US3823766A - Dynamic regenerative heat exchanger - Google Patents

Dynamic regenerative heat exchanger Download PDF

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Publication number
US3823766A
US3823766A US00136430A US13643071A US3823766A US 3823766 A US3823766 A US 3823766A US 00136430 A US00136430 A US 00136430A US 13643071 A US13643071 A US 13643071A US 3823766 A US3823766 A US 3823766A
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United States
Prior art keywords
piston
pair
cold fluid
heat transfer
matrices
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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.)
Expired - Lifetime
Application number
US00136430A
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English (en)
Inventor
K Sawyer
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.)
Garrett Corp
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Garrett Corp
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Filing date
Publication date
Application filed by Garrett Corp filed Critical Garrett Corp
Priority to US00136430A priority Critical patent/US3823766A/en
Priority to JP47038379A priority patent/JPS513580B1/ja
Priority to DE2219479A priority patent/DE2219479C3/de
Priority to FR7214157A priority patent/FR2134006B1/fr
Priority to GB1865972A priority patent/GB1371998A/en
Application granted granted Critical
Publication of US3823766A publication Critical patent/US3823766A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F28D19/00—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium
    • F28D19/04—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium using rigid bodies, e.g. mounted on a movable carrier
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/08—Heating air supply before combustion, e.g. by exhaust gases
    • F02C7/10—Heating air supply before combustion, e.g. by exhaust gases by means of regenerative heat-exchangers

