US3915222A - Compressible fluid contact heat exchanger - Google Patents

Abstract

This invention is directed to the contact interchange of thermal and kinetic energy between adjacent compressible fluid streams across a virtual heat transfer surface at substantially different velocities in parallel flow. The invention may find especial application as a regenerative heat exchanger in gas turbine power plants, or as the low-velocity contact-type air pre-heater of a steam generator or furnace. Hot low-pressure exhaust fluids and cool compressed intake fluids enter the receiver-side section of an elongate heat exchanger. Intake-fluid stream pressure energy is converted to kinetic energy within nozzle passageways of the receiver-side section. The cold high-velocity intake-fluid stream is rapidly heated in the velocity-accelerated contact interchange process by the hot low-velocity exhaust-fluid stream within the mixing section. Following the contact interchange process, the intakefluid and exhaust-fluid streams are separated from each other by flow-dividing members and discharged from the separator-side section. Within the preheated intake-fluid stream, normal shock in supersonic flow across the inlet of the intake-fluid discharge passage is averted by the effects of variable control over characteristic length and exhaust-fluid outlet flow control.

Description

United States Patent [1 1 Hull [ COMPRESSIBLE FLUID CONTACT HEAT EXCHANGER [76] Inventor: Francis R. Hull, 567 E. 26th St.,

Brooklyn, NY. 11210 221 Filed: Jan. 27, 1971 211 Appl. No.: 110,046

Related US. Application Data [63] Continuation-impart of Ser. Nos. 830,189, May 19, 1969, abandoned, and Ser. No. 689,241, Nov. 29, 1967, abandoned, and Ser. No. 632,122, Feb. 6, 1967, abandoned, and Ser. No. 562,068, June 1, 1966, abandoned, and Ser. No. 323,499, Nov. 13, 1963, abandoned.

[52] US. Cl 165/111; 60/3951 R; 165/1; 165/52; 165/96 [51] Int. Cl. F28c 3/02 [58] Field 01 Search 165/1, 52, 96, 155, 164, 165/111; 60/3951 R, 95

[56] References Cited FOREIGN PATENTS OR APPLICATIONS 869,355 5/1961 United Kingdom 165/1 Primary ExaminerAlbert W. Davis, Jr.

[ 1 Oct. 28, 1975 [57] ABSTRACT This invention is directed to the contact interchange of thermal and kinetic energy between adjacent compressible fluid streams across a virtual heat transfer surface at substantially different velocities in parallel flow. The invention may find especial application as a regenerative heat exchanger in gas turbine power plants, or as the low-velocity contact-type air preheater of a steam generator or furnace.

Hot low-pressure exhaust fluids and cool compressed intake fluids enter the receiver-side section of an elongate heat exchanger. Intake-fluid stream pressure energy is converted to kinetic energy within nozzle passageways of the receiver-side section. The cold high-velocity intake-fluid stream is rapidly heated in the velocity-accelerated contact interchange process by the hot lowvelocity exhaust-fluid stream within the mixing section. Following the contact interchange process. the intake-fluid and exhaust-fluid streams are separated from each other by flow-dividing members and discharged from the separator-side section. Within the preheated intake-fluid stream, normal shock in supersonic flow across the inlet of the intake-fluid discharge passage is averted by the effects of variable control over characteristic length and exhaust-fluid outlet flow control.

26 Claims, 39 Drawing Figures U.S. Patent Oct.28, 1975 Sheet 1 of 10 3,915,222

Franc/Is R Hall INVENTOR iiii l1- arm ATTORNEY U.S. Patent 0m. 28, 1975 Sheet 2 of 1 3,915,222

' FIG. 3

Franc/Is R Hu/l INVENTOR ATTORNEY US. Patent Oct. 28, 1975 R 56 ENERATIVE APARAT U? Sheet 3 of 10 FIG 8 I OI -95 GENERATOR TURBINE FLOW COMPRESSOR 66 GAS REGENERATIVE APARATUS 3 FREE 57 TURBINE COMBUSTION 64 I HAMBER 67 7/ n nEsson 65 70 GAS GENERATOR TURBINE Bl #271212 R Hul/ ATTOR N EY U.S. Patent Oct.28, 1975 Sheet6of 10 3,915,222

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INVENTOR. F rancis R. Hull BY Z46- $63M;

ATTORNEYS U.S. Patent Oct.28, 1975 Sheet8of 10 3,915,222

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ATTORNEYS US. Patent 061.28, 1975 Sheet 10 of 10 3,915,222

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cu E7 m P3 LL. m Q m m m N N m (\1 L0 g 0 m m (D R, m m U! m a: 8 LL INVENTOR. Francis R. Hull ATTORNEY COMPRESSIBLE FLUID CONTACT HEAT EXCHANGER The present invention is acontinuation-in-part of my presently pending application Ser. No. 830,189, entitled Compressible Fluid Contact Heat Exchanger filed May 19, 1969, now abandoned; my prior application Ser. No. 689,241 entitled Compressible Fluid Contact Heat Exchanger" filed Nov. 29, 1967, now abandoned; my prior application Ser. No. 632,122 entitled Compressible Fluid Contact Heat Exchanger" filed Feb. 6, 1967, now abandoned; my prior application Ser. No. 562,068 entitled Compressible Fluid Contact Heat Exchanger" filed June I, 1966, now abandoned; and my prior application Ser. No. 323,499 entitled Compressible Fluid Contact Heat Exchanger" filed Nov. 13, 1963, now abandoned.

This invention relates to the contact interchange of thermal energy between adjacent streams of compressible fluids at different velocities in parallel flow by means of opposed sonic or super-sonic nozzle-diffuser combinations and arrangements, the entire nozzledifluser assemblage being concentrically mounted within the confines of a duct or tubular accommodating and mixing chamber.

As used hereinafter,

The term fluid shall refer to any liquid or gaseous medium;

The term compressible fluid shall refer to any gaseous medium; the term exhaust fluid shall refer to the discharge stream of combusted gases from an internal combustion engine, to the exhaust gases from any other heat engine, or to high-temperature gases leaving a combustion chamber or other heat source;

the term intake fluid shall relate to the incoming fluid stream of precombustion gases to an internal combustion engine (air), the incoming fluid stream to a heat engine, the incoming fluid stream to the combustion chamber of any heat exchange apparatus, or to the incoming fluid stream to any other heat source before major quantities of thermal energy are added to the incoming fluid stream;

the term heat engine shall refer to a thermodynamic engine which may convert thermal or molecular energy in the working fluid stream to mechanical energy, or convert mechanical energy to thermal or molecular energy in the working fluid stream;

the term contact interchange shall relate to the fluid'to-fluid exchange of thermal and kinetic energy between adjacent fluid streams having different velocities in parallel flow, and having now phys ical or mechanical separation between them;

the term heating fluid shall refer to the lowtemperature member of adjacent fluid streams in parallel flow which is being heated by contact interchange with an adjacent hightemperature fluid stream;

the term coming fluid shall relate to the hightemperature 1ember of adjacent fluid streams wh ch is being cooled by contact interchange with an adjacent low-temperature fluid stream;

the term combusted fluid shall refer to a fluid stream within which a combustion process has taken place following the injection ofa combustible fuel;

the term sub-sonic flow shall refer to fluid velocities which are less than the velocity of sound in the fluid at a particular energy state;

the term sonic flow shall refer to fluid velocities which are equal to the velocity of sound in the fluid at a particular energy state;

the term super-sonic flow shall refer to fluid velocities which are greater than the velocity of sound in the fluid at a particular energy state;

the term mixing length shall refer to the effective linear dimension perpendicular to the direction of mean fluid flow within which contact interchange of thermal and kinetic energy shall take place between a heating fluid stream and a cooling fluid stream;

the term characteristic length shall refer to the effective linear dimension parallel to the direction of mean fluid flow within which energy transfer be tween particles of adjacent heating fluid and cooling fluid streams shall take place by means of contact interchange;

the term regenerator shall refer to a device which transfers thermal energy from hot exhaust gases in a thermal process or cycle to cooler intake fluids normally a part of the same process or cycle;

the term atmospheric gas-turbine regenerator shall relate to a device which partially recovers thermal energy from hot gas turbine exhaust gases that would otherwise be lost on discharge to the atmosphere, by transfer to this themral energy so as to pre-heat the intake air-fluid stream;

the term purge system shall relate to mechanical means of varying the cross-sectional throat area of an atmospheric exhaust nozzle so as to permit periodically a temporary increase of throat area and so permit an increased discharge from the exhaust nozzle, resulting in a consequent reduction of combustion products concentration within the heating fluid intake stream in fluid system branches downstream of the apparatus of the invention which may be caused by recirculation of entrained combustion products.

While the apparatus of the invention is described in connection with gas turbine exhaust energy recovery for the purpose of improving the power plant thermal efficiency of gas turbine plants exhausting to atmospheric pressures, it will be understood by those skilled in the art that similar structures may be employed in connection with other apparatus where regeneration by means of contact interchange between adjacent fluid .eams at different initial pressure is desired.

