SA99200510A - A method for the recovery of heat rtom products of combustion of a fuel, a system therefor, a start up device and a burner assembly for said system - Google Patents

Abstract

A method and system for recovering heat from fuel combustion products at a high temperature to another liquid at a relatively lower temperature are detected. 1- The directional velocity of hot flue gases, from fuel combustion, is increased by compressed air strengthened by the turbocharger, to The fuel is in the combustion stage. 2- The high pressure air of the fuel burns in the locked space, adjusts the fuel combustion rate to match the amount / pressure of the air, in order to obtain a stable combustion condition, where the fixed flame is considered to be of smaller dimensions as stated. 3 - A small portion of the combustion temperature is cooled and transformed A relatively cooler external liquid is held and surrounds the stated combustion space, the combustion products are passed through the first heat exchanger, a major part of the heat of the combustion products is recovered, and indirectly converted, by the thermal transfer of the load in the first heat exchanger to the external liquid 4- The partially beneficial chimney gases that come out from the mentioned first heat exchanger are passed through the turbocharger / turbocharger turbine, and the fresh air of the partial heat energy content is converted to high pressure, where it is recovered as Add the remaining heat essentially through the mentioned second heat exchanger, and also by heat transfer (Figure 1).

Description

1 Full description A method for recovering heat from fuel combustion products, and a special device for it; And a means of operation and combustion device assembly for the aforementioned device Background of the invention This invention relates to modifications in the design and construction of incendiary heating devices such as steam generators » hot water boilers » thermal oil heating devices » water heaters or any heating devices Other liquids and other equipment also includes combustion gas generators such as direct combustion steam absorption heat pumps. In this invention, scalding heaters are compressed using an innovative method. It is known that the use of high vector speed in the load sector of the heat transfer equipment results in an increased thermal transfer coefficient, which in turn reduces the surface area of the thermal transfer. The dimensions of the flame are few. While we know that if the combustion chamber pressure increases, there is a high risk of high pressure drop when the combustion chamber pressure and the directional velocity of the flue gas increase. And in this invention, “it is expected that it will result from the incorporation of high known methods without the use of external stimulus energy,” the ol pb devices may be pre-compressed to generate pressure. Incendiary heating » by using a large change in its dimensions, and an operating device of the previous invention was presented. And a proposal for a new burner assembly for the mentioned modified design of the incendiary heating device, and it is preferable to use a turbo heater [1 turbo compressor] in a new way. E| It is usual » that all scorching heating devices such as steam generators » thermal oil heating devices » contain air heating devices. etc .; On the following main elements related to the process: Heat transfer or fuel combustion stove 0 b) Heat transfer surfaces in both the radiative sector and the convective sector. and be surface. Radiant heat conversion is a flame » also used as a combustion chamber

c) Fan or blower to monitor pressure drop (hydraulic resistance) This system includes a burner as well as a gas passage through the heat transfer surface. Gy) the state of the normal airflow system; The pressure drop corresponds to the intake stream produced by the stack. There are practical limitations to the design of this system » as a result of the high directional velocity in sector 0 of the load leads to a high pressure drop and requires high fan power. Therefore, a better balance must be struck between the fan power and the directional speed used in the convection heaters. It is known that the higher directional velocity in the load sector may produce a higher heat transfer coefficient in the load sector. It is also known that the higher the pressure in the combustion chamber, the smaller the dimensions of the flame. Nor is it practical to operate combustion chambers less than around you monn 0 mm. Without charging as the person may pay a fine as a result of the fan power to dF of operating costs. This tradition is followed in the design of incendiary heaters, with some exceptions where high fan power is tolerated in order to obtain the advantage of the reduced size of the heater if space is not available. . Accordingly, reaching the maximum allowable drop in pressure in the system; One has to accept the size of the furnace based on the dimensions of the flame and the maximum possible directional velocity of the carrying area. The maximum directional speed is based on the available top. The turbocharger/turbo compressor has been in use for a number of years and is mainly used to boost the combustion air pressure and quantity of internal combustion engines (de diesel engines). By using the en A supercharger, the power of diesel engines is enhanced as a result of pumping 0 more air into the combustion chamber Ig, which in turn allows more fuel to be burned for the same engine volume. The turbocharger consists of the turbine sector and the compressor sector. rotate in the same column. The turbine section receives the flue gases from the engine before it is ejected and the force generated as a result of gud is used in the temperature and pressure of the flue gases separately for the purpose of combustion pressure of the inlet combustor.

