WO2015028052A1 - Récupérateur, micro-turbine à gaz et utilisation du récupérateur - Google Patents

Récupérateur, micro-turbine à gaz et utilisation du récupérateur Download PDF

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Publication number
WO2015028052A1
WO2015028052A1 PCT/EP2013/067739 EP2013067739W WO2015028052A1 WO 2015028052 A1 WO2015028052 A1 WO 2015028052A1 EP 2013067739 W EP2013067739 W EP 2013067739W WO 2015028052 A1 WO2015028052 A1 WO 2015028052A1
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WO
WIPO (PCT)
Prior art keywords
gas
recuperator
block
flow
bridge
Prior art date
Application number
PCT/EP2013/067739
Other languages
German (de)
English (en)
Inventor
Sebastian KIEßLING
Heinz Peter Berg
Christian Schumacher
Original Assignee
Lux Powertrain S.A.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Lux Powertrain S.A. filed Critical Lux Powertrain S.A.
Priority to PCT/EP2013/067739 priority Critical patent/WO2015028052A1/fr
Publication of WO2015028052A1 publication Critical patent/WO2015028052A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/30—Exhaust heads, chambers, or the like
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0012—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form
    • F28D9/0018—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the apparatus having an annular form without any annular circulation of the heat exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction

Definitions

  • the invention relates to a recuperator for heat exchange between a first gas on the one hand and a second gas on the other hand according to the preamble of claim 1.
  • the invention also relates to a micro gas turbine and a use of the recuperator.
  • a heat exchanger as well as a recuperator, for heat exchange between a first and a second gas is formed. In principle, this may be required for use in a variety of applications where heat is produced.
  • a gaseous fluid is used as a waste heat carrier and a gaseous fluid as a cooling medium or Abisseetz commentary.
  • a heat exchanger in the form of a recuperator serves to recycle heat into a cycle.
  • This can, as in the present subject, preferably for preheating combustion air, in particular of compressed charge air, can be used.
  • a recuperator serves to utilize waste heat from a process for preheating a fluid to be supplied to the process.
  • a highly efficient recuperator is desirable in order to meet the requirements for heat exchange processes taking place at a comparatively high temperature and pressure between a first gas to be supplied to a combustion process, for example charge air for a micro gas turbine in particular serves as combustion air and a waste heat-carrying second gas, for example exhaust gas of the micro gas turbine to create.
  • recuperator serves the first gas in the form of charge air as a coolant or Abebenaufêt for the second gas in the form of exhaust gas from a combustion process, which is the carrier of the waste heat; the charge air heated up in such an advantageous manner is fed into the combustion process.
  • No. 4,229,868 discloses a recuperator constructed according to a similar principle with a plate block constructed in a sandwich structure for the separate and heat exchanging guidance of a first and second gas, in which the block is also designed for local flow in a counterflow arrangement; this is described with reference to an internal air flow and an internal gas flow.
  • This arrangement is also suitable for high pressurization, especially in the field of gas turbines and associated compressor drive systems.
  • Such and similar heat exchanger applications are foreign to the use of an exchanger bridge, as known, for example, from WO 2009/000581 A1 for the transfer of heat exchange fluid from a first heat exchanger block to a second heat exchanger block.
  • the latter measures known from conventional automotive fields are not suitable for heat exchange processes which take place at comparatively high pressures and temperatures; as is the case in particular with micro gas turbines and applications for micro gas turbines.
  • the present application relates in particular to a recuperator which is suitable for use in environmentally friendly, d. H. recuperative turbines as in engines or stationary power supply units to be used.
  • the hitherto preferred construction of such a recuperator is to provide two manifolds which are available via a plurality of e.g. B. 6000 lancet profile tubes are connected together.
  • relatively cool compressor air is introduced, which passes through the numerous lancet tubes in the other manifold.
  • the exhaust gases passed in crossflow through these lancet tubes heat the branched compressor air that is returned to the engine.
  • the efficiency is increased and also cooled by the heat exchange, the exhaust gases.
  • the invention begins, whose task is to provide a recuperator for heat exchange between a first gas on the one hand and a second gas on the other hand to provide a micro gas turbine and a use of the recuperator, in particular in connection to a micro gas turbine, which is improved over the prior art.
  • a recuperator, a micro gas turbine and a use of the recuperator that proves to be efficient and comparatively flexible in terms of the space requirements and performance requirements of a micro gas turbine.
  • flow losses in the recuperator should be ensured with nevertheless high thermodynamic parameters, such as pressure and temperature, in the heat exchange between the first and second gas.
  • the block in particular a number of such blocks, is arranged for superlocal flow in a counterflow arrangement, and the block, in particular the number of blocks, and / or further blocks can be flowed through in succession by the first and second gas.