The primary object of the invention is to provide a r eans of comparatively simple construction whereby tnermal energy present in the exhaust fluid stream of a heat engine, such as a gas turbine, may be partially recovered by means of contact interchange with the cooler, higher-pressure intake fluid stream to the engine.

Another object is the provision of practicable means of contact interchange between the exhaust and intake fluid streams of a gas turbine power plant so as to preheat the intake fluid stream before it enters the combustion chamber or other heat source, thereby decreasing fuel consumption and increasing power plant thermal efficiency.

Another object is to provide a practicable means of achieving contact interchange which will accelerate transfer of thermal energy to conditions approaching thermal equilibrium between the exhaust and intake fluid streams ofa gas turbine, or other heat engine, heat source, or thermal process.

Still another object of the invention is to provide a physically feasible means of effecting contact interchange of thermal and kinetic energy between adjacent fluid streams which are at substantially different initial pressures.

A further object is to achieve a regenerator configuration of comparatively simple construction and compact design which will be suitable for use in connection with mobile gas turbine power plants, and for compact, light-weight gas turbine power plants which may be installed as a fixed installation in remote areas.

With the foregoing objects in view, together with others which will appear as the description proceeds, the invention resides in the novel construction, assemblage, and arrangement of parts which will be described more fully in the discussion illustrated in the drawings, and particularly pointed out in the claims.

In the drawings:

FIG. I is a fragmentary longitudinal sectional view through an apparatus which involves the teachings of the present invention, the same being shown in the form of a gaseous contact heat exchanger, which is installed as part of the apparatus of a gas turbine power plant exhausting to atmospheric pressures for the purpose of effecting an exchange and transfer of thermal energy between the hot, low-pressure gases exhausted from the turbine and the cooler, higher-pressure fluid stream of incoming air being received from a compressor.

FIG. 2 is an exterior end view of the apparatus illustrated in FIG. I.

FIG. 3 is a transverse sectional view along line 3-3 of FIG. I.

FIG. 4 is a transverse sectional view along line 44 of FIG. 1.

FIG. 5 is a schematic sectional diagram of a pistonactuated purge control system for periodically lessening combustion products concentration within fluid system branches downstream of the apparatus of the invention. by a mechanical variation ofthe cross-sectional flow area of an atmospheric exhaust nozzle throat. The purge control apparatus is shown schematically in the extended, or normal operating position.

FIG. 6 is a schematic sectional diagram of the pistonactuated purge control means of FIG. 5 when it is in the retracted, or purge operating position.

FIG. 7 is a schematic process diagram of a gas turbine power plant which incorporates the apparatus of the illustrative embodiment within its flow processes in a conventional manner.

FIG. 8 is a schematic process diagram of a gas turbine power plant which incorporates the apparatus of the illustrative embodiment within its flow processes in an unconventional manner which segregates the combustion process from the power generating process.

FIG. 9 is a schematic sectional diagram of the throat piece operating linkage of FIGS. 5 and 6 when it is actuated by a handoperated power screw. This control means may be used to adjust exhaust nozzle throat pressure to ambient atmospheric pressure without purging for power systems and processes which do not produce solid products of combustion in their combus tion process.

FIG. 10 is a fragmentary longitudinal sectional view through an apparatus having the same application and purpose as the apparatus of Fig. I. Design is based upon an inversion of the apparatus of FIG. 1.

FIG. 1 I is a transverse sectional view taken along line 55 of FIG. 10.

FIG. 12 is a transverse sectional view taken along line 6-6 of FIG. 10.

FIG. 13 is an exterior end view of the apparatus illus trated in FIG. 10, taken along line 7-7.

FIG. 14 is a fragmentary longitudinal sectional view through an apparatus which is a multiple variation of the apparatus illustrated in FIG. 10.

FIG. 15 is an exterior end view of the apparatus illustrated in FIG. 14, taken along line l0l0.

FIG. 16 is an exterior upper view of the apparatus illustrated in FIG. 14, including the terminal outlines of the entering and leaving fluid passages.

FIG. 17 is a transverse sectional view taken along line 88 of FIG. 14.

FIG. 18 is a transverse sectional view taken along line 9 9 of FIG. 14.

FIG. 19 is an exterior end view of the apparatus illustrated in FIG. 14.

FIG. 20 is a fragmentary longitudinal sectional view of a receiver-side sectional which provides means of axially adjusting the linear position of its central annular intake-fluid nozzle member within the receiver-side section.

FIG. 21 is a substantially exterior longitudinal view of the movable compressed intake-fluid supply pipe and annular nozzle member shown in FIG. 20, together with its actuating linkage.

FIG. 22 is an exterior end view taken along line llll of FIG. 21.

FIG. 23 is a fragmentary longitudinal sectional view of a separator-side section which provides means of axially adjusting the linear position of its central annular pre-heated intake fluid discharge member within the separator-side section.

FIG. 24 is a substantially exterior longitudinal view of the movable annular pre-heated intake-fluid discharge member and discharge pipe as shown in FIG. 23, together with its actuating linkage.

FIG. 25 is an exterior end view taken along line 12-l2 of FIG. 24.

FIG. 26 is a fragmentary longitudinal sectional view of a heat exchanger similar to the structure of FIG. I, which provides a slidable connection in the mid-body of the heat exchanger and means of axially adjusting the linear position of the receiver-side annular nozzlediffuser member with respect to the separator-side annular exhaust-fluid discharge member.

FIG. 27 is a fragmentary longitudinal sectional view of a heat exchanger similar to the structure of FIG. 10, which provides a slidable connection in the mid-body of the heat exchanger and means of axially adjusting the linear position of the receiver-side intake-fluid nozzle member with respect to the separator-side annular intake-fluid discharge member.

FIG. 28 is an exterior frontal view of a heat exchanger apparatus which may find use in connection with contact heat exchange between the intake air fluid and exhaust gas streams of a steam generator, furnace or other combustion apparatus FIG. 29 is a fragmentary longitudinal sectional view along line llll of the heat exchanger apparatus illustrated in FIG. 28.

FIG. 30 is an exterior end view along line 12-l2 of the heat exchanger apparatus illustrated in FIG. 28.

FIG. 31 is a transverse sectional view along line l3l3 of the heat exchanger apparatus illustrated in FIG. 29.

FIG. 32 is a transverse sectional view along line l4l4 of the heat exchanger apparatus illustrated in FIG. 29.

FIG. 33 is a modification to the heat exchanger structure of FIG. 28 showing a fragmentary elevation of the receiver-side section wherein pressurized intake fluids supplied by a constant-delivery fan are accelerated within supply ductwork nozzle passageways exterior to the heat exchanger proper, and supplied as highvelocity intake fluids to fluid passageways of the receiver-side section.

FIG. 34 is a fragmentary longitudinal sectional view taken along line l515 of FIG. 33.

FIG. 35 is an exterior end view taken along line 16-16 of the heat exchanger apparatus illustrated in FIG. 33.

FIG. 36 is a modification to the heat exchanger structure of FIG. 33 showing a side elevation of intake-fluid supply ductwork for the receiver-side section through which high-velocity intake fluids are supplied to fluid passageways of the receiver-side section from a rotary fan located exterior to the heat exchanger proper.

FIG. 37 is an exterior end view taken along line l7l7 of the intakefluid supply ductwork illustrated in FIG. 36.

FIG. 38 is a fragmentary sectional modification to the contact heat exchanger structure of FIG. 1 wherein an adjustable coniform flow divider is centrally disposed adjacent the throat section of intake-fluid discharge ductwork to regulate the flow of pre-heated intake fluids through the heat exchanger.

FIG. 39 is a fragmenatary sectional modification to the contact heat exchanger structure of FIG. wherein an adjustable coniform flow divider is centrally disposed adjacent the throat section of intake-fluid discharge ductwork to regulate the flow of pre-heated intake fluids through the heat exchanger.

As indicated earlier herein the present invention involves a physical and mechanical arrangement upon the flow processes of a gas turbine power plant, or other similar processes and heat transfer systems, whereby thermal and kinetic energy may be exchanged in parallel flow between adjacent contacting fluid streams traveling at different velocities and having no physical or mechanical separation between them. More exactly, the invention involves an assemblage of ducting chamber sections and opposted sub-sonic, sonic, or super-sonic nozzle-diffuser configurations and combinations which guide the expansion and contraction of fluids at initially different thermodynamic energy states within their several fluid passages to substantially equal pressure states for the purpose of facilitating the transfer of thermal energy between the several fluid streams by contacting interchange, followed by the reseparation of the several fluid streams after the energy transfer process between the has been completed.

The present invention also involves an assemblage of appropriate entrance and exit configurations to the various ducting chamber sections for the purpose of controlling the physical state of the fluid streams which enter and leave the ducting chamber.