And in the present invention it is assumed that the supercharger ou A) / compressor (oA) can be used in place of the fan to create high pressure combustion air using the residual temperature and pressure in the exhaust gases in order to generate the power required for the compressor. Accordingly, it is expected that the turbocharger will be used preferably in scorching heaters, which cause a substantial reduction in the size of the scorching heater. In the internal combustion engine, it is not necessary to operate the turbocharger from the start. The engine may run without the sa A supercharger as it cycles at the normal normal drop indicator 3 if sufficient gas pressure and quantity are developed; The turbocharger can be direct. Accordingly, the operating system for internal combustion engines has been installed tightly. Promise 0 The use of the turbocharger on the incendiary heater » an innovative method of operation is required and in the absence of the fan there is no way to ignite the burner when the st charger is turned off. The invention JU also describes the new operating system. The combustion system consists of a fuel-burning stove. In the traditional combustion system, the heaters are operated at an air pressure not exceeding 0000 mm. And without charging. The designs of the stoves are well constructed ve to be operated under these pressure conditions. When using a turbocharger, the combustion chamber is operated at a higher pressure, which requires a different design of the burner. If the incinerator is pressurized with a turbocharger » one needs a suitable burner system. Therefore a new burner assembly was installed to operate the combustion chamber at a higher pressure. It is preferable that the operating system of the special turbocharger “Sle burner heating” is suitable for burning multi-fuel 0 such as FO, LSTHS, 10,150,10 h away from gaseous fuels such as natural gas 1706; biogas; brother . Accordingly, the present invention relates in one aspect to heat transfer equipment. On the other hand; The present invention relates to a new operating system for use in modified heat transfer equipment. Yes, and in a third aspect related to a new way to use the turbocharger / turbo compressor system.

— 0 cm In a fourth aspect this invention relates to de gant. A new burner for use in modified heat transfer equipment and other heat transfer equipment. It is known that in order to obtain the normal type heat transfer equipment depends on the special convection and radiation transfer. 0 Despite the use of thermally conductive radiation transfer equipment, there are advantages/limitations/disadvantages; Some of them are mentioned in the following: a) They require equipment and components of a large size and do not increase the initial costs of equipment, fixtures and space. b) the heat transfer coefficient is limited as it depends on the flue gas conditions; In particular, it is determined by the directional velocity of the penetration products (flue gases) in the load segments used for heat recovery. c) There are certain requirements for the electrical power of the combustion duct fan. 6 A certain amount of excess air PS has an effect on the overall efficiency. The furnace must be larger in relation to the large dimensions of the length and diameter of the burner 1. 6 The flexibility of Tels for many applications is determined by several constraints. A change in the design of heat transfer equipment in the form of a modified small-dimensional heat transfer equipment is proposed.

Accordingly, the main purpose of the invention is to provide modified thermal transfer equipment that is compact and cost effective. The other purpose of this invention is to introduce heat transfer equipment that requires less heat transfer area than the known equipment and at the same time guarantees a higher heat flow/0 heat transfer coefficient. In addition to the other purpose of this invention, which is to provide heat transfer equipment that has reduced weight and total volume when compared to the known equipment, while ensuring other purposes, in addition to canceling the main part of the electric energy combustion by adding a turbocharger / turbo compressor in the system. Another purpose of the invention is to provide heat transfer equipment that requires lower operating costs. So that make the equipment and operation more economical. Furthermore . There is another purpose of this invention which is trimming the modified heat transfer equipment that has greater flexibility of operation and flexibility to cope with the many applications Je steam generators, hot water generators, thermal fluid heating devices » air heating devices \o hot gas generators » pumps direct thermal incineration of vapor absorption ¢ etc. Another purpose + FAB is thermal conversion equipment that can be used for multiple fuels such as LDO, FO, LSHS, 1150 » H. OR ANY LIKE LIQUID FUEL WITH FUEL 0 WITH ANOTHER PURPOSE » It provides a new first-cycle drive mechanism for the turbocharger/turbocharger matched with and compatible with modified heat transfer equipment.