  • the first gas flows through a first block and then through a second block, and the second gas flows through the second block and then through the first block.
  • the invention has recognized that it is fundamentally advantageous to align a block for local flow in the cross-flow arrangement in the recuperator, ie. H. Locally, or as referred to in the art "internally" - a block of the recuperator, the first gas (preferably charge air) and the second gas (preferably exhaust gas) flow transversely, in particular perpendicularly, to each other, i.e., locally in cross flow.
  • first gas preferably charge air
  • the second gas preferably exhaust gas
  • the first gas is a charge air, in particular combustion air and the second gas is exhaust gas;
  • the invention recognizes that it is conducive to the heat exchange to arrange a number of such blocks, ie one or more, for superlocal flow in a counter current arrangement.
  • a further number, if necessary, of differently designed blocks may be provided.
  • the first and second gas in particular charge air and exhaust gas, flows locally, ie in particular outside the blocks at least on a substantial part of the flow path in a counter-current arrangement.
  • Another number in the opposite order of the first and second gas can be flowed through successively.
  • the exhaust gas flows from one side of the powerhead, so to speak from the front, directly into the recuperator.
  • the charge air is supplied to the recuperator laterally on the opposite side of the inflow side or on the opposite side of the inflow side of the exhaust gas, so to speak from behind.
  • the pressure losses in the exhaust gas (AG) are comparatively low.
  • the pressure losses in the charge air (LL), in particular combustion air, are also limited and are borne by the advantages of an efficient heat exchange; This is especially the overall concept of a pressure drop on the charge air side is advantageous in itself.
  • the concept of the invention offers a particularly flexible adaptability of the recuperator as well as a possible extension of the recuperator with regard to the number of blocks provided according to the invention.
  • the recuperator is thus advantageously modular.
  • Pressure and temperature profiles of the charge air, in particular for loading a combustion chamber in a micro gas turbine can be set comparatively efficient and optimized; this taking into account the pressure and temperature profiles of the exhaust gas of a turbine, preferably a micro gas turbine.
  • the concept of the invention also leads to a micro gas turbine of claim 16 with a powerhead comprising a turbo group with an air bearing on a shaft (also called shaft), a combustion chamber, a generator with bearings and the recuperator.
  • a turbo group with an air bearing on a shaft (also called shaft), a combustion chamber, a generator with bearings and the recuperator.
  • the air bearing, the bearing and a flow direction of the second gas, in particular exhaust gas, the recuperator along, in particular, are arranged on a common axis.
  • the concept of the invention thus leads fundamentally different from previously known concepts away from a stacked arrangement of powerhead and recuperator of the prior art.
  • the invention is based on the consideration that the relative orientation of the recuperator and the bearings of the powerhead and generator on a common axis is conducive to an elongated arrangement, although space-saving and also efficient, as well as a variable recuperator design.
  • Blocks of the recuperator may independently be arranged and / or aligned transversely to the common axis of an elongated arrangement.
  • Blocks of the recuperator may also be arranged and / or aligned independently of the circumference to the common axis of an elongated arrangement.
  • the concept is made possible by a recuperator of claim 1.
  • the recuperator according to the concept, in particular according to one of the developments, is designed in particular for a micro-gas turbine. In particular, it has proved to be advantageous that the recuperator
  • a mobile unit such as a vehicle on land or water or the like and / or
  • a stationary unit such as a power plant and / or
  • a micro gas turbine can be used in particular in mobile applications that arise in the commercial vehicle sector or heavy vehicle sector on land or water.
  • a micro gas turbine can also be used in stationary units such as, for example, a power station or air conditioning units for stationary applications.
  • a charge air as the first gas and / or an exhaust gas as a second gas in particular the charge air as a coolant for the exhaust gas
  • a charge air (LL) as a first gas and / or an exhaust gas (AG) as a second gas - in particular the charge air (LL), in particular Verbrennungs Kunststoff- as coolant for the exhaust gas (AG) feasible and the second gas along an elongated oil type flow path, in particular on a main axis (A), and / or substantially in the direction of a major axis (A) through the chambers of the blocks is feasible.
  • a first block and a second block are arranged relative to one another in such a way that they are opposite to the first gas, wherein the flow channels of the blocks are connected in a flow-reversing manner with an exchanger bridge designed to be gas-conductible, and the exchanger bridge has a common fluid connection Forms all the heat exchanger tubes of a block, and the first gas along a total or partial S-like flow path, and / or
  • the first gas is feasible along a total or partial U-like flow path.
  • the first gas can be guided along a total or partial S-type flow path which crosses the one main axis (A).
  • the first gas can be guided along a total or partial U-shaped flow path, which lies in a peripheral region around the main axis (A) without crossing the main axis (A).