According to the teachings of the present invention, low-pressure turbine exhaust gases, acting as the heat source to intake fluids passing through the apparatus enters the receiver-side section of the ducting chamber and are guided to a minimum-velocity, maximumpressure state by flowing through the interior sub-sonic diffuser passage of a combination nozzle-diffuser member affixed to the exhaust gas entrance pipe or duct within the receiver-side section of the ducting chamber. As shown in the illustrative embodiment of the drawings, the exterior surface of this same nozzlediffuser member together with the interior walls of the receiver-side section comprise an annular nozzle which may have either a convergent or convergent-divergent configuration. The boundaries of the receiver-side nozzle passage serve to guide the expansion of compressed intakes air fluid to a high-velocity, low-pressure state. As the high-velocity intake heating fluid stream (air) and the low-velocity exhaust cooling fluid stream (combusted turbine exhaust gases) leave their respective sides of the adjacent nozzle and diffuser passages within the receiver-side ducting chamber section at substantially equal pressures, the contact interchange of thermal and kinetic energy between the low-velocity exhaust cooling fluid and the high-velocity intake heating fluid will take place in turbulent flow over a characteristic length within the mixing section of the ducting chamber. After thermal expansion of the intake heating fluid stream and thermal contraction of the exhaust cooling fluid stream has taken place over the characteristic length within the ducting chamber mixing section, the combined adjacent fluid streams are again physically divided on passage into a separator-side section of the ducting chamber. The contracted exhaust cooling fluid now passes into convergent nozzle passage for discharge to the atmosphere. The pre-heated intake heating fluid stream (air) plus a small-scale mixture of entrained combustion products from the exhaust cooling fluid stream, still traveling at a high velocity, enters an annular fluid passage comprised of the interior walls of the separator-side section of the ducting chamber and to the outer walls of the convergent atmospheric exhaust nozzle member. The pre-heated intake fluid stream then leaves the separator-side ducting chamber section and enters a diffuser passage of either the subsonic or super-sonic variety, from whence it enters the supply system leading to the combustion chamber. The effect the apparatus of the invention (often called a regenerator) is to decrease the amount of heat energy which must be supplied by the fuel within the combustion chamber to raise the intake fluid streams to the upper operating temperature, and thus improve the thermal efiiciency of the entire gas turbine power plant.

After the high-velocity intake fluid and the lowvelocity exhaust fluid streams leave their respective sides of the nozzle-diffuser member and assume intimate contact with each other, highly complex energy transfer relationships between the adjacent fluid streams will exist in their annular interfacial mixing region. Turbulent flow conditions would exist within the high-velocity intake fluid stream as it leaves the exit lip on the nozzle side of the nozzle-diffuser member. Either laminar, transitional or turbulent flow conditions may exist within the low-velocity exhaust fluid stream as it leaves the exit lip on the diffuser side of the nozzlediffuser member. A violently turbulent annular mixing region at the interface of the adjacent fluid streams would exist downstream of the nozzle-diffuser member due to the large difference in velocity between the adjacent fluid streams. This turbulent annular mixing region is particularly favorable to the rapid transfer of momentum from the high-velocity intake fluid stream to the low-velocity exhaust fluid stream; and to the accelerated transfer of thermal energy from the highertemperature exhaust fluid stream to the lowertemperature intake fluid stream.

The annular region of extreme turbulence induced by the violent interchange of momentum between particles of the high-velocity and low-velocity fluid streams is described as the region of contact interchange. At the present time, the complex mechanism of energy transfer between the adjacent fluid streams is only partly understood by those skilled in the art. it has been the general practice in the art to describe flow condi' tions in a turbulent mixing region in terms of an average velocity plus a fluctuating, time-varying velocity component in the direction of mean flow, together with a fluctuating, time-varying velocity component perpendicular to the direction of mean flow. From this practice has grown theories of turbulent mixing length, concepts of dynamic eddy viscosity for describing momentum interchange in turbulent flow, concepts of eddy diffusivity or eddy heat conductivity for describing the flow of thermal energy across turbulent mixing regions, and other concepts which attempt to scientifically explain mass and energy transport between fluid regions in turbulent flow.

However, it is known from observation, experiment and empirical formulae that highly turbulent mixing zones are extremely favorable for accelerated transfer of thermal energy between adjacent fluid regions.

lt should be understood that the fundamental approach to the problem of achieving contact interchange between fluid streams at substantially different thermodynamic energy states and pressures consists of the following stages:

1. Conversion of intake fluid pressure energy to maximum kinetic energy 2. Conversion of exhaust fluid kinetic energy to maximum effective pressure energy 3. Bringing the intake and exhaust fluid streams into physical contact at substantially equal pressures in parallel flow with respect to each other within the confines of a closed plenum or ducting chamber. The object of this stage is to divide flow within the mixing section of the ducting chamber into fluid laminae having greatly different moments.

4. After the energy transfer between the contacting fluid streams is substantially complete, the greatly different momenta of the fluid laminae is utilized to effect a substantial physical separation of the intake and exhaust fluid streams within the separator'side section.

5. The separated fluid streams are then discharged from the separator-side section of the ducting chamber.

Another teaching of the present invention involves an inversion of the design arrangements previously described, which attains similar effects and advantages by means of somewhat different arrangements and related configurations. Low pressure turbine exhaust gases,

acting as heat source to compressed intake fluids (air) passing through the apparatus are guided to a minimum-velocity maximum-pressure state by flowing through an exterior sub-sonic diffuser passage communicating with the receiver-side section of the ducting chamber. The compressed intake fluids are routed into the interior nozzle passage of a central nozzle member by means of a connecting intake fluid supply pipe that pierces the endwall of the receiver-side section, and expanded within the nozzle passage to a high-velocity, low-pressure state. As shown in the drawings, diffused turbine exhaust gases enter the ducting chamber and flow into an annular fluid passage bounded by the exterior walls of the central receiver-side nozzle member and the interior walls of the receiver-side section. The central nozzle passage defined by the interior walls of the receiver-side nozzle member may have either a convergent or converge nt-divergent configuration. The adjacent fluid streams leave their respective sides of the receiver-side nozzle member at substantially equal pressures, and flow into the mixing section of the ducting chamber in intimate contact with each other. The contact interchange process takes place as previously described within the mixing section. The large difference in momenta between the intake and exhaust fluid stream is again used to effect separation within the separatorside section of the ducting chamber. The greater inertia of the pre-heated intake fluid stream now carries it substantially past the leading edge of a converging discharge member into a central fluid passage, to which is connected a discharge pipe piercing the confining boundaries of the separator-side section and leading to processes downstream of the invention. The cooled exhaust fluid stream substantially passes into an annular fluid passage bounded by the exterior walls of the separator-side discharge member and the interior walls of the separator-side section, from whence it is exhausted frm the apparatus of the inventron.

As stated earlier herein, it is among the objects of the present invention to provide a feasible means of achieving contact interchange which will accelerate transfer of thermal energy to conditions approaching thermal equilibrium between the exhaust and intake fluid streams of a gas turbine, or other heat engine, heat source or thermal process. This objective is achieved by an initial large-scale conversion of intake fluid pressure energy to kinetic energy, which in tum-aids the es tablishment of a highly turbulent mixing region between the adjacent fluid streams within the ducting chamber mixing section. It is this violent turbulence, largely induced by the high-velocity intake fluid stream, which will accelerate the large scale transfer of thermal energy from the hot exhaust fluid stream to the relatively cool intake fluid stream. Due to the large velocity difference between the adjacent fluid streams,

it is expected that both the mixing and characteristic lengths over which energy transfer is substantially complete will be of modest dimension.

If the contact regenerators described were part of a gas turbine power plant which combusted ordinary refinery fuels, particularly of the heavy residual variety, the concentration of combustion products within the working fluid branch serving the gas turbine would slowly increase. This increase in combustion products concentration within the working fluid branch serving the gas turbine would occur because combustion products entrained in the region of contact interchange would be partially recirculated through the gas turbine rather than being discharged directly to the atmosphere. The rising combustion products concentration in the working fluid stream serving the turbine would result in the build-up of heavy deposits on the blade surfaces of the gas-generator turbine and upon surfaces within the combustion chamber, since solid combustion products would tend to adhere to surfaces in the hotter parts of the thermal process as the solids products melting points are approached. The present invention results in several ways of avoiding this problem, such as:

l. A purge control method of temporarily increasing atmospheric exhaust nozzle throat area which will evacuate excessive concentration of combustion products from the working fluid branch serving the gas turbine.

II. A segregation method of arranging gas turbine power plant flow processes which is schematically presented in FIG. 8. This arrangement differs from the more conventional schematic flow process of FIG. 7 in that the regenerator is the sole direct heat source for both the gas-generator turbine and free turbine, and that major quantities of heat energy are added to the exhaust fluid stream by a downstream combustor after expansion of the working fluid has taken place within the turbines. In this method, all but a small percentage of the products of combustion are discharged directly to the atmo sphere without passing through the turbines.

It is expected that method I, referred to immediately hereinbefore, or a combination of methods I and ll will entirely relieve the solid products deposit problems as it occurs in ordinary practice.

