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WO2018150410A1 - Appareil de réfrigération du type à adsorption susceptible de dériver des températures négatives - Google Patents

Appareil de réfrigération du type à adsorption susceptible de dériver des températures négatives Download PDF

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Publication number
WO2018150410A1
WO2018150410A1 PCT/IL2017/050190 IL2017050190W WO2018150410A1 WO 2018150410 A1 WO2018150410 A1 WO 2018150410A1 IL 2017050190 W IL2017050190 W IL 2017050190W WO 2018150410 A1 WO2018150410 A1 WO 2018150410A1
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WO
WIPO (PCT)
Prior art keywords
heat
heat exchanger
heat carrier
coolant
carrier
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/IL2017/050190
Other languages
English (en)
Inventor
Andrey DOBKIN
Mikhael SITKOVSKY
Oleg GERSHOV
Ofer VEXLER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
N A M Technology Ltd
Original Assignee
N A M Technology Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by N A M Technology Ltd filed Critical N A M Technology Ltd
Priority to IL258855A priority Critical patent/IL258855B/en
Priority to PCT/IL2017/050190 priority patent/WO2018150410A1/fr
Publication of WO2018150410A1 publication Critical patent/WO2018150410A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B17/00—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type
    • F25B17/08—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type the absorbent or adsorbent being a solid, e.g. salt
    • F25B17/083—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type the absorbent or adsorbent being a solid, e.g. salt with two or more boiler-sorbers operating alternately
    • 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
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • 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
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
    • 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
    • F25D16/00—Devices using a combination of a cooling mode associated with refrigerating machinery with a cooling mode not associated with refrigerating machinery
    • 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
    • F25D23/00—General constructional features

