US20160252277A1 - Modulation absorption refrigerator in plate design - Google Patents

Modulation absorption refrigerator in plate design Download PDF

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Publication number
US20160252277A1
US20160252277A1 US15/030,661 US201415030661A US2016252277A1 US 20160252277 A1 US20160252277 A1 US 20160252277A1 US 201415030661 A US201415030661 A US 201415030661A US 2016252277 A1 US2016252277 A1 US 2016252277A1
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Prior art keywords
plates
ammonia
absorber
plate
aqua
Prior art date
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Abandoned
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US15/030,661
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English (en)
Inventor
Gerhard Kunze
Marshal RUBINSTEIN
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SOLARFROST LABS Pty Ltd
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SOLARFROST LABS Pty Ltd
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Publication of US20160252277A1 publication Critical patent/US20160252277A1/en
Assigned to SOLARFROST LABS PTY LTD reassignment SOLARFROST LABS PTY LTD ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KUNZE, GERHARD, RUBINSTEIN, Marshal
Abandoned legal-status Critical Current

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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
    • 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
    • F25B17/02—Sorption machines, plants or systems, operating intermittently, e.g. absorption or adsorption type the absorbent or adsorbent being a liquid, e.g. brine
    • 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
    • F25B15/00—Sorption machines, plants or systems, operating continuously, e.g. absorption type
    • F25B15/02—Sorption machines, plants or systems, operating continuously, e.g. absorption type without inert gas
    • F25B15/04—Sorption machines, plants or systems, operating continuously, e.g. absorption type without inert gas the refrigerant being ammonia evaporated from aqueous solution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04F—PUMPING OF FLUID BY DIRECT CONTACT OF ANOTHER FLUID OR BY USING INERTIA OF FLUID TO BE PUMPED; SIPHONS
    • F04F1/00—Pumps using positively or negatively pressurised fluid medium acting directly on the liquid to be pumped
    • F04F1/06—Pumps using positively or negatively pressurised fluid medium acting directly on the liquid to be pumped the fluid medium acting on the surface of the liquid to be pumped
    • 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
    • F25B37/00—Absorbers; Adsorbers
    • 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
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/62—Absorption based systems