Still another teaching of the present invention involves the arrangement of a plurality of central receiver-side nozzle members within the receiver-side section of an integral plenum or ducting chamber opposing a plurality of converging discharge members within the separator-side section. This multiple version would be useful for effecting contact interchange between the intake and exhaust fluid streams of power plant apparatus involving very large flow rates. As shown in the drawings, the plurality of central receiver-side nozzle members is supplied from a common compressed intake fluid receiver through a plurality of supply pipes which pierce the confining boundaries of the receiverside section. Hot low-pressure exhaust gases, acting as the heat source to the compressed intake fluids passing through the apparatus, enter the fluid passage defined by the exterior surfaces of the plurality of receiver-side nozzle members and their supply pipes together with the interior walls of the receiver-side section of the ducting chamber. The expansion of the compressed in' take fluid streams within the receiver-side nozzle passages to a high-velocity low-pressure state takes piace as previously described. The contact interchange process takes place along the plurality of interfacial mixing regions within the mixing section, and the larger inertias of the pre-heated intake fluid streams are again used to separate the intake and exhaust fluid streams within the separatonside section. The pre-heated intake fluid streams are substantially diverted into the plurality of opposed and converging discharge members, which have connecting pipes that pierce the con fining boundaries of the separator-side section. The

cooled exhaust fluid stream is substantially diverted into the fluid passage defined by the exterior surfaces of the plurality of converging separator-side discharge members and their supply pipes together with the interior walls of the separator-side section. The pre-heated intake fluid streams are thence routed to processes downstream of the invention, while the cooled exhaust fluid stream is exhausted from the ducting chamber.

Thermodynamic properties of intake fluids (air) entering regenerative atmospheric gas turbine power plants would vary in accordance with ambient atmospheric conditions. This continuing change in the thermodynamic properties of air intake fluids would be reflected as minor variations in the linear dimension of characteristic length over which contact interchange takes place within the regenerative apparatus of the invention. Effective local adjustments between the rcceiver-side annular nozzle member and the separatorside annular discharge member to the optimum charao teristic length becomes necessary to limit formation oof normal shock waves in supersonic flow across the leading edge of the annular discharge member of the separator-side section.

Yet another teaching of the present invention involves means of adjusting linear position of the central annular nozzle member within the receiver-side section with respect to the leading edge of its corresponding opposite central annular discharge member of the separator-side section. This arrangement permits local adjustments to the optimum characteristic length di mension within the mixing section of the heat exchanger in accordance with variable atmospheric conditions. The linear position of the central annular discharge member within the separatorside section may be alternately adjusted with respect to the trailing edge of its corresponding opposite central annular nozzle member of the receiver-side section to provide equivalent variable adjustment to optimum characteristic length. The method described for effecting local adjustment to the optimum characteristic length dimension may be applied to either the central annular nozzle members of the receiver-side section or the central an nular discharge members of the separator-side section in any of the heat exchangers disclosed in connection with either of FIGS. 1, 10 or 14.

Certain types of gas turbines exhausting to atmospheric pressures which do not produce solid products in their combustion process, such as alcoholfired tur bines, will not require periodic purging of recirculated and entrained combustion products from the working fluid branch serving the gas turbine. Such gas turbine power plants will require a method of adjusting exhaust nozzle throat area so that exhaust nozzle pressure will not exceed atmospheric pressure. The operating linkage of FIGS. 5 and 6 may be actuated by a handoperated power screw as schematically presented in the sectional diagram of FIG. 9. in this variation, the movable fulcrum pin of the lever together with the operation of the threaded force rod combine to compose an adjustable positioning system which flexibly holds the conical throat piece in a desired position with respect to the atmospheric exhaust nozzle throat so as to effec tively control the cross sectional flow area of the exhaust nozzle.

Heat energy may also be admntagcously transferred between the intake air-fluid and exhaust gas streams of a steam generator, furnace or other similar combustion apparatus by means of the contact-type heat exchanger illustrated in FIGS. 28, 29, 30, 3] and 32. In this apparatus, pressurized intake air is supplied by a forced draft fan and expanded in sub-sonic nozzle passageways of the heat exchanger. The high-velocity intake air-fluid stream and the hot low-velocity exhaust gas stream are each divided into several adjacent alternately contacting fluid streams in parallel flow with respect to each other. Following the contact interchange process, the heated intake fluid streams and the cooled exhaust gas streams are substantially separated from each other. The apparatus shown in H68. 28, 29, 30, 3l and 32 would be described in the art as a contacttype air preheater for a steam generator or furnace.

Referring more particularly to the accompanying drawings, FIG. I specifically illustrates a longitudinal section of the invention in the form of an atmospheric gas turbine regenerator which is part of the apparatus of an atmospheric gas turbine power plant. ln this atmospheric gas turbine regenerator compressed air enters intake fluid supply pipe 8 having a socket flange 9 secured thereto. From this intake fluid supply pipe 8 the compressed air flows into optional sub-sonic diffuser section 11 which is fitted with an entrance flange l and an exit flange 12. The compressed intake airfluid then passes through an entrance flange l3 and into receiver-side ducting chamber section 14. As shown, this receiver side ducting chamber section 14 is provided with an exit flange 15 which is angularly disposed with respect to its entrance flange 13.

The receiver-side ducting chamber section 14 receives hot sub-sonic exhaust gases from the exhaust fluid supply pipe 16 of the turbine or combustor which is centrally disposed therein, extending through the adjacent end wall as shown.

Within the receiver-side ducting chamber section 14, and concentrically disposed with respect thereto is an annular nozzle-diffuser member 17 which is connected to exhaust fluid supply pipe 16 and stabilized by intermediately disposed bracket or spider member 18. The inner surface of the annular nozzle-diffuser member 17 is outwardly flared and defines a diverging sub-sonic diffuser passage 22, wherein the hot exhaust fluid is guided to a thermodynamic energy state of maximum pressure and minimum velocity.

The space between the outer surface of the annular nozzle-diffuser member 17 and the interior of the receiver-side ducting chamber section 14 defines an annular super-sonic nozzle composed of convergent subsonic fluid passage 19, annular sonic fluid passage 20, and divergent annular super-sonic fluid passage 21. The purpose of the annular super-sonic nozzle composed of the successive fluid passages 19, 20 and 21 is to guide the expansion of the compressed intake fluid stream until the pressure at the exit lip of the annular super-sonic nozzle is substantially equal to the pressure on the inner side of the nozzle-diffuser member 17, the said exit lip terminating at the end of the subsonic diffuser passage 22.

The expanded intake fluid stream leaves the exit lip of the fluid passage 21 traveling at super-sonic speed, while the compressed exhaust fluid stream leaves the exit lip of the diffuser passage 22 traveling at a low subsonic speed. As the adjacent high-velocity intake fluid stream and the low-velocity exhaust fluid stream leave the nozzle diffuser member 17 on their respective sides of the exit lip, a violent contact interchange of kinetic .snamnmhhanr.kum-isw... nu-A and thermal energy takes place with turbulent mixing along the interface between the adjacent fluid streams.

The exit flange 15 of the receiver-side section 14 is connected to the entrance flange 23 of a cylindrical mixing section 24, the latter being also provided with an exit flange 25.

The aforementioned contact interchange of kinetic and thermal energy between the adjacent fluid streams largely takes place within the boundaries of the mixing section 24. The outer intake heating fluid stream expands within the annular fluid passage region 26 of the mixing section as the thermal energy flows across the annular region of contact interchange, while the inner exhaust cooling fluid stream contracts within the fluid passage region 27 of the mixing section as thermal energy is transferred from the exhaust fluid stream.

The process of contact interchange is substantially complete as the intimately associated fluids leave the outlet of the mixing section 24.

The exit flange 25 of the mixing section 24 is connected to the entrance flange 28 of the separator-side section 29, the latter being also provided with an exit flange 30.

After the intimately associated fluids leave the mixing section 24, they pass into the separator-side section 29 of the ducting chamber and the fluid streams are again divided. Centrally disposed within the separatorside section 29 there is a frusto-conical atmospheric exhaust nozzle member 3], the convergent end of which terminates in a cylindrical throat section 34 which extends through and projects from the adjacent endwall of the separator-side section. Adjacent its larger end the frusto-conical atmospheric exhaust noule member 31 is stabilized by bracket or spider members 32.

From the foregoing it will be perceived that the inner exhaust fluid stream enters the converging nozzle passage 33 and exits at atmospheric pressure from the cylindrical throat 34 at the convergent end of the frustoconical exhaust nozzle member 31. The outer, annular pre-heated intake fluid stream passes into the diverging passage formed by the inner walls of separator-side ducting chamber section 29 and the outer walls of the frusto-conical exhaust nozzle member 31.

Referring to the right-hand side of FIG. 1, a conical divider or throat piece 35 is disposed to extend axially into the exhaust noule throat 34, the same being mounted on the end of a slidable control rod 37 and secured by a lock nut 36.

The slidable control rod 37 is mounted to extend through an annular collar 38, the latter being provided with a bushing 39.

This annular collar 38 is supported by a bracket or spider 40 which will be referred to hereinafter.

To the outer end of the separator-side section 29 of the ducting chamber there is secured the annular end flange 41 of the exhaust duct 42, the other end of said exhaust duct being provided with an exterior boss 43 having a bushing 44 extending therethrough.