  • developments taking into account the concept of the invention can also be realized in such a way that one or more of the number of blocks and / or the further number of blocks at a right angle to the axis (as exemplified with respect to FIGS.
  • a first block of the recuperator could be parallel to or on the axis
  • a second block of the recuperator could be flat with the axis
  • a third block could be steep Be aligned axis and a fourth block to be aligned perpendicular to the axis.
  • the heat exchanger tube is formed as a lancet tube, in particular, the lancet tube is oriented such that the narrow side of the second gas can be flowed.
  • a lancet tube recuperator has proven itself, especially in applications with a micro gas turbine.
  • the number of flow channels in the housing can advantageously be arranged in such a way that flow paths for the second gas with a flow path cross section which remains relatively constant remain in the chamber.
  • the number of flow channels over the cross section of the chamber can be arranged along substantially straight or zigzag-like arrangement lines. In particular, this is advantageous in the case that the first gas is guided along a total or partial S-type flow path, in particular crossing a major axis (A).
  • the number of flow channels can be arranged over the cross section of the chamber along an involute-like arrangement line.
  • this is advantageous in the case in which the first gas lies along a total or partial U-like flow path, in particular in a peripheral region around the main axis (A), without crossing the main axis (A).
  • the number of blocks comprises at least one first and second block, between which see a fluid-carrying exchanger bridge is attached.
  • the blocks or the swap bridge of the number are aligned longitudinally transversely to a major axis.
  • an exchanger bridge forms a common fluid connection for all heat exchanger tubes of a block.
  • an exchanger bridge has a compensator. It has proved to be particularly advantageous that the number of blocks comprises at least one first and second block aligned with a longitudinal block axis transverse to a main axis (A), between which a fluid-carrying exchange bridge with a bridge long axis along a major axis (A) is mounted.
  • the number of blocks may comprise at least one first and second block aligned with a long block axis along a major axis (A), between which a fluid bearing exchange bridge having a bridge longitudinal axis transverse to a major axis (A) is mounted.
  • an inlet diffuser connects a fluid connection for all the heat exchanger tubes of a block to a compressor and / or an outlet diffuser advantageously connects a fluid connection for all heat exchanger tubes of a block to a combustion chamber.
  • a rear one of the number of heat exchanger modules may preferably have an inflow module with an inlet diffuser, for gas flowing in from a locally upper or alternatively lower direction, and
  • a front one of the plurality of heat exchanger modules having an outflow module with an outlet diffuser for first gas flowing out in a locally lower or alternatively lower direction.
  • a directional connection between said directions may be transverse to an overall l-type flow path.
  • a peripheral gas guide can be designed such that the first and second gas superlocated from the same side, in particular a powerhead side, the recuperator can be fed.
  • an outer one of the number of heat exchanger modules is an inflow module with an input diffuser for gas flowing locally in the axial direction (A) or alternatively against the axial direction (A), and
  • a directional connection between said directions may be transverse to an overall l-type flow path.
  • recuperator is advantageously a peripheral gas guide designed such that the first and second gas is superlocated from the same side, in particular a powerhead side, the recuperator can be fed.
  • the first gas can be guided along a total S-like flow path through flow guides.
  • S-type flow path are used in particular alternately transversely to and along a main axis arranged flow channels of the blocks and the fluid connection of an exchanger bridge.
  • the first gas can be guided along a total U-like flow path through flow guides.
  • To form the U-like flow path serve in particular parallel to a main axis arranged flow channels of the blocks, which lie in a peripheral region to the axis and the flow-deflecting fluid connection of at least one exchanger bridge. These can be realized in an all-round ring or ring segment around the axis.
  • the second gas can be guided along an overall l-type flow path through the chambers of the blocks.
  • the l-type flow path is in particular arranged completely along and on a main axis; in particular in the case of a total S-like flow path of the first gas.
  • the l-type flow path can also be arranged only partially on a main axis and further out along the main axis but in a radial deviation to the outside; in particular in the case of a total U-like flow path of the first gas, then namely crossing the flow tion paths of the first gas in the U-like flow path with the second gas when it is guided in a radial deviation to the outside.
  • an S-type flow path is formed by the flow channels of at least a first, second and third block and at least a first and a second exchange bridge, wherein the first exchange bridge between the first and second block and the second exchange bridge between the second and third block is arranged ,
  • a U-like flow path is formed by the flow channels of at least a first, second and third and fourth block and at least a first and a second exchange bridge, wherein the first exchange bridge between the first and second block and the second exchange bridge between the third and fourth block is arranged.