Definitions

  • the disclosed subject matter relates to an adsorption-type refrigerating apparatus and a process of operating the apparatus to derive negative temperatures from low-grade heat.
  • the present subject matter can be embodied as a technological part of refrigerating equipment, both mobile and stationary, used in the sectors of retail industry, public catering and food production, as example.
  • the frequently utilized adsorption-type refrigerating apparatuses are driven by mortar-substances of two components: coolant and adsorbent.
  • the design of such apparatuses contains a generator, condenser, evaporator and adsorber, paired into the corresponding units: generator-condenser, evaporator-adsorber.
  • Other integral functional parts are represented by a mortar recuperative heat exchanger, gas separator and circular pump.
  • This type of apparatus contains two adsorbers, enclosed in a single compartment therein, a condenser of the coolant and a cooling chamber with an encapsulated evaporator.
  • the adsorbent layer in the above-mentioned adsorption apparatus is too thick to result in noticeable increase of the time of the operation cycle. Further restrictions on the application of this type of apparatus are explained by a twenty-four hour period of the adsorption cycle.
  • the process of deriving cold with help of a refrigerating apparatus containing an evaporator filled with methanol, adsorber filled with methanol vapors, sorbent and condenser presumes the use of pore matrix in the function of the sorbent.
  • the cycle of this type of apparatus is characterized with the following parameters: the temperature of the evaporator of 0 or 7°C, the temperature of the condenser ranging from 30 to 45°C, the temperature of desorption 85°C (See for example RU Patent no. 2,294,796 "Sorbent of methanol vapors and the process of deriving cold by utilizing a adsorption-type refrigerating apparatus", F25B 17, Published 10.03.2007).
  • Objectives of the disclosed subject matter are to increase the cooling efficiency and to simplify the design of the adsorption-type refrigerating apparatus.
  • a refrigerating apparatus capable of producing heat carrier of negative temperatures, comprising:
  • first heat exchanger unit and at least one second heat exchanger unit wherein the first unit and the second unit are enclosed within a single chamber, wherein the first and the second heat exchanger units comprises at least one tube through which heat carrier can flow from an inlet to an outlet and heat sinks made of substantially parallel layers having surfaces that are perpendicular to at least a portion of the tubes, wherein the tubes pass through the surfaces of the heat sinks;
  • an absorbent capable of reversibly entrapping a coolant is coating the at least one first heat exchanger unit;
  • the heat carrier can be of high, medium, or low temperatures and wherein the inlets of the heat exchanger units can alternately receive the heat carrier in an appropriate temperature so that when high temperature heat carrier passes through the first heat exchanger unit, said coolant escapes from the absorbent to the single chamber and condenses onto the second heat exchanger unit through which medium temperature heat carrier flows, and wherein when medium temperature heat carrier flows through the first heat exchanger unit so as to cool the absorbent and cause a pressure drop within the single chamber, and low temperature flows through the second heat exchanger unit so that the coolant boils, re-absorbed within the absorbent, and cools the heat carrier in the tube of the second heat exchanger to negative temperatures.
  • a plurality of basins made of bent portions of the surfaces adjacent to the tube are provided to said at least one second heat exchanger unit, wherein the basins are capable of accumulating the coolant in liquid state.
  • said coolant can be selected from a group of coolants such as methanol and ammonia.
  • said absorbent can be selected from a group of absorbents such as silica gel or activated carbon.
  • the heat carrier is a fluid.
  • said absorbent is a thin layer of two or three granules of silica gel.
  • a distance L between the first and the second heat exchanger units is designed to be minimal.
  • the single chamber is provided with an outlet and a valve.
  • the tube is configured with portions that are descending and portion that are ascending.
  • the tube is configured to be a plurality of substantially parallel tubes having a distributing portion that distribute the heat carrier to within the parallel tubes and a collecting portion that collects the heat carrier from the tubes.
  • a method of refrigerating a heat carrier to negative temperatures comprises: providing a module comprising at least two heat exchangers, each heat exchanger has at least one tube configured to let heat carrier flow within from an inlet to an outlet and heat sinks, wherein the module is enclosed within a single chamber; coating one of the at least two heat exchangers with an absorbent so as to form a coated heat exchanger;
  • said heat sinks are substantially parallel riffles that are positioned substantially perpendicular to the tube.
  • the method further comprises providing a plurality of basins made of bent portions of the riffles that are adjacent to the tube.
  • said coolant can be selected from a group of coolants such as methanol and ammonia.
  • said absorbent can be selected from a group of absorbents such as silica gel or activated carbon.
  • the heat carrier is a fluid.
  • said absorbent is a thin layer of two or three granules of silica gel.
  • Figure 1 depicts a design of a refrigerating module in accordance with a preferred embodiment.
  • Figure 2 depicts an enlarged cross- sectional view of the evaporator-condenser of the heat exchanger shown in Figure 1.
  • Figure 3 depicts a design of a refrigerating module in accordance with another preferred embodiment.