Definitions

  • Aqua-ammonia absorption refrigeration machines are considered to be large, heavy and expensive, and the energy efficiency is significantly less than with compression refrigeration machines. In conjunction with renewable energies, however, new approaches exist in refrigeration technology, which attempt to awake new interest in aqua-ammonia absorption again.
  • the present invention describes a conceivable architecture of such intermittent aqua-ammonia absorption refrigeration machines as a batch process with a bypass system, which permits the integration of control elements; including the use of a steam pump that can be controlled without moving parts and which is specifically adapted to this type of design.
  • Such steam pumps operate at a low frequency, because the medium to be conveyed must itself absorb heat in order to produce the necessary pressure. Subsequently, fresh cold solution must be drawn in again. This is because of a pressure reducer that operates automatically, which is a cold fluid volume through which—after the completion of the pump delivery process—the gas from the pump chamber bubbles while being absorbed. This typically achieves a pump cycle time from one up to several minutes. Using such cycle time, the solution quantity that is conveyed with each pump stroke almost equals the residual amount in the entire machine. The operating process of such type of refrigeration machine is therefore not continuous, but intermittent. This therefore involves a batch process. Any experience gained from working with continuously operating aqua-ammonia absorption refrigeration machines can be applied to systems with such steam pumps only subject to limitations.
  • the amount of energy which can be recovered from the absorber most important is the amount of energy which can be recovered from the absorber, subject to the condition, that the absorbing solution is cooled slowly along an extended route, while the solution concentration increases simultaneously and the pressure in the absorber remains constant.
  • the heat quantity released during the absorption almost equals the heat quantity that the generator requires to vaporize the ammonia.
  • the heat of absorption occurs in a temperature interval, the limits of which are lower than those of the temperature interval of the generator heating, even though both temperature intervals overlap, so that the heat of absorption can be recycled into the process only in this range.
  • the amount of energy used per degree Celsius to heat the solution during the gas stripping operation is much larger at low temperatures than at high temperatures.
  • Another method for improving the efficiency at low cooling temperatures and at high re-cooling temperatures consists in continuing to boil the solution coming from the generator in a second generator at a pressure level that lies between the absorber pressure and the generator pressure, and to bring this steam from the second generator into contact with the solution coming from the first absorber in a second absorber, which is at this intermediate pressure, prior to pumping said solution into the generator.
  • One part of the ammonia therefore does not circulate via the condenser and the evaporator, but returns into the first generator via a parallel route, called “bypass.”
  • the second generator and the second absorber then would be better termed bypass generator and bypass absorber.
  • this complex system requires two solution pumps, the first from the absorber to the bypass absorber, and the second pump from the bypass absorber to the generator.
  • two types of plates are used to build-up a plate stack, i.e. on the one side so-called shaped plates, made of a sealant material, preferably composite fibrous sealant materials, like a fillet fabric penetrated by holes as well as channel-shaped cutouts that are used for conducting liquids or gases, and separating plates made of metal sheet, which have holes for passing liquids or gases perpendicular relative to the plate horizontal.
  • the stack is compressed between two heavier metallic end plates by means of bolts, clamps or other mechanical means, such that each separating plate is positioned between two shaped plates and each shaped plate is positioned between two separating plates.
  • a sealant material preferably composite fibrous sealant materials, like a fillet fabric penetrated by holes as well as channel-shaped cutouts that are used for conducting liquids or gases
  • separating plates made of metal sheet, which have holes for passing liquids or gases perpendicular relative to the plate horizontal.
  • AT 511 228 B1 proposes a hydraulic cushion.
  • the main problem are the steam pumps. Their pump output cannot be controlled, because it rather depends on the applicable temperature and pressure conditions, as well as on certain statistical errors that occur. For that reason, more complex cooling cycles, involving two or more parallel or simultaneous processes involving multiple pumps cannot be performed; this applies particularly for the above-mentioned bypass system.
  • the bypass system also has problems because of the batch method: Because of the intermittent solution flow through the bypass absorber, the degassing of the hot solution in the bypass generator can sometimes not take place, and the entire bypass process runs only incompletely.
  • the temperature in a room to be cooled would only be kept constant by means of a “stop and go” operation, if temperature fluctuations are anticipated.
  • the startup of the cooling process following a shutdown can take up to 30 minutes, however.
  • the slow startup process is also related to the fact that the mentioned steam pumps require a starter, which presses the solution into the pump chamber, wherein this process has often to be repeated several times until the machine starts up.
  • a further problem is the fact that the standard structural design of absorbers and generators of conventional aqua-ammonia absorption refrigeration machines does not work as a plate design, and had to be Stahled.