The bracket or spider 40 which supports the slidable control rod 37 is secured to the interior walls of the exhaust duct 42 and the outer end of said rocl extends through and projects from the bushing 44 in the exterior boss 43 on the outer end of the exhaust duct 42.

According to the foregoing construction and arrangement the concial divider or throat piece 35 may be retracted to purge control position 35' which is clear of the throat 34 of the atmospheric exhaust nozzle 31 when the slidable control rod 37 is caused to retract along the longitudinal axis of the ducting chamber by variable force F (see right-hand end of FIG. 1). The temporary increase in cross-sectional flow area occasioned by the retraction of the conical throat piece 35 (to purge control position 35') permits an increased discharge of cooled exhaust gases to the atmosphere through the exhaust duct exit 46 and a consequent purging of the entrained combustion products which may be recirculated within fluid system branches downstream of the apparatus of the invention, as will be understood by those skilled in the art.

As also shown in FIG. 1, the pre-heated intake fluid stream passes through the exit flange 30 of the separa tor-side section 29 and through the entrance flange 47 of the aforementioned optional diffuser section 48, the latter being also provided with an exit flange 49. While flow conditions may be either sub-sonic or super-sonic at this point depending upon the design parameters chosen for a particular installation, flow velocity is assumed to be supersonic for the purposes of the present illustrative disclosure.

The optional diffuser section 48 is shown as being of inverted frusto-conical shape and its interior walls 50 provide a convergent super-sonic diffuser passage 51 and a lower cylindrical sonic diffuser throat section 52.

Exit flange 49 of the converging super-sonic diffuser member 48 is connected to the entrance socket flange 53 of intake fluid discharge pipe 54.

The pressure drop resulting in moving over the relatively short length of the interior walls 55 of the combustor supply pipe 54 will be sufficient to insure a slightly sub-sonic velocity; accordingly a diverging diffuser section might be added to the combustor supply pipe 54 downstream with respect to the entrance socket flange 53 should a further reduction of the preheated intake fluid stream velocity be desired before entering a combustion chamber.

An additional variation for regulating the flow of intake fluids through the contact heat exchanger structure of FIG. 1 is disclosed in the illustrative embodiment of FIG. 38. In FIG. 38 exit flange 49 of optional super-sonic diffuser section 48 (FIG. 1) connects to socket flange 311, the same housing annular sonic throat section 312. Annular sonic throat section 312 is secured by welding or other suitable means to annular sub-sonic diffuser section 313, which is similarly secured to intake-fluid discharge conduit 314. Coniform flow divider or throat piece 317 is suitably attached to the end of slidable control rod 318 and disposed centrally of annular sonic throat section 312 and annular diffuser section 313. Slidable control rod 318 extends through bushing 321 and annular collar 320 of spider assembly 319 (attached to discharge conduit 314), and through bushing 322 and exterior duct boss 315. Variable force F acting on slidable control rod 318 as shown may adjust coniform flow divider or throat piece 317 to any position along the control axis with respect to annular throat section 312 or diffuser section 313. Throat control assembly 317-318 may be actuated by the adjustable pneumatic control apparatus of FIGS. and 6, or by other suitable means.

Intake-fluid discharge throat control assembly 317-318 inclusive and exhaust-fluid throat control as sembly 35-37 may be joinly operated by their respective control apparatuses to dampen pressure fluctuations within the contact heat exchanger, or to regulate the contact interchange process.

The schematic diagram of FIG. 7 represents the application of the invention to the thermodynamic processes of an atmospheric gas turbine power plant. Atmospheric air at thermodynamic energy state 56 enters a compressor 57 (driven by the shaft member 66 of the gas-generator turbine 64) where it is compressed to thermodynamic energy state 58. The compressed intake air then enters the regenerative apparatus of the invention (59) where it is pre-heated by contact interchange in parallel flow with the hot exhaust gases of free turbine 67. The pre-heated intake fluid stream leaves the regenerative apparatus of the invention (59) at thermodynamic energy state 60. The pre-heated intake fluid stream then enters combustion chamber 61 where fuel is injected at thermodynamic energy state 62, and combustion then proceeds within the combustor. The high-temperature combusted fluid stream leaves combustion chamber 61 at thermodynamic energy state 63 and is expanded in gas-generator turbine 64 (having a shaft member 66 which drives the compressor S7). The combusted fluid stream leaves the gasgenerator turbine 64 at thermosdynamic energy state 65, and is further expanded in free turbine 67 having a shaft member 70 which drives an alternator 71 or other work-absorbing device. The combusted fluid leaves the free turbine 67 at thermodynamic energy state 68, and enters the aforementioned regenerative apparatus of the invention (59) in a parallel flow direction with the intake fluid stream traveling between thermodynamic energy states 58 and 60.

Within the regenerative apparatus of the invention (59) the combusted exhaust fluid stream is cooled by contact interchange in parallel flow with the intake fluid stream, and discharged to atmosphere at thermodynamic energy state 69.

The schematic diagram of FIG. 8 represents a novel application of the apparatus of the invention to the thermodynamic processes of an atmospheric gas turbine power plant. wherein the blading of the turbines is substantially protected from fouling by deposit of the products of combustion. All of the initial heating of intake air-fluid is accomplished within the regenerative apparatus of the invention (59) and the combustion process is entirely carried out in the free turbine exhaust fluid stream. .Save for a small amount of entrained combustion products within the pre-heated intake fluid stream, no combustion products will pass directly through the gas-generator turbine 64 or the free turbine 67. The fouling of blading surfaces within the turbines by deposit of the products of combustion is thus bypassed almost entirely by the method of segregation.

Referring still to FIG. 8, atmospheric air at thermodynamic energy state 56 enters compressor 57 (driven by the shaft member 66 of the gas-generator turbine 64) where it is compressed to thermodynamic energy state 95. The compressed intake air stream then enters the regenerative apparatus of the invention (59) where it is pre-heated by contact interchange in parallel flow with the high-temperature exhaust gases from combustion chamber 61. The pre-heated intake fluid stream leaves the regenerative apparatus of the invention (59) at thermodynamic energy state 96, and is then expanded in gas-generator turbine 64 (driving compressor 57, etc.). The pre-heated fluid stream leaves gasgenerator turbine 64 at thermodynamic energy state 97, and is then further expanded in free turbine 67 (having shaft member 70 which drives alternator 71 or other work-absorbing device). The expanded fluid stream leaves free turbine 67 at thermodynamic energy state 98, and enters the combustion chamber 61. Within the combustion chamber 61 fuel is injected at thermodynamic energy state 99, and the combustion process proceeds therewithin. The combusted hightemperature exhaust fluid stream leaves the combustion chamber 61 at thermodynamic energy state 100, and enters the regenerative apparatus of the invention (59) in parallel flow with the intake fluid stream traveling between thermodynamic energy states 95 and 96. Within the regenerative apparatus of the invention (59) the combusted exhaust fluid stream is cooled by contact interchange in parallel flow with the intake fluid stream, and then discharged to atmosphere at thermodynamic energy state 101.

FIG. 5 is a schematic diagram partially in section, of a piston-actuated control system for carrying out the purging operation on a cyclical basis. In this figure the pneumatic control system is illustrated when it is approaching the normal operating position, wherein the conical flow divider or throat piece 35 would be nearly disposed in the correct position with respect to exhaust nozzle throat 34 of the atmospheric exhaust nozzle member 31. As shown, the slidable control rod 37 carries a yoke fitting 72 which houses a yoke pin 73. A lever 74 is provided with a guide slot 75 for receiving the yoke pin 73; and in this manner the motion of the lever 74 is transmitted to the slidable control rod 37.

The lever 74 pivots about an adjustable fulcrum pin 76 and has a guide slot 77 within which a yoke pin 78 is slidably disposed. This yoke 78 is housed in a yoke fitting 79 and the adjustable fulcrum pin 76 is housed by a traveler member 80 which is threaded onto a power screw member 81. This power screw member 81 is housed in machine-frame socket member 82 by a suitable sleeve-type bushing, and in machine-frame bearing member 83 by sleeve-type bushing and thrust collars. A handwheel 84 rotates this power screw member 81 to cause the traveler member 80 to advance or retract along the threaded shaft, thus adjusting the linear position of the fulcrum pin 76.

The yoke fitting 79 is secured to the piston rod 85 of a pneumatic double-acting piston 86 which is disposed in a cylinder 87, and in this manner the movement of said piston is transmitted to the slidable control rod 37.

The numerals 88 and 89 designate pipe branch members which are connected to the upper and lower lefthand orifices of a four-way valve 90.

A pneumatic supply pipe 91 is connected to the upper right-hand orifice of the four-way valve 90, and an exhaust pipe 92 is connected to the lower right-hand orifice thereof.

