US20130058817A1 - Surface heat exchanger for compressible fluid alternative volumetric machines - Google Patents

Surface heat exchanger for compressible fluid alternative volumetric machines Download PDF

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Publication number
US20130058817A1
US20130058817A1 US13/584,202 US201213584202A US2013058817A1 US 20130058817 A1 US20130058817 A1 US 20130058817A1 US 201213584202 A US201213584202 A US 201213584202A US 2013058817 A1 US2013058817 A1 US 2013058817A1
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Prior art keywords
fluid
heat exchanger
duct
permanent motion
passage
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Abandoned
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US13/584,202
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English (en)
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Raffaele Cozzolino
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Individual
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    • 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
    • F28D9/0031—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 the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0037—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 the conduits for one heat-exchange medium being formed by paired plates touching each other the conduits for the other heat-exchange medium also being formed by paired plates touching each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/06—Cooling; Heating; Prevention of freezing
    • F04B39/064—Cooling by a cooling jacket in the pump casing

Definitions

  • the present invention concerns the technical field of compressible fluid alternative volumetric machines, such as, e.g., industrial air and gas compressors, compressors for chemical or petrochemical industry, expanders, and it makes specific reference to an innovative surface heat exchanger to be installed in an compressible fluid alternative volumetric machine so that maximum amount of heat is exchanged at the same time work exchange realised during thermodynamic transformation occurring within said volumetric machine.
  • compressible fluid alternative volumetric machines such as, e.g., industrial air and gas compressors, compressors for chemical or petrochemical industry, expanders
  • thermodynamic transformation is an adiabatic transformation, i.e. gas does not exchange heat with outer environment.
  • thermodynamic it would be suitable realising an isothermal transformation, and thus maintaining temperature constantly equal to the starting point temperature, n order to reduce the work amount to be spent to compress the same gas mass at the same final pressure value, or to increase the work amount that can be obtained by expansion of the same gas mass with respect to the same expansion ratio value.
  • limits for realising an isothermal transformation is due to difficulties of fluid evolving within volumetric machine to exchange heat with outside, i.e. with a thermal source able to absorb heat generated during a compression or adducing heat during an expansion.
  • fins have been provided on said wall.
  • thermal exchange inverse of thermal exchange global coefficient, defined as global resistance, is substantially given by addition of two terms (convective thermal resistance of fluids), each one being opposite of convective exchange coefficient of relevant fluid. Therefore, in volumetric machine, one of the two terms is reverse of convective coefficient of a fluid carrier, usually a fluid having a permanent motion, and other term is reverse of convective coefficient of a fluid evolving within volumetric machine and it has not therefore a permanent motion.
  • thermal exchange global coefficient driven by fluid convective coefficient with the lower value between the two fluid convective coefficients.
  • a drawback is due to the fact that values of evolving fluid convective coefficient can be difficulty obtained.
  • amount of data available, collected in a dimensionless way for a high number of geometries refers to permanent motion conditions of both flows, and thus permits an easy proportioning of heat exchangers wherein fluids passing through are both in a permanent motion.
  • a further disadvantage is due to the difficulty of realising efficient heat exchangers with small dimensions so that they can be easily applied within the alternative volumetric machine, so that heat exchange occurs simultaneously with thermodynamic transformation realised in said volumetric machine.
  • Object of the present invention is that of overcoming said disadvantages, by providing a surface heat exchanger which is compact, to be applied within a compressible fluid alternative volumetric machine, so that maximum amount of heat is exchanged between fluid having a not permanent motion, evolving within the alternative volumetric machine, by a first conduct assembly, provided within the heat exchanger, and a fluid carrier, having a permanent motion, passing through a second conduct assembly of the heat exchanger, simultaneously to the work exchange during thermodynamic transformation occurring within said alternative volumetric machine, thus remarkably improving performances of the volumetric machine, as far as work given or obtained per kg of fluid is concerned.
  • object of the invention is that of reducing unitary compression work for each evolving fluid mass unit, i.e. work to be provided to a compressor, or that of increasing unitary expansion work that can be obtained during within an expander from evolving fluid mass unit.
  • a surface heat exchanger to be inserted within a compressible fluid volumetric alternative machine, within which a fluid moves in a not permanent motion, said heat exchanger comprising a plurality of walls, side by side each other, so shaped to realize at least a first duct for the passage of a fluid in a permanent motion, and at least a second duct for the passage of said fluid in a not permanent motion, said first and second ducts being configured so as to make said two fluids exchanging heat.
  • heat exchanger can be provided with a core having a cylindrical shape, said cylindrical shape having any straight, regular or irregular, section contained within the straight section of a cylinder of said alternative volumetric machine, and said at least a second duct for passage of said fluid in a not permanent motion is parallel to the longitudinal axis of said cylinder.