Definitions

  • a gas turbine particularly a gas turbine directed towards a vehicular application
  • One method of accomplishing this result is to utilize a fixed boundary recuperator of either tubular or plate-fin construction as a direct transfer heat exchanger in which the compressor discharge air and the turbine exhaust gas exchange thermal energy directly through, and separated by, the heat transfer surface itself.
  • a periodic flow regenerator consisting of matrix heat transfer surfaces periodically passed through the hot and cold flow streams and back again, 7
  • FIGS. 14 are axial sectional views of the dynamic regenerator of the present invention illustrating the pistons in various axial positions.
  • FIG. 5 is an isometric view of a turbomachine including the dynamic regenerator of FIGS. 1-4.
  • FIG. 6 is a sectional view of the turbomachine of FIG.
  • FIG. 7 is a sectional view of the dynamic regenerator taken generally along lines 7--7 of FIG. 3.
  • FIG. 8 is anisometric view of an individual C-shaped matrix package.
  • FIG. 9 is an axial sectional view of an alternate dynamic regenerator having 8 matrix packages.
  • FIG. 10 is an axial sectional view of another alternate dynamic regenerator having 11 matrix packages.
  • the regenerator 10 basically comprises a pair or pairs of axial piston assemblies 40, 42 slidably within a pair or pairs of piston cylinders 44, 46 in a regenerator housing 48.
  • the housing 48 includes a central cold fluid manifold 50 to receive the flow of air to be heated, such as the compressed air from a compressor, and two hot fluid manifolds 52, 54,
  • Piston assemblies 40, 42 are disposed in piston cylinders-44, 46 respectively for alternate reciprocal axial movement therein.
  • Each piston assembly comprises a plurality of heat transfer matrix packages disposed between two piston end retainer members with adjacent matrix packages separated by piston rings.
  • piston assembly v40 includes Smatrix packages 60, 61, 62, 63 and 64, separated by piston rings '65, 66, 67 and 68 respectively.
  • the matrix packages 60,. 61, 62, 63 and 64 are retained between end retainers 80, 81.
  • Piston assembly 42 likewise has 5 matrix packages 70, 71, 72, 73 and 74 separated by piston rings 75, 76, 77 and 78 respectively.
  • End retainers 82, 83 are positioned at either end of the piston assembly 42 matrix packages 70, 71, 72, 73 and 74.
  • the piston cylinders 44 and 46 have been designated with 15 equal positions 101 through 115 respectively, each equal position substantially equal to the length of a single matrix package.
  • the piston cylinder end includes 4 positions 101, 102, 103 and 104; that is its length is equivalent to 4 matrix packages.
  • the hot fluid manifold 52 represents two positions 105 and 106 while hot fluid manifold 54 likewise represents two positions and 111.
  • Positions 107 and 109 represent bulkheads 56 and 58 respectively, while position 108 represents cold fluid manifold 50.
  • the piston assembly end retainers 80, 81, 82 and 83 while they cannot be assigned positions since they reciprocate back and forth in the piston cylinders, have a length equivalent to the combined length of 3 matrix packages or one matrix package length less than the piston cylinder ends 90, 91.
  • piston assembly 40 and 42 The axial movement of the piston assembly 40 and 42 is of an alternate reciprocal nature, that is, when piston assembly 40 is moving in one axial direction, piston assembly 42 is moving in the opposite axial direction.
  • piston assembly 40 is at its extreme left-hand position while piston assembly 42 is in its extreme right-hand position.
  • piston end retainer 80 occupies positions 101, 102 and 103;
  • matrix package 60 occupies position 104;
  • matrix packages 61 and 62 occupy positions 105 and 106 in the hot fluid manifold 52,
  • matrix package 63 occupies position 107,
  • matrix package 64 occupies position 108 in the cold fluid manifold 50 and end retainer 81 occupies positions 109, 110 and 111.
  • Positions 112, 113, 114 and 115 are vacant.
  • positions 101, 102, 103 and 104 are vacant, end retainer 82 occupies positions 105, 106 and 107; matrix package 70 occupies position 108 in the cold fluid manifold 50, matrix package 71 occupies position 109; matrix packages 72 and 73 occupy positions 110 and 111 in the hot fluid manifold 54; matrix package 74 oocupies position 112; and end retainer 83 occupies positions 113, 114 and 115.
  • end retainer 82 prevents hot fluid from hot fluid manifold 52 from entering piston cylinder 46 while piston rings 76 and 78 prevent leakage from the hot fluid manifold 54. Piston ring 75 and end retainer 82 prevent leakage or carry over from the cold fluid manifold 50.
  • piston assembly 40 has moved one position or matrix package length to the right while piston assembly 42 has moved one position to the left. In these positions, matrix packages 60 and 61 and 73 and 74 are heated by the hot fluid while matrix packages 63 and 71 are releasing heat to the cold fluid.
  • piston assembly 40 has moved a total of 2% positions to the right while piston assembly 42 has moved a total of 2% positions to the left from their respective initial reference positions.
  • the purpose of illustrating the piston assemblies 40 and 42 in a half position is to demonstrate the sealing of the piston rings during the travel between positions. It can be seen that piston rings 65 and 76 prevent leakage between hot fluid manifold 52 and cold fluid manifold 50 while piston rings 67 and 78 prevent leakage between hot fluid 'manifold 54 and cold fluid manifold 50.