In addition to the other purpose; It is to introduce a new design of the burner in order to obtain efficient burning by means of smaller dimensions of the flame than those known in the art. Furthermore, the invention has another purpose of trimming a modified heat conversion process to a higher heat flow or heat conversion rate/coefficient that requires electrical energy to blow combustion air through equipment and at the same time has higher flexibility to be compatible with numerous applications such as steam generators. Hot water generators, thermal fluid generators » air heaters » hot gas generators, direct burning heat pumps for steam absorption » etc. and other applications easily and economically. These are clear for other purposes and purposes from the following paragraphs: 0 general description of the invention lib of the present invention; A method for recovering heat from the combustion products (flue gases) of fuels at a high temperature is presented; from another liquid at a relatively lower temperature; The following steps include: a) Increasing the vectorial velocity of the hot flue gases ¢ from the combustion of fuel which is 10 folds too high” by feeding compressed air converted into powder by turbocharger/turbocompressor to the fuel at combustion velocity. b) Exposing the pressure air Jl of the fuel to the combustion step in the closed space. c) Adjusting the fuel combustion rate to match the amount/pressure of the air in order to obtain a stable combustion state.

d) Producing and keeping a fixed flame with dimensions (size/diameter) that are smaller than it should be within the aforementioned combustion range. e) Recovering a small part of the combustion heat and converting it indirectly into a relatively colder hot liquid that is kept around the enclosed space of the aforementioned combustion. © f) Passage of the invention products through the first heat exchanger.

g) Recovering a major part of the heat of combustion products and converting them indirectly ». By convection heat transfer in the primary heat exchanger device is predominantly to the external fluid. Which is the same aforementioned liquid surrounding the closed space of the burner or a totally different liquid.

0 c) Partially exhausted flue gases exiting from the aforementioned first heat exchanger pass through the turbine of the turbocharger / turbo compressor and the partly conversion of the energy content (SAH) of the flue gases into mechanical energy in the turbine of the turbocharger / compressor Cot A which uses open air pressure to high pressure compressor of the turbocharger/turbocompressor installed in the same shaft as the compressor oA

ds to be used as combustion air in the stove in applications designated for that, then through a 0 device. Second thermal i) Receiving partly exhausted heat and flue gases in the second heat exchanger and transferring them indirectly to the external fluid; which is the same surrounding liquid. contained in the enclosed compartment of the burner and the first heat exchanger or a completely different liquid

Ys k) Substantially all residual heat is recovered by means of the aforementioned second heat exchanger and through ply heat transfer

(J) Allowing all heat exhausted flue gases to pass to the exhaust / chimney. The cooled compressed air shall be at a high pressure of R. h? bar, and the vector velocity of the flue gases in the gas conversion sector shall be between 30006 = 00 m / sec. It is preferable that the ratio of Lubricated compressed air for combustion stage time between Vege: 1 to 1:11.

0 The gas is selected from HSD, LDO, FO, LSHS a » or a gaseous fuel such as [LPG natural gas] a . It is ignited by an experimental gas burner, which in turn is ignited with the help of ignition sparks through a thermal transfer device. Air is fed to the combustion flame at different steps in the enclosed space of the aforementioned combustion.

iPod also provides a system for the conversion and recovery of heat from combustion products (flue gases) yo. : With fuel in the radiating part and two stages of the load sector, which includes in total the following: / with a burner group via fuel, connected when operating in the upper direction to the turbocharger (1) mentioned in the starting mechanism and connected to the co A group of the turbocharger and supplies the charger / compressor The aforementioned fuel-filled stove is operating in the lower direction with a heat transfer and recovery system

10 which has one or more heat exchangers preferably two of a convection heat exchanger type and an exhaust pipe or stack for exhaust flue gas exhaust; The said starting device includes the air outlet assembly » feed line for the outlet air supply; External fuel supply source » gaseous fuel burner / SW and mixing chamber assembly connecting said starting device with said turbocharger / compressor on A and said heat recovery system; and includes

0 in the said fuel burner assembly “gf burner” source of ignition such as a ignition switching device; inlet pipe ol bl turbine; Basic enablement place for flaring rod housing and assembly

1. — - ESL and secondary housing made of combustion chamber; It contains the secondary mixing sll group and the general deployment group. Two heat exchanging devices of the bearing with said combustion chamber shall be installed together in order to house a general fluid in the same enclosed space or different fluids as described hereinafter in Separate enclosed grooves for heat absorption by heat transfer in the convection path

radiation. The system is not limited to steam generator ¢ hot water generator 1 thermal liquid heater ¢ ol pb heater) hot gas generator » direct burning vapor absorption heat pump or similar equipment or combinations thereof for covering various jumped surface turbines

,. Heat includes without limitation the installation of the flue pipe 0 . The burner housing group shall be provided with a flame detection device and its opening for viewing at a suitable location. The secondary housing shall contain a curved front section; The aforementioned section contains the secondary, which is equipped to enter the secondary air in the corner of the ol bl, with a set of openings and vents to feed the . Suitable to the transverse axes of the torch

Vo cdl device for use in a system for the conversion and recovery of heat from combustion products (flue gas) to fuel in the manner described below » includes with air supply group as output device » bast feed for external air supply source for external fuel supply starting burner and outlet chamber assembly When operating, the said starting device, the said turbocharger/turbo compressor, and the said heat recovery system are connected.