  • said plurality of walls can be comprised of at least a group of three walls, wherein at least the first and the second walls are respectively provided with at least a groove, provided on a lateral surface of each one of said walls; said walls being provided so that said at least one groove of said first wall realises with the lateral surface of said second wall, a duct for passage of the fluid in permanent motion, and in that said at least one groove of said second wall realises a duct for passage of the fluid in a not permanent motion, along with the lateral surface of said third wall.
  • said at least one groove of said first wall has an equal or different orientation with respect to said at least one groove of said second wall, which is adjacent with respect to said first groove.
  • said at least one duct for passage of the fluid in permanent motion and/or said at least one duct for passage of the fluid in a not permanent motion has a rectangular section. If the shortest side of the rectangular section of said ducts varies, with the same longest side and the same duct length, inner volume of each duct varies, without substantially varying the exchange surface as well as the hydraulic diameter, and the ratio between the exchange surface and the volume, which is the inverse of the hydraulic diameter.
  • lower side of rectangular section of each one of said ducts for passage of said fluid in a not permanent motion can be included within the interval of 0.1 mm and 1 mm.
  • orientation each other of said at least one groove for passage of fluid in permanent motion and said at least one groove for passage of the fluid in a not permanent motion is such to realise a cross flow heat exchanger, e.g. a perpendicular flow exchanger, or a parallel flow heat exchanger, e.g. a co-current exchanger or a counter current exchanger.
  • said group of walls is made up of a single piece, or by different elements assembled together.
  • a compressible fluid alternative volumetric machine comprising inside the surface heat exchanger as defined in the above, provided between the Top Dead Centre of a movable member of said volumetric machine, e.g. a piston, and a discharge valve or a discharge valve system.
  • an intake valve or an intake valve assembly is provided, in the compressible fluid volumetric machine, close to the Tope Dead Centre of the movable member, at the exit of an intake duct provided in heat exchanger.
  • an intake valve or an intake valve assembly is provided, in the compressible fluid volumetric machine, so as to take fluid in not permanent motion from outside, by a duct bringing said fluid from outside directly within a cylinder of said volumetric machine.
  • heat exchanger according to the invention is applied within a compressor, but it can be advantageously applied within every kind of compressible fluid alternative volumetric machine, e.g. an industrial gas compressor, a chemical or petrol chemistry industry compressor, an air conditioning compressor or an expander.
  • compressible fluid alternative volumetric machine e.g. an industrial gas compressor, a chemical or petrol chemistry industry compressor, an air conditioning compressor or an expander.
  • FIG. 1 is a longitudinal section view of a known volumetric machine, such as an alternative compressor;
  • FIG. 2 is a longitudinal section view of volumetric machine of FIG. 1 , with a heat exchanger according to the invention within the same;
  • FIG. 3 schematically shows path of a fluid having a permanent motion within heat exchanger of compressor of FIG. 2 ;
  • FIG. 4 is a top view of surface heat exchanger according to the invention.
  • FIG. 5 is a lateral view of surface heat exchanger according to the invention.
  • FIG. 6 is an exploded view of a particular of surface heat exchanger, relevant to two walls of heat exchanger, each one having a lateral surface provided with grooves for passage, respectively in first wall, of a fluid having a permanent motion, and in second wall of a fluid, having a not permanent fluid.
  • a surface heat exchanger configured to be installed within a compressible fluid alternative volumetric machine, so that an amount of heat is exchanged simultaneously with work exchange during thermodynamic transformation occurring within said alternative volumetric machine.
  • said alternative volumetric machine is a compressor 200
  • said heat exchanger 100 is positioned within said compressor 200 , between stop of a piston 203 (Top Dead Center or TDC), movable within a cylinder 201 , and outlet valve or discharge valve 207 provided in head 202 of said compressor.
  • TDC Top Dead Center
  • Heat exchanger 100 has a metallic mass for heat exchange, also indicated as core, generically indicated by reference number 103 , comprising two duct systems, through one of which a fluid having a not permanent motion passes, and through the other one a carrier fluid having a permanent motion passes, preferably a refrigerating fluid.
  • Core 103 has a cylindrical shape, having a straight section included within the straight section of cylinder 201 of compressor 200 .
  • Core 103 of heat exchanger 100 provides a plurality of walls 1 , 1 ′ (in the embodiment shown in FIG. 6 it is provided a pair of walls 1 , 1 ′) side by side each other, each one providing, on its lateral walls, one or more grooves, respectively grooves 2 , 2 ′, comprising channels for passage of fluid having a permanent motion and a fluid having a not permanent motion.
  • Walls 1 , 1 ′ are provided so that surface of wall 1 on which grooves 2 are provided touches wall surface 1 ′ without grooves to create ducts for passage of fluid having a permanent motion ( FIG. 5 ).
  • grooves 2 of wall 1 are perpendicular to grooves 2 ′ of adjacent wall 1 ′.
  • orientation each other of grooves 2 , 2 ′ can be different from the perpendicular one.
  • Lateral surfaces of ducts 22 , 22 ′ comprised by said grooves 2 , 2 ′ are exchange surfaces through which fluid having a not permanent motion yields heat to fluid having a permanent motion.
  • each one of ducts 22 , 22 ′ has a straight section. This permits obtaining for each duct 22 , 22 ′, that to a variation of lower side of straight section corresponds to a variation of S/V ratio, as well as of hydraulic diameter, proportional to inverse of said S/V ratio.
  • Longer side of straight section of ducts 22 for passage of fluid having a permanent motion and of ducts 22 ′ for passage of fluid having a not permanent motion can have any length, on the basis of core dimensions. Length of longer side of straight section of ducts 22 for passage of fluid having a not permanent motion can be different with respect to length of ducts 22 ′ for passage of fluid having a not permanent motion. With increase pressure of fluid having a not permanent motion, depending on use of type of alternative volumetric machine wherein it is introduced heat exchanger 100 , it is necessary reducing length of longer side of straight section of each one of ducts 22 for passage of fluid having a not permanent motion, thus increasing number of ducts, so that they give a higher resistance to stresses due to inner pressure.