A solenoid 93, forming part of an electrical pilot circuit 94, may be utilized to control the operation of the double-acting piston 86 in the cylinder 87. When the solenoid 93 is de-energized, compressed air will flow from the pneumatic supply pipe 91 into the upper righthand orifice of the four-way valve 90 into the pipe branch member 88 with the direction of flow indicated by the arrows. in this manner the compressed air enters the cylinder 87 to act upon the rod face of piston 86, causing the piston to move to the right as viewed in the drawings. This movement of the piston 86 exhausts low-pressure air from the cylinder 87 into the pipe branch member 89, which communicates with the lower left-hand orifice of the four-way valve 90. Exhausted air then flows through the four-way valve into the exhaust pipe 92 (which communicates with the lower right-hand orifice of the four-way valve), from whence the exhaust air leaves the pneumatic control system.

it will be understood that the installation of an additional cross-over valve connection between the pneumatic supply pipe 91 and the exhaust pipe system 92 downstream of the aforementioned four-way valve plus a stop valve fitting within the exhaust pipe 92 system downstream of said crossover valve connection will permit the pneumatic control system to hold the piston 86 in any desired operating position within the cylinder 87.

FIG. 6 is a schematic diagram, partly in section, of the pneumatic purge control system, wherein the apparatus of the control system is shown as nearing the retracted purge operating position. The movement of the piston 86 within the cylinder 87 is now disclosed as opposite to that illustrated in FIG. 5; and the control system linkage has retracted the conical throat piece 35 form the exhaust nozzle throat 34.

According to FIG. 6, the solenoid 93 has been energized by the electrical pilot circuit 94, thereby actuating the four-way valve 90 to cross-route the compressed air supply from the pneumatic supply pipe 91 to the pipe branch member 89. Thus, the compressed air enters the cylinder 87 to act upon the head face of the piston 86, causing the piston to move within the cylinder 87 to the left as illustrated. This movement of the piston 86 exhausts low-pressure air from the cylinder 87 into the pipe branch member 88. The exhausted low-pressure air is then cross-routed from the pipe branch member 88 to the pneumatic exhaust pipe 92 by the four-way valve 90, from whence the exhaust air leaves the pneumatic control system.

In this connection, it will be understood that the installation of an additional crossover valve connection between the pneumatic supply pipe 91 and the pneumatic exhaust pipe 92, together with a stop valve fitting within the exhaust pipe system 92 downstream of the additional crossover valve connection will permit the pneumatic control system to hold the piston 86 in any desired operating position within the cylinder 87, when said stop and crossover valves are jointly operated.

FIG. 9 is a schematic diagram of the throat piece operating linkage of FlGS. 5 and 6 (ie adjustable lever type) as actuated by a hand operated power screw. This form of throatpiece control apparatus may be utilized to insure that exhaust nozzle discharge and throat pressures are adjusted to the optimum conditions consistent with ambient atmospheric conditions, simply by adjusting the position of the conical throat piece 35 with respect to the exhaust nozzle throat 34. According to this embodiment there is no provision for a cyclic retraction of the conical throat piece 35 form the exhaust nozzle throat 34 as occurs in the purge control apparatus illustrated in FIGS. 5 and 6, since the handoperated type is for use in connection with the regener' ative apparatus of gas turbine power plants exhausting to atmospheric pressures and which do not produce solid combustion products in their combustion process.

Rotation of the handwheel imparts similar movement to the power screw shaft member 103 within the threaded machine-frame housing 104, causing the power screw shaft member to advance or retract with respect to the said machine-frame housing. The end of the power screw shaft member 103 opposite to that carrying the handwheel 105 is fitted with a tuned and necked end which may rotate freely within the socket member 102 which is affixed to the yoke fitting 79. The power screw shaft member 103 may be additionally stablized by a sleeve-type bushing housed in an additional machine-frame bearing member, or by other suitable means. The lever-type linkage of P16. 9 functions similarly to the lever-type linkage of FIGS. and 6 when the double-acting piston 86 is held in a fixed position, wherein the position of the conical throat piece 35 is adjustable by both the actuating power screw shaft member 103 and the fulcrum screw shaft member 81 acting separately or in conjunction with each other.

FIG. specifically illustrates a longitudinal section of the invention in the form of an atmospheric gas turbine regenerator whose design represents an inversion of the illustrative embodiment of FIG. 1. Hot lowpressure turbine exhaust gases enter exhaust fluid sup ply pipe 106, which is fitted with exit flange 107. Exit flange 107 of exhaust fluid supply pipe 106 is connected to entrance flange 108 of diffuser member 109, the latter also being provided with exit flange 110. The hot-low pressure exhaust gases flow from supply pipe 106 into an interior diffuser passage of diffuser member 109 defined by interior walls 111, where they are guided to a minimum-velocity, maximum pressure state. Exit flange 110 of diffuser member 109 is connected to entrance flange 112 of receiver-side section 113, the latter also being provided with angularly disposed exit flange 114. The compressed exhaust gases pass from diffuser member 109 into receiver-side section 113 through its entrance flange 112.

Receiver-side ducting chamber section 113 receives compressed intake fluid (air) from intake fluid supply pipe 115, which is centrally disposed and extends through the adjacent endwall as shown.

Within receiver-side ducting chamber section 113 and concentrically disposed with respect thereto is an annular nozzle member 116, which is connected to intake fluid supply pipe 115 and stabilized by intermediately disposed bracket or spider members 117. The inner surface of receiver-side nozzle member 116 defines the boundaries of a convergent-divergent nozzle composed of sub-sonic nozzle passage 1 18, sonic nozzle passage 119 and super-sonic nozzle passage 120. Within the receiver- side nozzle passage 118, 119 and 120, the compressed intake fluid stream is guided and expanded to a high-velocity, low-pressure state. The space between the outer surface of annular nozzle member 116 and the interior walls of receiver-side section 113 composes an annular fluid passage 121, which is in turn supplied with compressed exhaust gases from diffuser member 109. The purpose of the super-sonic nozle composed of successive fluid passages 118, 119 and 120 is to guide the expansion of the compressed intake fluid stream until the pressure at the exit lip of the super-sonic nozzle is substantially equal to the pressure of the hot exhaust gases on the outer side of annular nozzle member 116 in exhaust fluid passage 121.

The expanded intake fluid stream leaves the exit lip of fluid passage 120 traveling at super-sonic speed, while the compressed exhaust fluid stream leaves annular exhaust fluid passage 121 traveling at a low subsonic speed. As the adjacent high-velocity intake fluid stream and the low-velocity exhaust fluid stream leave annular nozzle member 116 on their respective sides of the exit lip, a violent contact interchange of kinetic and thermal energy takes place with turbulent mixing along the annular interface between the adjacent fluid streams.

The adjacent intake and exhaust fluid streams leave receiver-side section 113 and pass into mixing section 123, which is fitted with entrance flange 122 and exit flange 124. Exit flange 114 of receiver-side section 113 is connected to entrance flange 122 of mixing section 123.

The previously mentioned contact interchange of thermal and kinetic energy between the adjacent fluid streams largely takes place within the boundaries of mixing section 123. The inner high-velocity intake heating fluid stream expands within the inner fluid passage region 126 of the mixing section as thermal energy flows across the annular interfacial region of contact interchange, while the outer exhaust cooling fluid stream contracts within annular fluid passage region of the mixing section as thermal energy is transferred from the exhaust fluid stream. The process of contact interchange is substantially complete as the intimately associated fluid streams leave the outlet of mixing section 123.

Exit flange 124 of mixing section 123 is connected to entrance flange 127 of separator-side section 128, the latter being provided with angularly disposed exit flange 129.

After the intimately associated fluid stream leave the mixing section 123, they pass into separator-side section 128 of the ducting chamber and the fluid streams are again divided. Centrally disposed within separatorside section 128 there is a frusto-conical discharge member 130, the convergent end of which is connected to discharge pipe member 131, which in turn pierces the endwall of separator-side section 128. The substantially greater inertia of the pre-heated intake fluid stream carries it past the entrance lip of separator-side discharge member 130 into convergent fluid passage 132 defined by the interior walls of the aforesaid discharge member. Adjacent its larger end. the convergent discharge member 130 is stabilized by intermediately disposed bracket or spider members 133. The pre-heated intake fluid stream is discharged from discharge fluid passage 132 through discharge pipe 131 from the ducting chamber to processes downstream of the invention.

After passing the entrance lip of separator-side discharge member 130, the cooled exhaust fluid stream enters the converging annular exhaust fluid passage 134, defined by the exterior surfaces of the convergent discharge member 130 and its connecting discharge pipe 131 together with the converging interior walls of the separator-side section. It should be particularly noted that the walls of separator-side section 128 converge from the inlet at the entrance flange 127 to the outlet at the angularly disposed exit flange 129.

Exit flange 129 of separator-side section 128 is connected to entrance flange 142 of atmospheric exhaust duct 144, from which the cooled exhaust fluid is finally exhausted to the atmosphere.