0 IN THE BURNER ASSEMBLY FOR USE IN THE SYSTEM OF HEAT CONVERSION AND RECOVERY OF THE combustion products (flue phase) of fuels in the manner described below includes SA burner ignition source

— \ \ _ such as the mentioned ignition transfer device; Inlet pipe oh bt compressed turbo ¢ primary housing for the burner rod knife and nozzle assembly and a secondary housing containing the steam upstream 9 , of ob Lid ie gost the secondary and the air diffusion group. The burner group shall be provided with a device for detecting the flame and a hole for viewing in appropriate locations. 0 The place of the secondary housing contains a curved front section, and the aforementioned section contains a group of openings or vents to feed the secondary air, prepared to enter the secondary air at an angle suitable to the transverse axes of the torch. Figure A: Schematic diagram of the preferred arrangement of Obey's heat transfer equipment. It is based on the technology of the modern invention Super Se 0. Figure B: Shows the preferred arrangement for the new burner system. Figure C: Shows the new first-cycle starting system of the turbocharger/compressor: Co A)

SU The present invention includes but is not limited to these preferred turbines only alg arrangements and there may be changes in those arrangements / designs. While the present invention depicts the use of such arrangements/designs in which a turbocharger/turbocompressor is used instead of a fan or blower to deliver combustion air at high pressure for one purpose, which is to compress the scorching heater by operating the combustion chamber at high pressure and section pregnancy at. High andl speed

-11- A brief explanation of the drawings With reference to the attached drawings that illustrate the broad idea US The invention will be explained. It is not limited to it lly with reference to the specific application only Schematic diagram of heat transfer equipment based on “Ps” technology and in the drawings; Explain. The modern invention form b; The new burner used in the equipment shows Figure C; Demonstrates a new starting system designed for the initial cycling of the turbocharger/compressor. Turbine Detailed description Figure A relates to the overall system of newly invented heat transfer equipment. In order to cycle the turbo-compressor first (1). The external air source (1) is used for less than 1 second only. The air generated by the compressor (A1) is available for combustion fuel in 0. The newly invented burner (8 1) is shown Its details are in Figure B and described in the following paragraphs

Gib controls the ly » of the burner ol dl and after achieving sufficient pressure in the inlet pipe 1 with the help of the ignition spark in the gas fruit (Y) pressure transducer (9) » the ignition of the fuel pilot burner ales yl through the ignition transformer (4). The valve is actuated and the power released by the fuel increases from . (A) Fuel by combustion in Ty combustion chambers, which allow operation under stable and self-sustaining conditions. (1) uA The speed of the compressor is adjusted after obtaining a constant speed, and the rate of fuel combustion increases. And with (1) closing the starting system 0 higher speed is available correspondingly (1) me A) increased fuel combustion rate » the compressor achieves more air for combustion. At the full combustion rate, the rate is obtained

- 1 (V) Goma) and compressor absorber (A1) of the compressor. (1) gd the speed of the compressor at pressure and flow rate (1 4) and sends it to the burner (V)eld) fresh air through a filter