  • Lower side of straight section of ducts 22 for passage of fluid having a permanent motion and of ducts 22 ′ for passage of fluid having a not permanent motion can be the equal to lower than 1 mm.
  • heat exchanger 100 can be characterized by a remarkable compactness with respect to traditional heat exchangers.
  • Size limit for section of said ducts is connected with needing of housing the highest number of ducts within heat exchanger core 103 , to increase exchange surface, bearing in mind that inner volume of ducts 22 ′ for passage of fluid having a not permanent motion is as lower as possible, and that pressure drops within ducts 22 for passage of fluid having a permanent motion are very low.
  • micro-turbulences of said fluid are caused within said ducts, particularly during the re-expansion stage of the fluid contained within dead space of compressor 200 , obliging the same fluid to flow back, i.e. to invert its flow direction, even if for short time periods, with positive effects on convective exchange coefficient of fluid with a not permanent motion.
  • Reduction of section of ducts 22 , 22 ′ made up of relevant grooves 2 , 2 ′ can be done up to the permitted value useful to prevent pressure drop of fluid passing through.
  • inlet valve or intake valve 205 of compressor 200 is displaced from a position close to the testate 202 , to exit of an intake duct 102 provided in heat exchanger 100 , still being close to the Top Dead Center, to permit to the entering fluid to fill in cylinder 201 , without heating the latter fluid by heat exchanger walls ( FIG. 2 ).
  • intake valve 205 of alternative volumetric machine is so positioned to take gaseous fluid from outside, by a duct bringing it within cylinder 201 of compressor 200 .
  • a first advantage of the solution according to the invention is due to the compactness of heat exchanger with respect to a known one.
  • Compactness of heat exchanger according to the present invention is an important feature to permit its introduction within an alternative volumetric machine, without an increase of dead space of volumetric machine caused by inner volume of ducts for passage of gaseous fluid, and without reducing buckling of compression or expansion transformation, i.e. without reducing exponent of relevant polytrophic.
  • the above means preventing that maximum pressure that can be reached within a compressor is reduced or increasing pressure during expansion phase within an expander.
  • possibility of realizing a compact heat exchanger wherein increase of work volume due to inner volume of ducts through which fluid with a not permanent motion passes is limited with respect to increase of exchange surface.
  • S/V ratio of volumetric machine provided with said heat exchanger is substantially higher than ratio of a traditional volumetric machine without said heat exchanger.
  • a second advantage is due to possibility of realizing, by choosing suitable sections of each duct for passage of fluids, a heat exchanger with dimension defined by cylinder bore of compressor on which heat exchanger is to be provided, maximum thermal exchange surface, minimum inner volume of passage ducts for gaseous fluid with not permanent motion and minimum pressure drops of passage ducts for carrier fluid with permanent motion.
  • a third advantage is that use of heat exchanger according to the invention is the high energy saving, in function of ratio between pressures and thus saves of costs. Said energy saving is given, for a compressor, as the lower work necessary to compress 1 Kg of fluid and for an expander, the higher work done during expansion of one Kg of fluid.
  • a fourth advantage is that fluid with a permanent motion within corresponding ducts characterized by values of relevant convective exchange coefficient that can be easily defined, thanks to huge amount of studies and test results available, along with the increase of convective exchange coefficient on side of fluid with a not permanent motion, permits an easy interpretation of global exchange coefficient.
  • a fifth advantage is due to the fact that heat exchanger can be used even where an amount of fluid evolves within a volume trapped between two shut off means to realize a transformation characterized by simultaneous exchanges of thermal energy and pressure, under periodical and varying kinetic conditions.
  • heat exchanger can be also installed between two compressible fluid volumetric machines, regardless if they are of the same type, such as two compressors or two expanders, or different each other, such as a compressor and an expander.
  • heat exchanger can be positioned between two volumetric machines to realize a regenerative thermodynamic cycle.
  • said two volumetric machines are so connected each other by two different ducts that fluid with a not permanent motion, evolving within first volumetric machine, enters within second volumetric machine, by a first duct, evolves within the second volumetric machine, going back to the first volumetric machine, through a second duct, wherein said first and second ducts are ducts of a heat exchanger that can be thus defined as regenerative.
  • said heat exchanger can be applied to any alternative volumetric machine, e.g. an alternative volumetric machine in an energetic system for production of mechanical work or in energetic system for air conditioning or in a system for obtaining temperatures under 0°, or even temperatures of about ⁇ 180° C. or ⁇ 250° C., transferring to the system the consequent energetic advantages.
  • an alternative volumetric machine in an energetic system for production of mechanical work or in energetic system for air conditioning or in a system for obtaining temperatures under 0°, or even temperatures of about ⁇ 180° C. or ⁇ 250° C., transferring to the system the consequent energetic advantages.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US13/584,202 2010-02-16 2012-08-13 Surface heat exchanger for compressible fluid alternative volumetric machines Abandoned US20130058817A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
ITRM2010A000060 2010-02-16
ITRM2010A000060A IT1398189B1 (it) 2010-02-16 2010-02-16 Scambiatore di calore a superficie per macchine volumetriche a fluido comprimibile.
PCT/IT2011/000040 WO2011101882A1 (en) 2010-02-16 2011-02-16 Surface heat exchanger for compressible fluid alternative volumetric machines