  • Figure 4 depicts routing of coolants in the two modules, according to Figure 1.
  • Figure 5 represents routing of coolants, according to Figure 3.
  • the apparatus has two modules, alternately operating as an evaporator-adsorber and desorber-condenser, respectively.
  • the latter are connected to systems of heating and cooling mediums preferably via a three-way spiral automatic ball valve gate, allowing heat intake and withdrawal on the respective steps of desorption and adsorption to the system of operational cold connected to the evaporator.
  • the two modules or units of heat- exchangers alternately functioning as an evaporator-absorbent and condenser- desorbent are enclosed in a minimal distance L between them and within a single chamber, wherein, the tubes of the heat-exchangers have heat sinks in the form of riffles that are made of layers of one-piece surface in each layer. The elements of the layers are placed horizontally, in parallel to each other. More than two modules can be used and more than one unit of heat exchanger can be utilized.
  • the surfaces of the heat-exchangers riffles are designed with circular bends in the areas adjoining the tubes to form basins for the liquid coolant to accumulate.
  • a process of deriving negative temperatures from low-grade heat by an adsorption-type refrigerating apparatus is an integral part of the disclosed subject matter.
  • the process stipulates the use of a solid-bodied coolant-adsorbent, wherein, methanol is used as a coolant, and adsorption takes place in the at least two independent modules consisting of a pair of heat-exchangers that act as an adsorber- desorber and evaporator-condenser, respectively. Needless to mention that more heat exchangers can be used.
  • Methanol when in the phase of adsorption of the process is subjected to pressure of about 0,007 - 0,03 bars. This approach enables boiling temperature to range from about 0°C to minus 20°C.
  • ammonia can be used as a coolant, with a pressure , when in the phase of adsorption ranges from 0,4294 to 0,04082 mPa and the temperature from 0°C to minus 50°C.
  • silica gel or activated carbon can be used as a solid-bodied adsorbent applied in a thin layer over the outer surface of the heat exchanger, which acts as an adsorber-desorber.
  • each module is designed as at least two heat exchangers, enclosed within a single pressure controlled chamber and functioning by turns as an evaporator-adsorber and condenser-desorber, the hydrodynamic resistance is minimized and the two phases of the operational cycle in each unit are joined by turns. As a result, the cooling capacity increases, the overall design of the refrigerant is simplified, and the quality of the apparatus is enhanced.
  • the alternating mode of operation of the modules when functioning in the cycles of evaporation-adsorption and condensing-desorption supports continuity of the cooling process and faultless operation of the adsoption-type refrigerating apparatus as a technological mechanism.
  • the design of the heat exchanger configured as tubes, which have single forming of heat sinks representing a one-piece surface in each layer, the elements of which are placed horizontally in parallel to each other, increases the efficiency of heat and mass transfer by a more even distribution of coolant in the apparatus. This effect is further supported by designing circular bends in the areas of riffles adjacent the tubes. This form determines an increase of the heat gradient and, correspondently, an enhancement of stability of the heat exchanger operation as well as an increase of the coefficient of heat emission.
  • Ammonia when used as a coolant, with the pressure in the operational chamber in the phase of adsorption ranging from 0,4294 to 0,04082 mPa, determines the temperature to fall in the range from 0°C to minus 50°C.
  • This approach broadens the technological span of the apparatuses, and allows using them, for example, against technological cold of the range from 0°C to minus 20°C or low-temperature cold of the range from minus 20°C to minus 50°C.
  • silica gel as a solid-bodied adsorbent in the presented process enhances both the cooling capacity and the service-time of the apparatus.
  • silica gel When applied in a thin layer of two or three granules over the outer surfaces of the heat exchanger, including the tubes and the riffles, silica gel reduces noticeably the time of the operational cycle and facilitates heat mass transfer. Similar indicators can be reached when activated coal is used as solid-bodied adsorbent.
  • the drawings included herein reflect the specific features of both the design of the adsorption-type refrigerating apparatus and the process of deriving negative temperatures.
  • FIG. 1 illustrating a design of a refrigerating module in accordance with a preferred embodiment.
  • the configuration of a refrigerating module is preferably as follows:
  • the heat exchanger 2 comprises of tube 5 having descending and ascending portions with riffles 6 through which the ascending and descending portions of the pipe 5 passes. .
  • the outer surface of the heat exchanger 2 is covered with a thin layer of an adsorbent 3 that can reversibly absorb a coolant that is presented within the chamber 1.
  • the heat exchanger 4 comprises in a similar manner tube 7, configured with ascending and descending portions that passes through riffles 8.
  • the heat exchangers are enclosed within a single chamber 1 with a partition 10, at a minimal distance L from one another.
  • the outlet branch 9 with a valve 11 fitted to it is used to form vacuum in an operational chamber 12 formed between the heat exchanges.
  • the pipe of the heat exchanger 2 has an input 13 and an output 14.
  • an outlet 16 and an inlet 15 of the heat exchanger's 4 pipe 7 are shown.
  • the directions, indicated with arrows in Figures 1, 3, 4, and 5, represent the direction of the coolant flow.