  • a rudimentary proposal can be found in AT 511 228B1 FIG. 4 , wherein there, the form of generator or absorber does not differ much from the serpentine shape, which has been specifically successful for high performance heat exchangers having a plate design.
  • the solution cannot mix properly with a gas in a serpentine in the narrow gap between a shaped plate between two separating plates, which is a major limitation for the functionality of serpentine-shaped absorbers, in particular.
  • the gas generated accelerates the liquid between the gas bubbles such that the retention time of the liquid is much less than planned for.
  • throttle valves are generally customary in refrigeration machines, they have not at all proven successful in batch systems, because significant pressure fluctuations occur during the intermittent flow, which can also produce large fluctuations in the flow through a throttle valve. Float valves could solve the intermittent flow problems, but it is extremely difficult to fit these between the narrow plates. Due to the very limited space, the only suitable valves are so-called “umbrella valves,” which are small elastomer flap valves. Because of their small size, the flow ports are also very small and tend to block, if suspended solids are present in the solution, which, unfortunately, is frequently the case with the above-mentioned fibrous composite materials.
  • FIG. 1 illustrates the outside view of a refrigeration machine in the form of a plate stack
  • FIG. 2 illustrates a functional diagram with an intermittent aqua-ammonia absorption refrigeration machine with two steam pumps and bypass system.
  • FIG. 3 illustrates a functional diagram, to represent the absorber or generator including their heat transfer media as a plate stack
  • FIG. 4 illustrates a detailed section of a single ammonia plate, which represents an generator element
  • FIG. 5 illustrates a detailed section of a single ammonia plate, which represents an absorber element.
  • FIG. 6 illustrates a detail section of a single water plate, which serves for heat transfer with a generator element or an absorber element.
  • FIG. 1 illustrates the architecture of a plate stack according to the invention as an oblique view.
  • three plate stacks - 1 A, - 2 - and - 1 B- are positioned in tandem, of which the two outer ones consist of several thick plastic plates, with separating plates and water plates for temperature control; these are not shown, however, because of the scale of this drawing.
  • the plates in the inner partial stack - 2 - consist of thin shaped plastic plates with separating plates in-between, and they are a few centimeters narrower than the end plates.
  • the holes - 4 - for the connection rods, which compress the plates, can be seen on the end plate - 3 -.
  • these holes are not positioned only on the plate edges, but also define zones - 28 , 29 , 30 , 31 - in the inner plate area, behind which the containers or heat exchangers with different pressures are located, which are reciprocally bounded, because of the local pressure of the connection rods.
  • these four zones extend horizontally through the entire machine and they define in which area of the thin plates - 2 -, the functional elements, i.e. the generators - 13 , 15 -, the absorbers - 17 , 18 , 20 -, the evaporator - 25 - and the condenser - 23 -, are located.
  • the openings - 5 - can also be seen, where the straight connection lines for the heat transfer media which extend across the entire plate stack, terminate. There is space for control elements, such as solenoid valves, in the frontal recess between the two protruding thick plates - 1 A-, - 1 B- on both ends. Sensors for measuring the liquid level in the containers are likewise fitted into the thick plates - 1 A-, - 1 B-, and the corresponding openings - 7 - are to accommodate these sensors.
  • FIG. 2 illustrates a functional diagram of a module of a refrigeration machine according to the invention as a plate stack.
  • the containers are drawn as rectangles with rounded corners, and plate heat exchangers are drawn as plate packs in oblique view.
  • Arrows indicate the direction of flow of solution or gas, and connection lines without arrows refer to lines which serve for pressure equalization or for the condensate return flow. Any arrows on the drawing pointing up or down refer to lines which are also actually running up or down.
  • Heat transfer media which are moving in the so-called “water plates” - 27 -, have not been shown to maintain clarity.
  • the two steam pumps are in the left part of the picture, wherein pump 1 is formed by the parts 9 A, 9 B, 9 C, 9 D and 8 A as well as M 3 , V 1 and V 2 , and the pump 2 is formed by parts 11 A, 11 B, 11 C, 11 D an 10 A, as well as M 5 , V 3 and V 4 .
  • the function of the steam pumps is explained by the example of pump 1 : When a solenoid valve -M 3 - is open, the chamber - 9 A- is filled with solution from the absorber reservoir - 8 - that lies above the ball check valve -V 1 -. Chamber 9 A is constantly temperature controlled by two water plates positioned on the outside, such that the temperature is kept between a minimum of 7° C.
  • the inlet chamber - 8 A- is constantly kept at the temperature of the condenser by the abutting water plates, and is supplied with fresh solution from absorber - 18 - in each cycle, which, after a brief residence period in the inlet chamber - 8 A-, flows across an overflow into the actual solution reservoir - 8 - of the absorber - 18 -.
  • the solution gets into the generator pre-reservoir - 12 -, the purpose of which is to reduce the pressure surges from the pump onto the generator and from there into the actual generator - 13 - and then into the generator gas separator - 14 -.
  • the solenoid control valve -M 1 - then permits the now weak solution to flow into the bypass generator - 15 -.