  • FIG. 4 illustrates piston assembly 40 at its extreme right-hand position and piston assembly 42 at its extreme left-hand position, both a total of 4 positions removed from their initial reference positions.
  • matrix packages 62, 63 and 64 will pick up heat in positions 110 and 111 and give up this heat to the cold fluid as they move to the left through position 108 in the cold fluid manifold 50.
  • the back and forth movement of piston assembly 42 will subject matrix packages 70, 71, 72, 73 and 74 alternately to hot and cold fluid in the same manner.
  • the dynamic regenerative heat exchanger can be used in a great number of heat exchanger applications including as an intercooler, an industrial-or domestic air preheater, a process air to air unit or as a gas turbine regenerator.
  • the following detailed description of the dynamic regenerative heat exchanger is directed to a gas turbine regeneratoralthough itis equally applicable to all of the other applications.
  • the dynamic regenerative heat exchanger or regenerator 10 can be mounted at the discharge-end 11 of turbomachine 12.
  • a piston actuating mechanism 14 is mounted at one end of the dynamic regenerator 10 to provide alternate reciprocating linear motion to the pistons within the regenerator.
  • the piston actuating mechanism 14 may be a direct gear drive from an auxiliary turbomachine shaft or alternately, hydraulic, pneumatic, or electrical motors may be provided.
  • the turbomachine 12 may comprise a compressor 16 having an air inlet 20 to a single radial stage 18.
  • a regenerator duct 22 transfers the compressed air from the compressor discharge collector 24 tothe compressed air inlet 26 then to the cold fluid manifold 50 of the regenerator 10.
  • the compressor discharge air flows radially outward through the matrices 61, 72 of the pistons 40, 42 respectively of the dynamic regenerator 10.
  • the heated compressed air from the regenerator 10 is then passed to the gas generator inlet scroll 30. Following combustion in the combustor 31, the combustion gases pass through the blades 32 of the turbine 34.
  • the exhaust gases are directed through the hot fluid manifolds 52 and 54 of the regenerator which are mounted at the discharge end 11 of the turbomachine 12. As shown in FIG. 7, the hot exhaust gases pass radially inward through heat transfer matrices 63, 74 of pistons 40, 42 respectively before passing from the regenerator through exit ducts 36, 38.
  • the individual matrix packages may be straight axial matrices of a C" configuration as shown in FIGS. 6 and 7 or may be axially convoluted to increase the flow frontal area andthus reduce piston length. While these figures show the cold fluid flowing radially outward and the hot fluid flowing radially inward, this relationship can be reversed to meet specific applications.
  • Pearshaped flow splitting lobes 59 may be provided to more evenly distribute the flow through the matrices.
  • Secondary seals 55, 57 of a labyrinth type may be utilized at 5 ing:
  • any type of matrix material can be packaged within the C-shaped piston since the matrix is not a structural element.
  • the matrix material can be selected solely on the basis of its heat transfer performance, weight, and volume. It is not called upon to prevent leakage, support seals, or carry mechanical and transmission loads.
  • Matrix cores consisting of triangular fins, wavy or offset fins, woven wire screens, crossed rods, packed spheres, or glass-ceramic cellular structures can be utilized.
  • Wire wrapped screen matrices can be wrapped tightly to form a large matrix face area in a small diameter at low cost with small carry over losses.
  • An isometric view of a C-shaped wire wrapped screen is shown in FIG. 8.
  • Inherent in the dynamic regenerator is a true counterflow heat exchange condition, that is two fluid streams moving in direct opposition to each other. Heat is absorbed on the surfaces of the matrices moving through the hot exhaust gases and subsequently released to the compressor discharge air as a result of the continued axial movement of the matrices. Synchronization of the axial piston movement motivates the matrices alternately between hot and cold fluid streams and provides a self-cleaning action which insures that no fouling or clogging will occur in any of the matrices.
  • regenerator which requires face seals.
  • the axial piston ring art is highly developed for automotive and aircraft reciprocating engines which have velocities in the order of 30 ft./sec. Unlike the rotary regenerator,
  • FIGS. 1-4 While a 5 matrix package regenerator as shown in FIGS. 1-4 has been described in considerable detail and its operation provided, the number of matrix packages can be varied considerably. For example, an 8 matrix package regenerator as shown in FIG. 9 and an 11 matrix package regenerator as shown in FIG. 10 can be employed. It is possible to construct regenerators having virtually any number of matrix packages, e.g., 3, 5, 8, 9, 11, etc. There are practical limitations that make a 5, 8 or 11 matrix package most attractive. The greater the number of packages, the shorter the overall length of the regenerator and the smaller the carry over losses between the-hot and cold fluids.
  • the dynamic regenerator provides a continuous flow device (no pulsing) that can be easily packaged for efficient heat exchange and can be easily integrated with associated turbomachinery. It has numerous advantages over equivalent rotary type regenerators and fixed boundary recuperators.