The reduction in cross sectional exhaust fluid flow area within the separator-side section composes an effective convergent exhaust nozzle which terminates in

Claims (26)

1. A non-reversing single-pass fluid-to-fluid contact heat exchanger adapted to receive and exchange energy between a plurality of fluid streams at different thermodynamic energy states in parallel flow with respect to each other; said contact heat exchanger comprising a substantially closed plenum or ducting chamber defined by side and confining walls and providing receiver-side, mixing and separator-side sections, said mixing section disposed in said ducting chamber between the receiverside and separator-side sections thereof; intake and exhaustfluid passageways disposed within both the aforesaid receiverside and separator-side ducting chamber sections, the boundaries of the said intake and exhaust-fluid passageways being defined by the interior walls of said ducting chamber and the surfaces of annular internal fluid flow control members of substantially lesser cross section than aid disposed centrally of both their respective receiver-side and separator -side sections; an intakefluid supply pipe(s) or duct(s) in communication with the receiver-side intake-fluid passageway(s), and supplying intake fluids thereto; and exhaust-fluid supply pipe(s) or ducts(s) in communication with the receiver-side exhaust-fluid passageway(s) and supplying hot, low-pressure exhaust fluids thereto; an intake-fluid discharge pipe(s) or duct(s) in communication with the separator-side intake fluid passageway(s) and receiving heated intake fluids therefrom; and an exhaust-fluid discharge pipe(s) or duct(s) in communication with the separator-side exhaust-fluid passageway(s) and receiving cooled exhaust fluids therefrom; whereby particles of the aforesaid intake-fluid and exhaust-fluid streams aare brought into physical contact with each other within said mixing section at substantially equal pressures while possessing substantially unequal and parallel velocity vectors so as to facilitate the contact interchange of thermal and kinetic energy therebetween, followed by a reseparation of the aforesaid intake and exhaust-fluid streams within the separator-side section of said contact heat exchanger after the contact interchange process has been substantially completed.

2. A non-reversing single-pass fluid-to-fluid contact heat exchanger adapted to receive and exchange energy between a plurality of fluid streams at different thermodynamic energy states in parallel flow with respect to each other; said contact heat exchanger comprising a substantially closed plenum or ducting chamber definEd by side and confining walls and providing receiver-side, mixing and separator-side sections, said mixing section disposed in said ducting chamber between the receiver-side and separator-side sections thereof; an annular nozzle member of substantially lesser cross section than and disposed centrally of said receiver-side section whose outer surfaces and the walls of the receiver-side section define an annular intake-fluid nozzle passageway discharging to said mixing section, and whose inner sufaces defines an exhaust-fluid passageway discharging to said mixing section; an intake-fluid supply pipe or duct in communication with the annular enveloping intake-fluid nozzle passageway of the receiver-side section and supplying compressed intake fluids thereto; an exhaust-fluid supply pipe or duct in communication with the central exhaust-fluid passageway of the receiver-side section and supplying hot, low-pressure exhaust fluids thereto; whereby particles of the aforesaid intake-fluid and exhaust-fluid streams are brought into physical contact with each other within said mixing section at substantially equal pressures while possessing substantially unequal and parallel and velocity vectors so as to facilitate the contact interchange of thermal and kinetic energy therebetween; an annular discharge member of substantially lesser cross section than and disposed centrally of said separator-side section whose outer surfaces and the walls of the separator-side section define an annular intake-fluid discharge passageway receiving heated intake fluids from said mixing section, and whose inner surfaces define an exhaust-fluid discharge passageway receiving cooled exhaust fluids from said mixing section, whereby the leading edge of said annular discharge member serves as a flow divider to separate the intake-fluid and exhaust-fluid streams from each other after the contact interchange process as flows proceeds from the mixing section into said separator-side section; an intake-fluid discharge pipe or duct in communication with the annular enveloping intake-fluid discharge passageway of the separator-side section and receiving heated intake fluid therefrom; and an exhaust-fluid discharge pipe or duct in communication with the central exhaust-fluid discharge passageway of the separator-side section whereby cooled exhaust fluids may be discharged from the apparatus of the invention.

3. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 2 wherein the annular nozzle member is disposed coaxially with the receiver-side section along the flow axis thereof.

4. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 2 wherein the annular discharge member is disposed coaxially with the separator-side section along the flow axis thereof.

5. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 2 wherein a coniform flow divider is disposed axially of an exhaust-fluid discharge aperture supplied by the said central exhaust-fluid discharge passageway of the separator-side section and directed against the discharge of cooled exhaust fluids therefrom, and means for axially advancing and retracting the said coniform flow divider with respect to the said exhaust-fluid discharge aperture.

6. A non-reversing single-pass fluid-to-fluid contact heat exchanger adapted to receive and exchange energy between a plurality of fluid streams at different theremodynamic energy states in parallel flow with respect to each other; said contact heat exchanger comprising a substantially closed plenum or ducting chamber defined by side and confining walls and providing receiver-side, mixing and separtor-side sections, said mixing section disposed in said ducting chamber between the receiver-side and separator-side sections thereof; an annular nozzle member of substantially lesser cross section than and disposed centrally of said receiver-side section whose inner surfaces define a central intake-fluid nozzle passageway discharging to said mixing Section, and whose outer surfaces and the walls of the receiver-side section define an annular exhaust-fluid passageway discharging to said mixing section; an intake-fluid supply pipe or duct in communication with the central intake-fluid nozzle passageway of the receiver-side section and supplying compressed intake fluids thereto; an exhaust-fluid supply pipe or duct in communication with the annular enveloping exhaust-fluid passageway of the receiver-side section and supplying hot, low-pressure exhaust fluids thereto; whereby particles of the aforesaid intake-fluid and exhaust-fluid streams are brought into physical contact with each other within said mixing section at substantially equal pressures while possessing substantially unequal and parallel and velocity vectors so as to facilitate the contact interchange of thermal and kinetic energy therebetween; an annular discharge member of substantially lesser cross section than and disposed centrally of said separator-side section whose inner surfaces define a central intake-fluid discharge passageway receiving heated intake fluids from said mixing section, and whose outer surfaces and the walls of the separator-side section define an annular exhaust-fluid discharge passageway receiving cooled exhaust fluids from said mixing section, whereby the leading edge of said annular discharge member serves as a flow divider to separate the intake-fluid and exhaust-fluid streams from each other after the contact interchange process as flow proceeds from the mixing section into said separator-side section; an intake-fluid discharge pipe or duct in communication with the central intake-fluid discharge passageway of the separator-side section and receiving heated intake fluids therefrom; and an exhaust-fluid discharge pipe or duct in communication with the annular enveloping exhaust-fluid discharge passageway of the separator-side section whereby cooled exhaust fluids may be discharged from the apparatus of the invention.

7. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 6 wherein the annular nozzle member is disposed coaxially with the receiver-side section along the flow axis thereof.

8. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 6 wherein the annular discharge member is disposed coaxially with the separator-side section along the flow axis thereof.

9. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 6 wherein a coniform flow divider is disposed axially of an exhaust-fluid discharge aperture supplied by the said annular enveloping exhaust-fluid discharge passageway and directed against the discharge of cooled exhaust fluids therefrom, and means for axially advancing and retracting the said coniform flow divider with respect to the said exhaust-fluid discharge aperture.

10. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 6 wherein a plurality of receiver-side nozzle members are disposed within the receiver-side section opposite a plurality of companion separator-side discharge members disposed within the separator-side section of said ducting chamber.

11. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 2 wherein the annular nozzle member and exhaust-fluid supply pipe of the receiver-side section are slidably disposed along the flow axis thereof; and means for axially advancing or retracting said receiver-side annular nozzle member with respect to the leading edge of its companion opposite separator-side annular discharge member along the longitudinal flow axis of said contact heat exchanger.

12. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 2 wherein the annular discharge member and exhaust-fluid discharge pipe of the separator-side section are slidably disposed along the flow axis thereof; and means for axially advancing or retracting said separator-side annular-discharge member with respect to the trailing edge of its companion opposite receiver-Side annular nozzle member along the longitudinal flow axis of said contact heat exchanger.

13. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 6 wherein the annular nozzle member and intake-fluid supply pipe of the receiver-side section are slidably disposed along the flow axis thereof; and means for axially advancing or retracting said receiver-side annular nozzle member with respect to the leading edge of its companion opposite separator-side annular discharge member along the longitudinal flow axis of said contact heat exchanger.

14. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 6 wherein the annular discharge member and intake-fluid discharge pipe of the separator-side section are slidably disposed along the flow axis thereof; and means for axially advancing or retracting said separator-side annular discharge member with respect to the trailing edge of its companion opposite receiver-side annular nozzle member along the longitudinal flow axis of said contact heat exchanger.

15. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 6 wherein a plurality of receiver-side annular nozzle members and attached intake-fluid supply pipes are slidably disposed within the receiver-side section along the flow axes thereof; and means for axially advancing and retracting said plurality of receiver-side annular nozzle members with respect to the leading edges of their respective individual opposite companion members of a plurality of separator-side annular discharge members along the longitudinal flow axes of said contact heat exchanger.

16. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 6 wherein a plurality of separator-side annular discharge members and attached intake-fluid discharge pipes are slidably disposed within the separator-side section along the flow axes thereof; and means for axially advancing and retracting said plurality of separator-side annular discharge members with respect to the trailing edges of their respective individual opposite companion members of a plurality of receiver-side annular nozzle members along the longitudinal flow axes of said contact heat exchanger.

17. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 2 wherein the elongate phenum or ducting chamber provides a slidable connection in the mid-body thereof which permits either of the receiver-side or separator-side sections to telescope into the other along the flow axis of the heat exchanger, and means for axially advancing or retracting either of the aforesaid receiver-side or separator-side sections to adjust characteristic length of the heat transfer process between the trailing edge of the receiver-side annular nozzle member and the leading edge of the separator-side annular discharge member.

18. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 6 wherein the elongate plenum or ducting chamber provides a slidable connection in the mid-body thereof which permits either of the receiver-side or separator-side sections to telescope into the other along the flow axis of the heat exchanger, and means for axially advancing or retracting either of the aforesaid receiver-side or separator-side sections to adjust characteristic length of the heat transfer process between the trailing edge of the receiver-side annular nozzle member and the leading edge of the separator-side annular discharge member.

19. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 6 wherein a plurality of receiver-side nozzle members are disposed within the receiver-side section opposite a plurality of companion discharge members disposed within the separator-side section, whereby the elongate plenum or ducting chamber provides a slidable connection in the mid-body thereof which permits either of the receiver-side or separator-side sections to telescope into the other along the slow axes of the heat exchanger, and meanS for axially advancing or retracting either of the aforesaid receiver-side or separator-side sections to adjust characteristic length of the heat transfer process between the trailing edges of the plurality of receiver-side annular nozzle members and the leading edges of the plurality of separator-side annular discharge members.

20. A non-reversing single-pass fluid-to-fluid contact heat exchanger adapted to receive and exchange energy between a plurality of fluid streams at different thermodynamic energy states in parallel flow with respect to each other; said contact heat exchanger comprising a substantially closed plenum or ducting chamber defined by side and confining walls and providing receiver-side, mixing and separator-side sections, said mixing section disposed in said ducting chamber between the receiver-side and separator-side sections thereof; a plurality of intake-fluid nozzles each formed by configured companion partition members disposed laterally between the sidewalls of said receiver-side section in spaced proximity with respect to each other and adjacent partition members and the said sidewalls so that interstices formed therebetween divide the receiver-side section into alternate adjacent intake-fluid nozzle passageways and exhaust-fluid passageways which discharge to the mixing section of said heat exchanger; intake-fluid supply conduits communicating with the nozzle passageways of said receiver-side section and supplying cool pressurized intake fluids thereto; exhaust-fluid supply conduits communicating with the exhaust-fluid passageways of said receiver-side section and supplying hot low-pressure exhaust fluids thereto; whereby particles of the aforesaid intake-fluid and exhaust-fluid streams are brought into physical contact with each other within said mixing section at substantially equal pressures while possessing substantially unequal and parallel and velocity vectors so as to facilitate the contact interchange of thermal and kinetic energy therebetween; a plurality of intake-fluid discharge members each formed by flow-dividing companion partition members disposed laterally between the sidewalls of said separator-side section in spaced proximity with respect to each other and adjacent companion partition members and the said sidewalls so that interstices formed therebetween divide the separator-side section into alternate adjacent intake-fluid and exhaust-fluid passageways disposed opposite their respective companion intake-fluid and exhaust-fluid passageways of the receiver-side section; whereby the contacting intake-fluid and exhaust-fluid streams leaving the said mixing section may enter their respective intake-fluid and exhaust-fluid passageways of the separator-side section and flow towards discharge outlets of said contact heat exchanger; intake-fluid discharge conduits communicating with the intake-fluid discharge passageways of said separator-side section and receiving heated intake fluids therefrom; and exhaust-fluid discharge conduits communicating with the exhaust-fluid discharge passageways of said separator-side section and receiving cooled exhaust fluids therefrom.

21. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 20 wherein the receiver-side partition members define a single nozzle passage disposed centrally with the central longitudinal flow plane of the heat exchanger.

22. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 20 wherein the separator-side partition members define a single intake-fluid discharge passageway disposed centrally with the central longitudinal flow plane of the heat exchanger.

23. A non-reversing single-pass fluid-to-fluid contact heat exchanger adapted to receive and exchange energy between a plurality of fluid streams at different thermodynamic energy states in parallel flow with respect to each other; said contact heat exchanger comprising a substantially closed plenum or ducting chamber defined by side and confining walls and providing receiveR-side, mixing and separator-side sections, said mixing section disposed in said ducting chamber between the receiver-side and separator-side sections thereof; a plurality of partition members having spaced proximity with respect to each other and the sidewalls of said receiver-side section and disposed laterally between the said sidewalls so that interstices formed therebetween divide the receiver-side section into alternate adjacent intake-fluid and exhaust-fluid passageways which discharge to the mixing section of said heat exchanger; a fluid pump or fan disposed to supply pressurized intake fluids; intake-fluid supply conduits communicating with the discharge of said fluid pump or fan and the individual intake-fluid passageways of the said receiver-side section; an intake-fluid nozzle passageway disposed in the supply conduit branch for each individual intake-fluid passageway of the said receiver-side section and discharging high-velocity intake fluids thereto; exhaust-fluid supply conduits communicating with the exhaust-fluid passageways of said receiver-side section and supplying hot low-velocity exhaust fluids thereto; whereby particles of the aforesaid intake-fluid and exhaust-fluid streams are brought into physical contact with each other within said mixing section at substantially equal presssures while possessing substantially unequal and parallel velocity vectors so as to facilitate the contact interchange of thermal and kinetic energy therebetween; a plurality of flow-dividing partition members having spaced proximity with respect to each other and the sidewalls of said separator-side section and disposed laterally between the said sidewalls so that interstices formed therebetween divide the separator-side section into alternate adjacent intake-fluid and exhaust-fluid passageways disposed opposite their respective companion intake-fluid and exhaust-fluid passageways of the receiver-side section; whereby the contacting intake-fluid and exhaust-fluid streams leaving the said mixing section may enter intake-fluid discharge conduits communicating with the intake-fluid discharge passageways of said separator-side section and receiving heated intake fluids therefrom; and exhaust-fluid discharge conduits communicating with the exhaust-fluid discharge passageways of said separator-side section and receiving cooled exhaust fluids therefrom.

24. A non-reversing single-pass fluid-to-fluid contact heat exchanger adapted to receive and exchange energy between a plurality of fluid streams at different thermodynamic energy states in parallel flow with respect to each other; said contact heat exchanger comprising a substantially closed plenum or ducting chamber defined by side and confining walls and providing receiver-side, mixing and separator-side sections, said mixing section disposed in said ducting chamber between the receiver-side and separator-side sections thereof; a plurality of partition members having spaced proximity with respect to each other and the sidewalls of said receiver-side section and disposed laterally between the said sidewalls so that interstices formed therebetween divide the receiver-side section into alternate adjacent intake-fluid and exhaust-fluid passageways which discharge to the mixing section of said heat exchanger; a fluid pump or fan disposed to supply high-velocity intake fluids; intake-fluid supply conduits communicating with the discharge of said fluid pump or fan and the individual intake-fluid passageways of the said receiver-side section; exhaust-fluid supply conduits communicating with the exhaust-fluid passageways of said receiver-side section and supplying hot low-velocity exhaust fluids thereto; whereby particles of the aforesaid intake-fluid and exhaust-fluid streams are brought into physical contact with each other within said mixing section at substantially equal pressures while possessing substantially unequal and parallel velocity vectors so as to facilitate the contact interchange of thermal and kinetic energy therebetween; a plurality of flow-dividing partition members having spaced proximity with respect to each other and the sidewalls of said separator-side section and disposed laterally between the said sidewalls so that interstices formed therebetween divide the separator-side section into alternate adjacent intake-fluid and exhaust-fluid passageways disposed opposite their respective companion intake-fluid and exhaust-fluid passageways of the receiver-side section; whereby the contacting intake-fluid and exhaust-fluid streams leaving the said mixing section may enter their respective intake-fluid and exhaust-fluid passageways of the separator-side section and flow towards discharge outlets of said contact heat exchanger; intake-fluid discharge conduits communicating with the intake-fluid discharge passageways of said separator-side section and receiving heated intake-fluids therefrom; and exhaust-fluid discharge conduits communicating with the exhaust-fluid discharge passageways of said separator-side section and receiving cooled exhaust fluids therefrom.

25. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 2 wherein a coniform flow divider is disposed axially of a duct throat section within the intake-fluid discharge ductwork of said contact heat exchanger and supplied from the said annular intake-fluid discharge passageway of the separator-side section, the said coniform flow divider being directed against the discharge of heated intake fluids therefrom, and means for axially advancing and retracting the said coniform flow divider with respect to the said intake-fluid discharge throat section.

26. The non-reversing single-pass fluid-to-fluid contact heat exchanger of claim 6 wherein a coniform flow divider is disposed axially of a duct throat section within the intake-fluid discharge ductwork of said contact heat exchanger and supplied from the said central intake-fluid discharge passageway of the separator-side siection, the said coniform flow divider being directed against the discharge of heated intake fluids therefrom, and means for axially advancing and retracting the said coniform flow divider respect to the said intake-fluid discharge throat section.

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