  • the bypass generator - 15 - also has a gas separator - 16 -, and when the solution level exceeds a predetermined value there, the second solenoid control valve -M 2 - allows the so-called “over-dilute solution” to flow into the hot absorber - 17 -, where the solution absorbs gas from evaporator - 25 -. From there, the solution and the part of the gas that was not absorbed in the heat is forwarded into the warm absorber - 18 -, where the absorption process is continued. Thereafter, the now concentrated solution gets into the absorption reservoir - 8 - and again into the first pump.
  • the gas from the gas separator - 14 - is supplied via the rectifying column - 22 -, where it releases part of its heat for heat recovery and is then directed through the check valve -V 5 - to the condenser - 23 - where it liquefies and then flows into the condenser reservoir - 24 -.
  • the solenoid control valve -M 4 - controls the stored quantity of liquid ammonia in reservoir - 24 -, and therefore the solution concentration in the absorbers. In this way, the cooling temperature of the machine can be defined. Via the valve -M 4 -, the liquid ammonia gets into the evaporator - 25 - where it evaporates and produces the cooling effect, which is absorbed by a cooling medium there. From the evaporator the gas then gets into the hot absorber - 17 -.
  • a check valve in this connection line can prevent any short-term problems of the machine operation in the event of large fluctuations in the re-cooling temperature, but this is not absolutely necessary.
  • the route of the ammonia from the bypass generator to the bypass absorber From the bypass generator - 15 -, the over-dilute solution including the released gas, gets to bypass gas separator - 16 -, where the solution flows to the solenoid control valve -M 2 -, while the separated gas goes to the gas cooler - 21 -, where it releases part of its heat to heat recovery, and gets from there to the bypass absorber.
  • FIG. 3 schematically illustrates an optimal design for a generator or absorber, including the heat transfer medium, using a stack that is made up of vertical plates according to the invention.
  • FIG. 3 schematically illustrates an optimal design for a generator or absorber, including the heat transfer medium, using a stack that is made up of vertical plates according to the invention.
  • the involved shaped plates are illustrated, because in reality, there is always one separating plate positioned between each two shaped plates, where the separating plate has holes precisely at the locations at which the connection lines illustrated in FIG. 3 must pass through the separating plate.
  • the illustrated plate sections correspond in each case only to a partial area of generators or absorbers - 13 , 15 , 17 , 18 - or - 20 - within the partial stack - 2 -, where they are collectively stacked in tandem to form a thicker plate stack, in which thin shaped plates - 26 , 27 - alternate with separating plates that are not illustrated.
  • the plates - 26 - are called ammonia plates, because only ammoniacal solution or pure ammonia can be present in those at any time, while the plates - 27 - are called water plates, because they can only contain heat transfer media, which usually but not always are containing a lot of water.
  • the water plates - 27 - and the ammonia plates - 26 - alternate systematically throughout the entire partial stack - 2 -.
  • FIG. 3 illustrates how the connection lines of these plates have to run so that both the ammonia plates - 26 - as well as the water plates - 27 - can change their temperature throughout the plate stack slowly and uniformly, since the involved media, on one side - 26 A, 26 B and then 27 A flow counter current.
  • FIG. 4 illustrates a plate section of zone - 28 - of a generator - 13 - or - 15 -.
  • the inflow and the outflow lines for gas - 26 B- can be seen on the left and on the right, and the boiling and bubbling solution - 26 A-.
  • Directional arrows are not indicated, because the generator plates, as can be seen in FIG. 3 , are alternatively flowed through from left and from right.
  • the generator elements - 13 - do not have dividers for redirecting solution - 26 A- or gas - 26 B-.
  • FIG. 5 illustrates a plate section of zone - 29 - of an absorber - 17 , 18 - or - 20 -, which are all developed identical. It can be seen that the gas - 26 B- is directed initially through a siphon - 17 A- downward below the solution - 26 A- and then streaming upward through the serpentine positioned on the right blubbering past the solution. A gas separator lies in the upper area - 17 B-, so that the gas - 26 B- can escape from the top of the plate, while the solution - 26 A-leaves the plate section at the lower end, which is possible because siphon - 17 A-predetermines a pressure differential to the adjacent plate.
  • the flow in the illustrated plate - 17 - is from right to left
  • the flow in the following ammonia plate is from left to right
  • the plate form is a horizontal mirror image, so that on the next absorber plate inlet, a siphon - 17 A-, is positioned on the left side again.
  • FIG. 6 illustrates a corresponding plate section of a water plate, wherein this form is applicable both for zone - 28 - as well as for zone - 29 -.
  • the special form of the rising serpentine is intended to force air bubbles to the top, so that the entire space covered by the serpentine will be free of air. In the event that an air bubble sticks in the downward channel on the right side, this will then affect only a very small part of the active heat exchanger surface.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Sorption Type Refrigeration Machines (AREA)
US15/030,661 2013-10-21 2014-10-16 Modulation absorption refrigerator in plate design Abandoned US20160252277A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
ATA807/2013A AT514997B1 (de) 2013-10-21 2013-10-21 Modulare Absorptionskältemaschine in Plattenbauweise
ATA807/2013-1 2013-10-21
PCT/IB2014/002399 WO2015059563A2 (de) 2013-10-21 2014-10-16 Modulare absorptionskältemaschine in plattenbauweise