  • a dynamic regenerative heat exchanger comprisa housing defining a pair of piston cylinders, said housing having a central cold fluid manifold and two hot fluid manifolds, one hot fluid manifold disposed on either side of said cold fluid manifold, each of said manifolds extending across both of said pair of piston cylinders; and
  • piston assemblies disposed within said pair of piston cylinders to alternately reciprocate therein, said piston assemblies each including at least five substantially C-shapedheat transfer matrices of 'a fluid permeable material to alternately reciprocate between one of said hot fluid manifolds and said cold fluid manifold, cold fluid from said cold fluid manifold physically passing through the fluid permeable C-shaped matrices material in one direction and hot fluid from said hot fluid manifolds physically passing through the fluid permeable C-shaped matrices material in the other direction;
  • the dynamic regenerative heat exchanger of claim land in addition, means operably associated with said housing and said pair of piston assemblies to alternately reciprocate said pair ofpiston assemblies with said pair of piston cylinders.
  • a dynamic regenerative heat exchanger comprising a housing defining a pair of piston cylinders, said housing having a central cold fluid manifold and two hot fluid manifolds, one hot fluid manifold disposed on either side of said cold fluid manifold, each of said manifolds extending across both of said pair of piston cylinders; and
  • each assembly having at least five substantially C-shaped heat transfer matrices of a fluid permeable material disposed between two end retainers with adjacent matrices separated by a piston ring to prevent the flow of fluid between adjacent matrices, each heat transfer matrix to alternately reciprocate between one of said hot fluid manifolds and said cold fluid manifold.
  • Av dynamic regenerative heat exchanger compris- 3,823 ,766 t 7 8 a pair of piston assemblies, each assembly having at least five substantially equal length, generally C- shaped heat transfer matrices disposed between two end I retainers, each end retainer having a length substantially equal to at least three heat transfer matric lengths, each of said pair of piston assemblies including at least four piston rings, one piston ring disposed between adjacent heat transfer matrices; and a housing defining a pair of piston cylinders in which 10 through the heattransfer matrices previously heated in the exhaust gas manifolds whereby the air recovers thermal energy from said heat transfer matrices, one exhaust gas manifold disposed on either side of said central air manifold.
  • a dynamic regenerative heat exchanger comprising a housing defining a first piston cylinder having a longitudinal axis and a second substantially identical to receive the air for combustion and pass the air said-pair of piston assemblies are disposed to oppositely reciprocate,
  • said housing having a central cold fluid manifold having an opening to direct the flow of cold fluid in piston cylinder having a longitudinal axis substantially parallel to the longitudinal axis of said first piston cylinder;
  • said housing having a central cold fluid manifold to one direction across said pair of piston cylinders direct the flow of a cold fluid transverse), across slibstannany equal to a ⁇ least 9 heat transffr the longitudinal'axes of said first and said second mx f hot fluld mamfolds g having an piston cylinders in one direction and having two Opening.
  • said second piston assembly disposed within said second piston cylinder to reciprocate therein along the longitudinal axis thereof oppositely to said first piston assembly, the matrices of said first and said second piston assemblies alternating between said cold fluid manifold and said hot fluid manifold.
  • a method of transferring thermal energy between a hot fluid and a cold fluid comprising:
  • a gas turbine including a fuel-air combustor, to produce. shaft power and hot exhaust gases;
  • a compressor operably associated with said gas tur- 40 bine to supply compressed air to the fuel-air combustor of said gas turbine;
  • a dynamic regenerative heat exchanger comprising,
  • a pair of piston assemblies each having at least five substantially C-shaped heat transfer matrices of a fluid permeable material therein andincluding flow splitting lobes
  • a housing defining a pair of piston cylinders in which said pair of piston assemblies are disposed to alternately reciprocate, said housing having two exhaust gas manifolds to receive the exhaust gases from said turbomachine and pass the exhaust gases through the heat transfer matrices of said pair of piston assemblies alternately reciprocating through said exhaust gas manifolds whereby said heat transfer matrices recover thermal energy cold fluid manifold and said hot fluid manifolds.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
US00136430A 1971-04-22 1971-04-22 Dynamic regenerative heat exchanger Expired - Lifetime US3823766A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US00136430A US3823766A (en) 1971-04-22 1971-04-22 Dynamic regenerative heat exchanger
JP47038379A JPS513580B1 (fr) 1971-04-22 1972-04-18
DE2219479A DE2219479C3 (de) 1971-04-22 1972-04-21 Regeneratlv-Wärmetauscher
FR7214157A FR2134006B1 (fr) 1971-04-22 1972-04-21
GB1865972A GB1371998A (en) 1971-04-22 1972-04-21 Heat exchanger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US00136430A US3823766A (en) 1971-04-22 1971-04-22 Dynamic regenerative heat exchanger