  • a first, second, in particular third, in particular fourth, heat exchanger module each have a first, second, in particular third, in particular fourth block and in each case a first, second, in particular third, in particular fourth , Housing, each having a first, second, in particular third, in particular fourth frame for grasping in each case a first, second, in particular third, in particular fourth number of lancet tubes.
  • a first fluid-carrying exchanger bridge is preferably mounted, in particular an exchanger bridge having a compensator ,
  • the S-type flow path is formed by the flow channels of at least a first, second and third block and at least a first and a second exchange bridge, wherein the first exchange bridge between the first and second block and the second exchange bridge between the second and third block is arranged ,
  • a first heat exchanger module has a first block and a first housing with a first frame for holding a first number of lancet tubes, and
  • a second heat exchanger module with a second block and a second housing a second frame for grasping a second number of lancet tubes, and
  • a third heat exchanger module has a third block and a third housing with a third frame for holding a third number of lancet tubes.
  • a first fluid-carrying exchange bridge is mounted, and
  • a second fluid-carrying exchange bridge is mounted between a frame output of the second heat exchanger module and a frame input of a third heat exchanger module.
  • recuperator it is provided, for example following the first variant, that
  • a first heat exchanger module an inflow module having an inlet diffuser for gas flowing in from a locally upper direction
  • a third heat exchanger module has an outflow module with an outlet diffuser for first gas flowing out in a locally lower direction, in particular a directional connection between lower and upper direction transverse to an overall I-like flow path.
  • a second heat exchanger module has an intermediate module with a first and second exchanger bridge for gas flowing through. It may also be provided a fourth or more heat exchanger modules.
  • the upper and lower directions can be reversed.
  • the upper and lower directions can also stand for a more outward and further inward arrangement of a flow connection as claimed; the direction even at an outboard and further inward location of a flow port can also be axially effective.
  • a peripheral gas guide is designed to supply the first and second gas superlocally from the same side, in particular a powerhead side, to the recuperator.
  • the modulability by means of the number of blocks can be advantageously used for adapting the shape of the recuperator and / or the blocks themselves, in particular in the present case an elongated form of the recuperator.
  • This can be z. B. in terms of a space requirement for the recuperator or a micro- Gas turbine, especially in the context of a mobile application, such as a vehicle od.
  • Like. Be useful; possible and generally not restrictive are angular, cylindrical, oval, elliptical or the like forms of a module or block and / or the recuperator.
  • the modulability can also be advantageously used for an adaptation of a choice of material with respect to temperature and / or pressure conditions in the charge air (LL) and / or along the extension of the recuperator, which are in particular elongated and / or circumferential the exhaust gas (AG).
  • the modulability can also be used to advantage to reduce manufacturing costs; because the modulability allows high quantities for the module or the block.
  • a module or a block of the recuperator can be represented as a ready-to-install module, for. B. using Lotdepots with filled solder at appropriate locations.
  • the assembled module can be placed with solder in a soldering oven and removed ready to install soldered.
  • a type of installation in different platforms of a recuperator, a micro gas turbine or application, such as a vehicle, can be used to meet specific adaptation requirements.
  • a repair effort in a recuperator can be reduced or simplified by replacing a module.
  • a block or a module can be represented comparatively simply by an advantageous laser-guided cutting process.
  • FIG. 1 is a perspective view of a first particularly preferred embodiment of a micro gas turbine with a recuperator in a preferred embodiment according to the principle of a first further developing variant, wherein the recuperator serves to implement a heat dissipation from an exhaust gas and the heat dissipated to preheat a compacted charge and to introduce combustion air, ie to further heat the charge and combustion air;
  • FIG. 2 shows a sectional view of the micro gas turbine with recuperator shown in principle in FIG. 1, the sectional view showing a varied microturbine exchanged with top and bottom in a view rotated about an axis A thereof;
  • FIG. Fig. 3 is a perspective partial section X of a block of the recuperator as shown in Fig. 1 above or as shown in Fig.
  • FIG. 5 is a schematic sectional view taken along an axis A and in view (A) transverse to the axis A of a second particularly preferred embodiment of a micro gas turbine with a recuperator in a further preferred embodiment according to the principle of a second further developing variant, wherein the recuperator serves to a To implement heat removal from an exhaust gas and bring the heat dissipated to preheat a compressed charge and combustion air, ie to further heat the charge and combustion air.
  • FIG. 1 shows a perspective view of a system of a micro gas turbine 1000 with a powerhead 1 100, a recuperator connected thereto for recuperative heat recovery. meley between charge air LL and exhaust gas AG of the micro gas turbine 1000 with peripheral gas guide 1300 and one powered by the powerhead 1 100 generator 1400. More specifically, the same reference numerals are used for the same or similar features or features the same or similar function. As a result, FIG. 1 also shows the individual structural units designated as they are explained below in FIG. 2.