  • FIG. 2 depicting an enlarged cross- sectional view of the evaporator-condenser of the heat exchanger shown in Figure 1.
  • circular downward bends 21 are formed about the tubes .
  • the circular bends 21, designed as relatively small basins, are adjacent to the tubes 7. The size of the basins and the curvature can be determined according to need.
  • Heat exchanger 2 now comprises a plurality of pipes 5 having a distributor 19 and a collector 20 that are connected to an inlet 13 and outlet 14, respectively.
  • the second heat exchange 4 comprises a plurality of pipes 7 and an inlet 15 fluidically connected to a distributer 18 that is connected to the plurality of pipes on one side and a collector 17 that collects the fluids from the pipes 7 and is connected to an outlet 17.
  • Collectors and distributers 17, 18, 19, and 20 are functional parts of the design that form uniform flow heat exchangers.
  • Both heat exchangers 2 and 4 are provided with riffles 6 and 8, respectively, that are placed vertically relative to the pipes 5 and 7, respectively. Other portions of the system are the same as previously disclosed.
  • hot heat-carrier is discharged from the source of low-grade heat into the tubes 5 of the heat-exchanger 2 via the inlet 13.
  • Hot air, steam, waste gas etc. can be the sources of low-grade heat and the heat carrier is preferably an aqueous solution of ethylene glycol.
  • the heat-carrier heats the thin layer of adsorbent 3 that is located on the outer surfaces of the tubes 5 and the riffles 6 and is saturated with the coolant (methanol, in this case). As a result, the coolant is heated and escapes the adsorbent as vapor that flows within the single chamber 1.
  • the tube 7 of the heat exchanger 4 is fed with the medium-heated heat-carrier via the inlet 15. This heat-carrier cools down the tubes 7 and the riffles 8, wherein, the coolant, which evaporated from the heat-exchanger 2, starts condensing onto heat exchanger 4. The first phase finishes once the coolant is fully condensed.
  • the three-way ball valve gate (not shown in the figures) switches to let the medium-heated heat-carrier pass through the tube 5 of the heat-exchanger 2, which cools down the layer of the adsorbent 3. This process results in the latter adsorbing the vapor of the coolant in the operational chamber 12, and by turn in dropping the pressure in the chamber.
  • the tube 7 of the heat-exchanger 4 are fed with the low-heat heat-carrier, which causes the coolant to boil and evaporate in the low pressure and temperature.
  • the low-heat heat-carrier in tube 7 cools down, as a result, to negative temperatures.
  • the circular bends 21 are configured to provide the increase of the temperature gradient and intensification of the heat mass transfer, resulting in enhanced refrigerating capacity of the apparatus.
  • Phase 2 finishes with substantially all the coolant adsorbed by the adsorber 3.
  • the inlet and outlet 13 and 14 of Module 1 are connected to the hot heat-carrier (HT)
  • the inlet and outlet 15 and 16 of Module 1 are connected to the medium-heat heat-carrier
  • the inlet and outlet 13 and 14 of Module 2 are connected to the medium-heat heat-carrier (MT)
  • the inlet and outlet 15 and 16 of Module 2 are connected to the low-heat heat-carrier (LT).
  • module 1 is connected as module 2, and module 2 as module 1.
  • the technological parameters of the adsorption-type refrigerating apparatus are controlled by increasing the temperature of the hot heat-carrier and decreasing the temperature of the medium-heat heat-carrier. This approach enhances refrigerating capacity of the adsorption-type apparatus and lowers the temperature, produced in the system of the low-heat heat-carrier.
  • control of the adsorption-type apparatus can be performed by varying the intensity of the heat-carriers discharge in the three systems.
  • the design of the adsorption-type refrigerating apparatus can be realized with varied spatial location of the inlets and outlets of the heat-exchangers, as show in Figure 1 and 3.
  • An adsorption-type refrigerating apparatus of cooling capacity of 7 kW was designed and built in accordance with the description herein.
  • Water-based ethylene glycol solution (40%) of temperature of about 70°C was used as a primary source of low-grade heat.
  • the solution was discharged into the heat exchanger of Module 1, wherein, the outer surface was coated with 2-4 mm thick of silica gel granules.
  • Dehydrated methanol was utilized as a coolant that is initially adsorbed within the silica gel coating.
  • Ethylene glycol aqueous solution was utilized also as the medium-heat carrier, which was cooled down in the outer heat-exchanger with forced air cooling up to temperature of about 32-34 °C.
  • the low-temperature heat carrier was cooled down to the temperature of substantially minus 8-9°C, providing, thereby, high cooling capacity of the present design of the adsorption-type refrigerating apparatus.
  • This embodiment has proved to be a highly effective energy-saving technological apparatus.
  • the important feature of the disclosed adsorption-type refrigerating apparatus is absence of any shifting or moving parts or those, connected by any actuating mechanisms. This approach simplifies the design of the apparatus, increases its reliability, and facilitates maintenance.
  • the prospective way of utilization of the present type of an apparatus is disclosed in effective derivation of technological cold with temperatures from minus 5 to minus 20°C.
  • the highest efficiency of utilizing of the present type of an apparatus is considered to be gained when installed within mobile refrigerators, or either sea or river vessels.
  • the embodiment of the present invention within a mobile refrigerator may save up to 7 - 8 liters of diesel for every 100 kilometers.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Sorption Type Refrigeration Machines (AREA)
  • Greenhouses (AREA)