F (A) through the pipe (0) and the burner (8) produces a very small flame inside the combustion chambers and is radiated (A). A small part of the heat is transferred to the external liquid (0) around the combustion chamber, and the heat is transferred from Route (11) Combustion products through the first pressurized heat exchanger 0 Determining the size of the first heat exchanger (V0) of the convective heat exchanger to the external fluid depends on the flue gases with a high directional velocity in order to achieve a high conversion coefficient ( VY) for heat and conditions suitable for pressure and temperature. The turbine inlet (B6) with the turbo compressor is sufficient for the rotation of (Vy). The enthalpy of the flue gases available at the turbine inlet is (7) followed by the compressor (1) so that the system is self-contained without a fan. External electric 0 to exchanger (VF) circulation Then the flue gases pass from the turbine (B6) through a medium pipe (V0) and the remaining heat energy is transferred to the external fluid (1) pressurized ly heat The high directional velocity of the flue gases (VY) depends on determining the size of the second heat exchanger to achieve a high thermal conversion coefficient and to achieve the optimal use of the enthalpy of gases and time D The external liquid is the same as the special one. (V1) the chimneys before being discharged into chimney 1 or different from it by means of certain conditions as required. (VT) and (11) with heat exchangers. Figure B relates to the newly invented hearth as part of the specified overall system In form A; burner (VA) burner rod and set (VV) jets of housing (14) and burner consists of primary diffuser assembly (Y0) ignition transformer (8) ¢ inlet pipe Air ¢ (©) (0%) and (VY) an aperture for viewing; a flame detection device » (V0) Secondary air mixing group (V1) 0 (A) Housing the flame produced by the burner in the combustion chamber The combustion chamber is installed on the eld, and the housing (17) is designed to withstand the high pressure of (VA) the combustion rod, and the nozzles group (YT) is on the walls of the heat transfer equipment, the type of pneumatic / steam emitter, and the burner is used The burning pilot (©) is in the first ignition of the main fuel, and the pilot gas is ignited with the help of an ignition transformer (4).

EEE

Air required for combustion of the main fuel from the compressor (0) of the turbo compressor primitive turbulence (VA) db) through the air intake pipe (0) and produces a diffusion group (7) powerful in order to obtain an overall mixing For primary air and primary fuel and the secondary mixing group is at a directional velocity ol bl Small holes at an appropriate angle push (Y) secondary air (A) high into the flame.The specific regulation completes combustion instantly inside the combustion chamber oo A detection device (VV) senses the combustion chamber connected to the first pressurized heat exchanger in the burner and gives a signal to the control system to complete the process. located in the housing (7 1) the burner through the viewing hole Figure C with details of the new starting system as part of the total system as shown in Figure A. Burner | (YE) for fuel supply Cissy The starting system consists From the external air supply (7); 0, the intake manifold (716)), the butterfly damper (77), and the ¢ chamber assembly (Yo) to start (YA) the mixing and a small amount of air is supplied at a pressure of Aali informs Hawa Li © bar through a supply group, and as a result of the absorption resulting from the device such as the output device, the L (Y) of the outside air is approximately twice the amount of air that was sucked from the air through the absorption hole (776) sufficient Vo as combustion air To ignite the stretched starting fuel by means of a special fuel supply pipe (4 7) burner at (YY) mixing chamber de ga to (YO) starting and the combustion products of the starting burner pass 18 m . The combustion chamber assembly is connected between the heat exchanger 0 high temperature of about combustion ols and the turbo compressor (1). The energy content (11) is the first compressed and with the first circulation. (1) sa A The compressor (Te) is sufficient for the first rotation of the turbine vy. The speed (VE) increases and is sent to the main burner (V) of the turbine (B6) through the filter of the turbine compressor (1) and achieves stable conditions where Its operation is self-restrained The case procedures are completed at this temperature (V0) and the air supply to the starting burner located at the opening (YY) is closed The outside air supply is closed and the butterfly idle (V0) is closed YT) absorption Yo

“Ve - oF Detailed description of the equipment of the invented process: a) In order to verify practically the realization of the several purposes of this invention, two Onn with the same heat outlet have been installed, one of which is based on the traditional technique and the other on the invention. The aforementioned idea has been verified under identical conditions through experimental studies on the aforementioned structures, and the results of typical designs are as follows: Table 1

New Traditional Burner Dimensions Diameter Da Av Da Length BEBE VJ Furnace Dimensions Diameter RE cr ; da cm l? Rh Yd Surface area of heat transfer Toy i To Total heat transfer coefficient kcal/hr m hr ?; hours Total thermal efficiency 0 AY cumulative b) In order to verify/compare partial loading performance; a The results of the typical designs were as follows:

11-- schedule? : Experimental data loading system into image 70 from design conditions

This channel is the combustion air pressure of Keller Pascal P3 | P2 1 PL of completed NEN

The total hydraulic resistance is set v VY v ¢ | DP3 | DP2 | DPI Replacement Temperature (Nl) Turbine 1 included | DP3 | DP2 in the case of a new technology

kilopascal

Electric energy consumption for blowing Nil air NiL | Ni 1 xp|.,ap Na

Loss of thermal content of terpene NA | empty | Kha | watt | For sat tv, the rise in the heat content of the compressor | Hala 1 Hala | Ghala | watt | order | tv A = e say n | ot | rah | our ljrk | vat

NA: Not applicable

Comparing the data presented in Yoo's table) and conclusion:

From SUL's introduction and notes on the size/shape of the torch; conversion surface areas

Thermal, combustion air pressure, etc... It is concluded that protection elements have been checked

The present invention is practical and that it is possible to reduce the dimensions of the oven / the area of heat transfer according to the amount using this iron idea without the need for a combustion air fan with external energy. These results are typical and the joint enhancements enable other arrangements/designs/applications.