  • a burner assembly 1 130 as symbolized by lines laterally on the circumference or axially connected to the rear end, which is symbolically further recognizable in Figure 2.
  • the torches of the torch assembly 1 130 may in principle be aligned radially with respect to the axis A or, as provided here, may be aligned along the axis A.
  • the powerhead 1 100 is a comparatively compact overall using flange connections between inlet funnel 1301 for charge air LL of the turbo group 1 1 10, combustion chamber 1 120 and peripheral gas guide 1300 formed.
  • the recuperator 1200 has a number of heat exchanger modules M1201, M1202, M1203 with blocks 1201, 1202, 1203 explained with reference to FIG.
  • FIG. 2 for the separate and heat exchanging guidance of the charge air LL, as a first gas, and the exhaust gas AG, as a second gas , on; this is also described in more detail with reference to FIG. 2 and the following FIG. 3.
  • the flow directions of the exhaust gas AG and charge air LL are shown here for a flow through the recuperator 1200 and the peripheral gas guide 1300. From this it can be seen that the recuperator of the exhaust gas AG is generally traversed by a second gas along an overall l-like flow path -in the present case along and on the main axis A- of the micro gas turbine. This direction is also referred to as R A in relation to the following FIGS. 2 and 3.
  • the charge air LL flows along a flow direction predetermined by the flow channels when flowing downwards or R L3 LL when flowing downwards; in between upwards in the direction of R L2 LL - ie the flow through the recuperator 1200 takes place in the heat exchanger modules M1201, M1202, M1203 locally in a cross-flow arrangement.
  • the recuperator 1200 is supplied with charge air LL from the peripheral gas guide 1300 from the same side-over-local with charge air LL, ie in the direction R L ⁇ +) .
  • This charge air is supplied to the recuperator 1200 via an input diffuser 1210 and discharged via an output diffuser 1230; ie in this case -over-local- the charge air LL in the recuperator flows against the direction of the exhaust gas flow R A in the direction R L ⁇ _), as is likewise shown in FIG. 1.
  • the charge air LL thus follows the superlocal flow direction R L ⁇ _) in countercurrent to the direction of the exhaust gas R A within a first exchanger bridge 1220 and a second exchanger bridge 1230.
  • FIG. 2 shows the system of a microturbine 1000 with the powerhead 1 100 comprising a turbo group 1 1 10, a combustion chamber 1 120 and a powerhead downstream recuperator 1200 for heat exchange between the exhaust and charge air of the powerhead 1 100 and a driven by the powerhead 1 100 generator 1300.
  • the turbo group 1 1 10 is present with a compressor 1 1 1 1 for charge air LL and a turbine wheel 1 1 12, powered by fuel gas BG -like, biogas, natural gas or other fuel, liquid such as diesel, kerosene or gas-particle mixture such as coal dust coupled to a common shaft 1 1 13.
  • the shaft 1 1 13 in turn is coupled to drive the generator 1400 with a rotatably mounted to the stator of the generator rotor of the generator.
  • the shaft 1 1 13 of the turbo group 1 1 10 is presently axially and radially mounted, namely in this embodiment by means of an air bearing assembly comprising a radial air bearing 1 1 14 and an axial air bearing 1 1 15.
  • An air bearing is basically of a number of Bearings and supporting foils, if necessary. Also spring foils constructed, which are stacked as plates (for an axial-air bearing 1 1 15) or annular (for a radial air bearing 1 1 14).
  • Exhaust AG of the powerhead 1 100 is presently supplied in a direction R A along the main axis A of the micro gas turbine 1000 to the recuperator 1200; the axis A designated in FIG. 2 is essentially essentially the axis of symmetry of the microturbine 1000.
  • the recuperator 1200 is designed to preheat charge air LL conducted via a peripheral gas guide 1300 by heat exchange with the exhaust gas AG, which in turn leaves the recuperator 1200 via an exhaust gas outlet.
  • the peripheral gas guide 1300 includes a charge air supply 1310, a charge air discharge 1320, an exhaust gas discharge 1340, and a central exhaust gas supply 1330.
  • Fig. 2 the supralocal countercurrent principle and the local cross flow principle with reference to the flow direction of an L-like flow path of the exhaust gas AG - namely R A - and the flow directions of the total S-like flow path of the charge air - namely R L ⁇ _) and R L3 LL- explained and shown.
  • the recuperator 1200 of both the exhaust gas and the charge air of the same Side namely the powerhead side via a charge air supply 1310 of the peripheral gas guide 130 and a central exhaust gas supply 1330 flows.