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PCT/IT2011/000040 Continuation WO2011101882A1 (en) 2010-02-16 2011-02-16 Surface heat exchanger for compressible fluid alternative volumetric machines

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EP (1) EP2536992B1 (it)
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WO (1) WO2011101882A1 (it)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113730953A (zh) * 2021-09-07 2021-12-03 合肥今越制药有限公司 用于痛风性关节炎痹克片制备的超临界萃取物总混装置

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014005229A1 (en) 2012-07-04 2014-01-09 Kairama Inc. Temperature management in gas compression and expansion

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4968222A (en) * 1988-05-31 1990-11-06 Aisin Seiki Kabushiki Kaisha Reciprocating compressor with an inter cooler for cooling the operational gas
US5072790A (en) * 1990-07-30 1991-12-17 Jones Environics Ltd. Heat exchanger core construction
US6026894A (en) * 1997-08-27 2000-02-22 Ktm-Kuhler Gmbh Plate-type heat exchanger, in particular oil cooler
US6739385B2 (en) * 2000-08-31 2004-05-25 Behr Gmbh & Co. Plate-type heat exchanger
US7152670B2 (en) * 1999-10-08 2006-12-26 Carrier Corporation Plate-type heat exchanger

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59185883A (ja) * 1983-04-07 1984-10-22 Aisin Seiki Co Ltd 往復式圧縮機
DE19535079C2 (de) * 1994-10-13 2001-02-22 Wabco Gmbh & Co Ohg Verdichter
DE102005012202A1 (de) * 2005-03-15 2006-09-28 Itg Kompressoren Gmbh Zylinderkopf für einen mehrstufigen Kolbenverdichter
DE102005059491A1 (de) * 2005-12-13 2007-06-14 Knorr-Bremse Systeme für Nutzfahrzeuge GmbH Wassergekühlter Kolbenverdichter

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4968222A (en) * 1988-05-31 1990-11-06 Aisin Seiki Kabushiki Kaisha Reciprocating compressor with an inter cooler for cooling the operational gas
US5072790A (en) * 1990-07-30 1991-12-17 Jones Environics Ltd. Heat exchanger core construction
US6026894A (en) * 1997-08-27 2000-02-22 Ktm-Kuhler Gmbh Plate-type heat exchanger, in particular oil cooler
US7152670B2 (en) * 1999-10-08 2006-12-26 Carrier Corporation Plate-type heat exchanger
US6739385B2 (en) * 2000-08-31 2004-05-25 Behr Gmbh & Co. Plate-type heat exchanger

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113730953A (zh) * 2021-09-07 2021-12-03 合肥今越制药有限公司 用于痛风性关节炎痹克片制备的超临界萃取物总混装置

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ITRM20100060A1 (it) 2011-08-17
IT1398189B1 (it) 2013-02-14
EP2536992A1 (en) 2012-12-26
WO2011101882A1 (en) 2011-08-25
EP2536992B1 (en) 2019-07-31

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