Abstract

L'invention concerne un appareil et un procédé de réfrigération susceptibles de produire un caloporteur à températures négatives. L'appareil comprend au moins une première unité d'échangeur de chaleur et au moins une seconde unité d'échangeur de chaleur, les unités étant enfermées à l'intérieur d'une seule chambre et les unités comprenant au moins un tube à travers lequel un caloporteur peut circuler d'une entrée à une sortie et des dissipateurs thermiques constitués de couches sensiblement parallèles ayant des surfaces qui sont perpendiculaires à au moins une partie des tubes et les tubes passent à travers les surfaces des dissipateurs thermiques. L'appareil comprend en outre un absorbant apte à piéger de manière réversible un fluide de refroidissement qui est le revêtement de la première unité d'échangeur de chaleur, le caloporteur pouvant être de haute, moyenne ou basse température et les entrées des unités d'échangeur de chaleur pouvant recevoir en alternance le caloporteur à une température appropriée.
PCT/IL2017/050190 2017-02-14 2017-02-14 Appareil de réfrigération du type à adsorption susceptible de dériver des températures négatives Ceased WO2018150410A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
IL258855A IL258855B (en) 2017-02-14 2017-02-14 Adsorption-type refrigerating apparatus capable of deriving negative temperatures
PCT/IL2017/050190 WO2018150410A1 (fr) 2017-02-14 2017-02-14 Appareil de réfrigération du type à adsorption susceptible de dériver des températures négatives

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/IL2017/050190 WO2018150410A1 (fr) 2017-02-14 2017-02-14 Appareil de réfrigération du type à adsorption susceptible de dériver des températures négatives

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WO2018150410A1 true WO2018150410A1 (fr) 2018-08-23

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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0455184A1 (fr) * 1990-04-28 1991-11-06 Rud. Otto Meyer Procédé de chauffage et/ou refroidissement d'un bâtiment par l'énergie solaire avec utilisation d'une isolation transparente et installation utilisant ce procédé
US20060000231A1 (en) * 2002-09-11 2006-01-05 Ziquan Zhao Multifunctional constant temperature refrigerator with thermal carriers
US20120000628A1 (en) * 2010-07-01 2012-01-05 Abb Technology Ag Method for function monitoring and/or control of a cooling system, and a corresponding cooling system
US20130105117A1 (en) * 2010-07-26 2013-05-02 Daniel Chludzinski Method and Device for Self-Acting Heat Transfer in a Direction Reverse to Natural Convection

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0455184A1 (fr) * 1990-04-28 1991-11-06 Rud. Otto Meyer Procédé de chauffage et/ou refroidissement d'un bâtiment par l'énergie solaire avec utilisation d'une isolation transparente et installation utilisant ce procédé
US20060000231A1 (en) * 2002-09-11 2006-01-05 Ziquan Zhao Multifunctional constant temperature refrigerator with thermal carriers
US20120000628A1 (en) * 2010-07-01 2012-01-05 Abb Technology Ag Method for function monitoring and/or control of a cooling system, and a corresponding cooling system
US20130105117A1 (en) * 2010-07-26 2013-05-02 Daniel Chludzinski Method and Device for Self-Acting Heat Transfer in a Direction Reverse to Natural Convection

Also Published As

Publication number Publication date
IL258855B (en) 2022-07-01
IL258855A (en) 2019-02-28

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