  • the recuperator 1200 is formed with a first heat exchanger module M1201 comprising the first block 1201 and a first housing having a first frame 201 for holding a first number of lancet tubes 21, a second heat exchanger module M1202 a second block 1202 and a second housing with a second frame 202 for holding a second number of lancet tubes 22 (not shown in detail) and a third heat exchanger module M1203 with a third block 1203 and a third housing with a third frame 203 for grasping A third number of lancet tubes 23.
  • a first fluid-carrying exchange bridge 1220 is mounted and between a frame exit of the frame 202 of the second heat exchanger module and a frame entrance of the third frame 203 of the third heat exchanger module, a second fluid-carrying exchanger bridge 1230 is attached.
  • the input diffuser 1210 is placed at the input of the first frame 201 and the output diffuser 1240 at the output of the third frame 203.
  • the exchanger bridges 1220, 1230 are mounted between the first and second blocks 1201, 1202 and between the second and third blocks 1202, 1203, respectively.
  • the exchanger bridges as well as the diffusers 1210, 12200, 1230, 1240 each form a fluid connection for all the heat exchanger tubes of a block 1201, 1202, 1203.
  • FIG. 3 shows, in a perspective cutout view of the detail X of FIG. 2 and with reference to the previously explained features and parts with the same reference numeral, essentially a representation of the second block 1202 of the recuperator 1200, by way of example also for a similar embodiment of FIG the first and third blocks 1201, 1203.
  • the block 1202 is housed in a housing forming a chamber for receiving the block 1202 inside. While the block has a number of charge air LL flow-through flow channels K -here in the form of lancet tubes LR, with oval cross-section-, the chamber is provided for the flow of exhaust gas AG, ie, the gaps ZR, the lancet tubes LR, from Exhaust gas flows through. According to the cross flow principle explained above, this flows Exhaust AG a narrow side s of the lancet tubes LR, while the broad side b of each lancet tube LR, aligned in the flow direction.
  • the frame 202 has suitable holding elements which are able to hold the lancet tubes LR in the row and column arrangement shown, wherein the narrow sides s of adjacent lancet tubes LR in the flow direction R A of the exhaust gas AG are not immediately face. But alternately, the lancet tubes LR, a column S against lancet tubes LR, an adjacent column S each offset by a width of the narrow side s against each other. Accordingly, in the present case two mutually offset by a narrow side s against each other row lines R1, R2 in Fig. 3 are displayed.
  • the housing G202 and / or the frame 202 also has a groove N202 for receiving a sealing plate D202; a sealing plate D202 is formed in the form of a sealing plate for limiting an exhaust gas mass flow in the chamber -here of the first heat exchanger module with block 1201-.
  • the sealing plate D202 is held in a groove N202 of the second housing G202 as well as in a groove N201 of the first housing G201 with the first block 1201.
  • a recuperator 1200 ' has a first, second and third block 1201', 1202 ', 1203', which are set up separately S-shaped; shown is each block without the other parts such as housing od.
  • the frames of the flow channels K are respectively designed as upper and lower frames 201, 201, 202, 202, 203, 203, and the lancet tubes LR to hold up and down.
  • the first and second block 1201 ', 1202' is fluid-connected with a first exchanger bridge 1220 'and the second and third block 1202', 1203 'with a second exchanger bridge 1230', ie, here too, a common fluid connection for all heat exchanger tubes of a block 1201 ', 1202', 1203 'through the heat exchanger bridge 1220', 1230 'shown.
  • the total here S-type flow path SS alternately transversely to and along a major axis A- results in the flow channels K of each of the blocks and each fluid connection of an exchanger bridge 1220 ', 1230'.
  • the recuperator 1200 ' also has an input diffuser 1210' located at the bottom thereof and an output diffuser 1240 'located at the top thereof to allow charge air LL to be pressurized at high pressure. cold air (cold gas) - the recuperator 1200 'supply and supply them in heated form via the output diffuser 1240' a combustion chamber 1 120.
  • the exhaust gas AG heating gas, low pressure
  • the flow direction of the exhaust gas R A relative to the superlocal flow directions of the charge air R L ⁇ _ results in the local countercurrent principle.
  • the general feed direction R L ⁇ + runs parallel to the flow direction R A of the exhaust gas AG.
  • the exchanger bridges 1220 ', 1230' are advantageously each equipped with a compensator K1220 'or K1230', so that a relative movement of the blocks 1201 ', 1202', 1203 'caused by temperature changes is already advantageously achieved by the compensators K1220', K1230 'be compensated.
  • the exchanger bridges 1220 ', 1230' are each housed in an outer housing 1250 of the recuperator 1200 '.
  • the peripheral gas guide 1300 -in the present case for example, can also be used.
  • the charge air discharge 1320 or the charge air supply 1310 of a recuperator 1200 of Figure 1 and Figure 2-- variable spacers or the like-as in the present case sleeves M1310 or compensators K1320- have.
