-03-26 |
EP2972020A1 (en) | 2016-01-20 |
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