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US20160252277A1 true US20160252277A1 (en) 2016-09-01

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US15/030,661 Abandoned US20160252277A1 (en) 2013-10-21 2014-10-16 Modulation absorption refrigerator in plate design

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US (1) US20160252277A1 (de)
CN (1) CN105849476A (de)
AT (1) AT514997B1 (de)
AU (1) AU2014338692B2 (de)
WO (1) WO2015059563A2 (de)

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CN106802017B (zh) * 2015-11-26 2023-08-01 四川捷元科技有限公司 吸收式制冷单元一体式水流管道系统
CN106802016B (zh) * 2015-11-26 2023-04-21 四川捷元科技有限公司 吸收式制冷单元水流接口
CN106802018B (zh) * 2015-11-26 2023-04-21 四川捷元科技有限公司 吸收式制冷单元
CN106802014A (zh) * 2015-11-26 2017-06-06 四川捷元科技有限公司 吸收式制冷单元内置式溶液热交换器
CN106802015B (zh) * 2015-11-26 2023-08-01 四川捷元科技有限公司 吸收式制冷单元节流装置
CN106802013B (zh) * 2015-11-26 2023-04-21 四川捷元科技有限公司 单元组合式制冷矩阵
CN106802030B (zh) * 2015-11-26 2023-08-01 四川捷元科技有限公司 吸收式制冷单元无循环泵冷媒蒸发器
DE102016010741A1 (de) * 2016-09-03 2018-03-08 Eco ice Kälte GmbH Ammoniak/Wasser- Absorptionskältemaschine
CN106288497A (zh) * 2016-10-17 2017-01-04 四川捷元科技有限公司 吸收式制冷单元内部换热组件、吸收式制冷单元及矩阵
CN106288491A (zh) * 2016-10-18 2017-01-04 四川捷元科技有限公司 吸收式制冷单元及吸收式制冷矩阵
CN111158411B (zh) * 2020-01-17 2021-05-18 深圳市曼恩斯特科技股份有限公司 一种恒温装置

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US20140029030A1 (en) * 2012-07-25 2014-01-30 Nike, Inc. Graphic Alignment For Printing to An Article Using A First Display Device And A Second Display Device

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Publication number Publication date
AT514997A1 (de) 2015-05-15
CN105849476A (zh) 2016-08-10
WO2015059563A2 (de) 2015-04-30
AU2014338692A1 (en) 2016-06-09
AT514997B1 (de) 2015-11-15
WO2015059563A3 (de) 2015-07-30
AU2014338692B2 (en) 2017-07-13

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