Publications (1)

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US3823766A true US3823766A (en) 1974-07-16

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US00136430A Expired - Lifetime US3823766A (en) 1971-04-22 1971-04-22 Dynamic regenerative heat exchanger

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US (1) US3823766A (fr)
JP (1) JPS513580B1 (fr)
DE (1) DE2219479C3 (fr)
FR (1) FR2134006B1 (fr)
GB (1) GB1371998A (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4052144A (en) * 1976-03-31 1977-10-04 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Fuel combustor
US4754806A (en) * 1986-09-12 1988-07-05 Astle Jr William B Reciprocating heat exchanger
WO1990015291A1 (fr) * 1989-06-08 1990-12-13 Astle William B Jr Four a air chaud a gaz efficace et procede de chauffage
US5184600A (en) * 1989-06-08 1993-02-09 Astle Jr William B Regulating the humidity of a heated space by varying the amount of moisture transferred from the combustion gases
US5562089A (en) * 1994-06-07 1996-10-08 Astle, Jr; William B. Heating with a moving heat sink
US20060054301A1 (en) * 2004-02-19 2006-03-16 Mcray Richard F Variable area mass or area and mass species transfer device and method

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2296966A (en) * 1995-01-06 1996-07-17 Andrew Bell Regenerative heat exchanger with reciprocating elements
ES2158752B1 (es) 1998-07-16 2002-06-16 Hrs Spiratube S L Mejoras en intercambiadores termicos para tratamiento de liquidos.

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US17185A (en) * 1857-04-28 cochran
GB220867A (en) * 1923-12-13 1924-08-28 Henry Harold Perry Improvements in regenerators for air and gases
GB675408A (en) * 1949-04-13 1952-07-09 Kristian Refslund Improvements in heat regenerators
GB760803A (en) * 1953-05-18 1956-11-07 British Leyland Motor Corp Heat exchangers
US2774573A (en) * 1952-07-16 1956-12-18 Air Preheater Regenerative heat exchanger with reciprocable rods
US2892615A (en) * 1953-06-12 1959-06-30 Carrier Corp Heat exchangers of the rotary regenerator type
CA675305A (en) * 1963-12-03 B.C. Jet Engines Limited Heat exchange unit
US3177661A (en) * 1962-10-09 1965-04-13 United Aircraft Corp Regenerative engine with rotating matrix

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8371C (de) * 1900-01-01 J. M. AMEIS in Nürnberg, Waizenstrafse 9 Maschine zur Fabrikation von Nachtlichten
US1548158A (en) * 1923-06-13 1925-08-04 Thomas E Murray Heat exchanger

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US17185A (en) * 1857-04-28 cochran
CA675305A (en) * 1963-12-03 B.C. Jet Engines Limited Heat exchange unit
GB220867A (en) * 1923-12-13 1924-08-28 Henry Harold Perry Improvements in regenerators for air and gases
GB675408A (en) * 1949-04-13 1952-07-09 Kristian Refslund Improvements in heat regenerators
US2774573A (en) * 1952-07-16 1956-12-18 Air Preheater Regenerative heat exchanger with reciprocable rods
GB760803A (en) * 1953-05-18 1956-11-07 British Leyland Motor Corp Heat exchangers
US2892615A (en) * 1953-06-12 1959-06-30 Carrier Corp Heat exchangers of the rotary regenerator type
US3177661A (en) * 1962-10-09 1965-04-13 United Aircraft Corp Regenerative engine with rotating matrix

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4052144A (en) * 1976-03-31 1977-10-04 The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration Fuel combustor
US4754806A (en) * 1986-09-12 1988-07-05 Astle Jr William B Reciprocating heat exchanger
WO1990015291A1 (fr) * 1989-06-08 1990-12-13 Astle William B Jr Four a air chaud a gaz efficace et procede de chauffage
US5005556A (en) * 1989-06-08 1991-04-09 Astle Jr William B Efficient gas hot-air furnace and heating process
US5184600A (en) * 1989-06-08 1993-02-09 Astle Jr William B Regulating the humidity of a heated space by varying the amount of moisture transferred from the combustion gases
US5562089A (en) * 1994-06-07 1996-10-08 Astle, Jr; William B. Heating with a moving heat sink
US20060054301A1 (en) * 2004-02-19 2006-03-16 Mcray Richard F Variable area mass or area and mass species transfer device and method

Also Published As

Publication number Publication date
JPS513580B1 (fr) 1976-02-04
GB1371998A (en) 1974-10-30
FR2134006A1 (fr) 1972-12-01
FR2134006B1 (fr) 1974-12-20
DE2219479A1 (de) 1973-07-26
DE2219479C3 (de) 1975-01-23
DE2219479B2 (de) 1974-05-22

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