  • FIG. 5 shows a further embodiment of a microturbine 1000 ", in which, for the sake of simplicity, the same reference numerals are used for identical or similar parts or parts of the same or similar function, with reference to the previous description of a microturbine 1000, 1000 ' 1, and in particular FIG. 1 and FIG. 2.
  • FIG. 5 the principle of a modified recuperator 1200 ", following the principle of the further developing second variant, will be explained below.
  • the recuperator 1200 " has in the present case, in particular the cross-section A-Aim part (A) of FIG.
  • the first outer ring block 1201 "-1202” is present with an upper part 1201 “and a lower part 1202", and the second inner ring block 1203 "-1204" is herein denoted by an upper part 1203 "and a lower part 1204."
  • the ring blocks 1201 “-1202” and 1203 "-1204" connected to an annular exchanger bridge 1210 "-1220" for reversing deflection, ie an upper part 1210 "and a lower part 1 220 "of the annular exchanger bridge 1210" -1220 "connected.
  • annular parts In total there are five annular parts, namely a first ring block 1201 "-1202", a second ring block 1203 “-1204" and an annular exchange bridge 1210 “-1220” and an annular input diffuser 1230 "and an annular output diffuser 1240".
  • the recuperator 1200 is connected to a peripheral gas guide 1300 via the annular input diffuser 1230” and to the combustor 1 120 via the annular output diffuser 1240 ", in particular, the flow channels are completely through the diffusers 1230", 1240 "for guiding the charge air between peripheral Gas guide 1300 and combustion chamber 1 120 fluidly connected.
  • the drawn flow path of the exhaust gas AG follows substantially the direction of the main axis A and introduces the exhaust gas from the combustion chamber 1 120 via an output diffuser-shaped gas guide 1330 for the exhaust gas AG on the axis A in the central The axis A lying and surrounding cylindrical space of the recuperator 1200 'between the gas guide 1330 and a tei- Lungsquerrough-Ab gleich 1331.
  • the flow-forming Operaungs- cross-section termination 1331 the exhaust gas removal, the exhaust gas AG from the axis A led away and in a surrounding the axis A circumferential region U of the recuperator 1200 "out before the exhaust gas enters the Abgasab Adjust 1340, which is presently arranged in the peripheral region.
  • a ring block 1201 "-1202" and 1203 “-1204" of the recuperator 1200 are arranged and aligned parallel to the axis A and without crossing them, while one block of the recuperator 1200 in FIGS. 1 and 2 crosses the axis A,
  • the charge air LL serving as combustion air is guided on a ring circumference along a U-like flow path in the circumferential area U of the ring circumference Peripheral region Ui guided at the height of the combustion chamber 1 120.
  • the overall annular exchanger bridge 1210 "-1220" in turn causes an annular flow reversal of the charge air LL so that the charge air in the outer peripheral area Ua largely in the direction of the exhaust gas, but in the inner peripheral area Ui substantially in countercurrent arrangement, d. H. against the flow direction of the exhaust gas AG, is performed.
  • the recuperator 1200 "realizes in the inner circumferential area Ui a counter-current arrangement according to the concept of the invention, namely in the inner ring block 1203" -1204 ".
  • each of the ring blocks need not necessarily be realized as a ring.
  • each of the ring blocks can be realized from at least two box-like modules, that is to say in the form of a block 1201, 1202, 1203, 1204 as in FIGS. 1 to 4 with rod-like lancet tubes LR, or else in another Shape can be realized, for. B. as a half-ring or ring cutout with semicircular or circular cut-out cross-section.
  • the lancet tubes LR ,, LR j are arranged along an involute-like arrangement line E1, E2. assigns.
  • This arrangement makes it possible that the spaces between the lancet tubes LR, or LR j created in the inner annular space of the Ringblocks1203 "-1204" or in the annular space of the outer ring block 1201 “-1202" to form a for the exhaust gas AG flow path such are that this remains essentially unchanged in the path cross section; that is, from an inner point of the flow path near the axis A to an outer point near the exhaust passage 1340 of the flow guide for the exhaust gas AG.
  • an arrangement of the Lnazettenrohre LR ,, LR j also be designed so that it forms a diffuser-like widening of the flow cross-section;
  • the lancet tubes LR ,, LR j can each be arranged deviating from an exact involute in an involute-like arrangement line E1, E2.

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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)

Abstract

L'invention concerne un récupérateur 1200 servant à l'échange de chaleur entre un premier gaz et un second gaz, comprenant : un bloc de guidage séparé des premier et second gaz avec échange de chaleur qui comporte un certain nombre de conduits d'écoulement pouvant être traversés par le premier gaz, et une première chambre recevant les conduits d'écoulement et pouvant être traversée par le second gaz, et un boîtier dans lequel sont disposés la chambre et les conduits d'écoulement. Un conduit d'écoulement est configuré sous la forme d'un tube échangeur de chaleur, et le bloc est orienté, notamment dans son ensemble, en étant configuré selon un agencement d'écoulement transversal ou en croix pour l'écoulement local. Selon l'invention, le bloc, notamment un nombre de tels blocs 1201, 1202, 1203, est disposés selon un agencement d'écoulement à contre-courant pour l'écoulement superlocal et le bloc, notamment le nombre de blocs, et/ou d'autres blocs d'un ordre inverse peuvent être traversés successivement par les premier et second gaz.
PCT/EP2013/067739 2013-08-27 2013-08-27 Récupérateur, micro-turbine à gaz et utilisation du récupérateur WO2015028052A1 (fr)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108798899A (zh) * 2018-06-13 2018-11-13 武汉英康汇通电气有限公司 微型涡轮发电机
CN110006243A (zh) * 2019-04-16 2019-07-12 广东技术师范大学 一种蒸发器及果蔬干燥系统

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GB624676A (en) * 1947-03-06 1949-06-14 Heat Exchangers Ltd Improvements in air preheaters and like heat exchange apparatus
FR1452128A (fr) * 1964-07-13 1966-02-25 Gen Electric Dispositif de récupération pour les moteurs à turbine à gaz
US3831374A (en) * 1971-08-30 1974-08-27 Power Technology Corp Gas turbine engine and counterflow heat exchanger with outer air passageway
US3894581A (en) 1973-04-16 1975-07-15 Garrett Corp Method of manifold construction for formed tube-sheet heat exchanger and structure formed thereby
US4229868A (en) 1978-10-26 1980-10-28 The Garrett Corporation Apparatus for reinforcement of thin plate, high pressure fluid heat exchangers
WO1983003663A1 (fr) * 1982-04-19 1983-10-27 North Atlantic Tech Echangeur thermique a plaque flottante
CA1193593A (fr) * 1984-05-08 1985-09-17 Jonathan P. Maendel Echangeur de chaleur
US20050097881A1 (en) * 2001-07-26 2005-05-12 Takanori Shibata Gas turbine installation
WO2009000581A1 (fr) 2007-06-22 2008-12-31 Valeo Systemes Thermiques Module d'echange de chaleur pour deux circuits d'echange de chaleur
EP2492471A2 (fr) * 2011-02-28 2012-08-29 Pratt & Whitney Canada Corp. Récupérateur de moteur à turbine à gaz doté de connexion flottante

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB624676A (en) * 1947-03-06 1949-06-14 Heat Exchangers Ltd Improvements in air preheaters and like heat exchange apparatus
FR1452128A (fr) * 1964-07-13 1966-02-25 Gen Electric Dispositif de récupération pour les moteurs à turbine à gaz
US3831374A (en) * 1971-08-30 1974-08-27 Power Technology Corp Gas turbine engine and counterflow heat exchanger with outer air passageway
US3894581A (en) 1973-04-16 1975-07-15 Garrett Corp Method of manifold construction for formed tube-sheet heat exchanger and structure formed thereby
US4229868A (en) 1978-10-26 1980-10-28 The Garrett Corporation Apparatus for reinforcement of thin plate, high pressure fluid heat exchangers
WO1983003663A1 (fr) * 1982-04-19 1983-10-27 North Atlantic Tech Echangeur thermique a plaque flottante
CA1193593A (fr) * 1984-05-08 1985-09-17 Jonathan P. Maendel Echangeur de chaleur
US20050097881A1 (en) * 2001-07-26 2005-05-12 Takanori Shibata Gas turbine installation
WO2009000581A1 (fr) 2007-06-22 2008-12-31 Valeo Systemes Thermiques Module d'echange de chaleur pour deux circuits d'echange de chaleur
EP2492471A2 (fr) * 2011-02-28 2012-08-29 Pratt & Whitney Canada Corp. Récupérateur de moteur à turbine à gaz doté de connexion flottante

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KNOTT ET AL.: "Fügetechnische Herausforderung bei der Herstellung eines Lanzetten-Wärmetauschers", DVS, vol. 237, pages 107 - 110

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108798899A (zh) * 2018-06-13 2018-11-13 武汉英康汇通电气有限公司 微型涡轮发电机
CN110006243A (zh) * 2019-04-16 2019-07-12 广东技术师范大学 一种蒸发器及果蔬干燥系统
CN110006243B (zh) * 2019-04-16 2024-04-02 广东技术师范大学 一种蒸发器及果蔬干燥系统

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