117 - Detailed description: The heat transfer equipment used in these applications is used, such as a steam generator; Hot Water Generator Thermal Fluid Heater ¢ Air Heater » Hot Gas Generator » Direct Burning Steam Absorption Heat Pumps etc... Traditionally Radiant as well as Convection Heat Converters. The combustion equipment used in the alld is the traditional hearth which produces an intrinsically large flame. The combustion chamber (OA) is designed to accommodate the flame produced by a conventional burner » and an electrically rotating fan is used to supply combustion air through the burner and to manage combustion products through the surfaces of the combustion chamber and the convection heat exchanger; The volume of the combustion chamber is large, Cli 0, as a result of the limitation imposed by the dimensions of the burner, and the heat exchanger surface of the load and the total heat transfer equipment is relatively large, as a result of the imposed limitation of the power requirements of the fan. Traditional stoves require about 90% of Yo-Yo air to complete the combustion of the fuel. The heat transfer surface area requirements are high due to the relatively low coefficient of decomposition. Vo and directs attention towards achieving a higher heat transfer per unit area sculpted under a specific set of conditions, Gt, by means of a modified process if compared to known processes. In order to achieve the aforementioned purposes, it was decided to enhance the thermal transfer of the convection by increasing the vectorial velocity of the combustion products on the surface of the thermal transfer. The vector velocity of the combustion products (flue gases) was increased to the level You so 500 m/sec if 0 compared to the lower level of the velocity of the combustion products in conventional systems and the combustion air pressure was increased in order to overcome the hydraulic resistance generated in the heat transfer equipment and from In order to achieve a reduction also in the size of the flame.

- 18

This results in a reduction in the heat transfer area and thus the volume of the heat transfer equipment

Such as steam generators » hot water generators ¢ thermal liquid heaters » slab heaters ¢

Hot Gas Generators » Steam Absorbent Direct Combustion Heat Pumps.

The use of the higher flue gas velocity increases the heat flow coefficient/variability

temperature a number of times. This results in a substantial reduction in the area of thermal transfer

. On 203 heat transfer equipment may be reduced in size a number of times Fels

An increase in the flue gas directional velocity increases the hydraulic resistance in the flue gas passage if

Compared with conventional radiation and convection heat transfer equipment. The air at substantially higher pressure must overcome that resistance and this is provided by using the 0 turbocharger / turbo compressor in the flue gas output. It heats the high-pressure water from its advantages

fuel combustion. The use of a turbocharger/turbocompressor also reduces the need for a fan

Wl gS is not managed to be an obligatory component of conventional heat transfer equipment.

In a turbocharger/turbocompressor, the turbine uses energy from the flue gases to

Operate the compressor installed on the same column. The total enthalpy loss of the 1 flue gases is recovered to provide catalyst power for the turbine of the turbocharger/compressor om A with a high

The enthalpy of the compressed air generated by the compressor of the turbocharger /

The compressor se AI which is sent in the form of combustion air to the system and therefore » there is no loss

for power outside the system. Heat is recovered from the flue gases at the turbine's own outlet

with a turbocharger/compressor co A) to reduce the flue gas temperature to a level 0 comparable to that of any conventional heat transfer equipment.

And in order to achieve the purpose of pressurized heat transfer equipment; It is necessary to develop a system

New stove combustion air at pressure also reduce the dimensions of the flame , the stove system is designed

new in order to achieve these purposes. :

In order to carry out the commissioning of the above-mentioned equipment, a mechanism unknown to Ye was used now. The turbocharger/turbo compressor used in this system is initially driven

1 9 —_ _ external air source for less than 0 seconds. During this period the operation of the turbocharger/compressor becomes self-sustaining and the external air source is removed. The attributes mentioned may be in the said description or in the claims and/or in the accompanying drawings. separate or combined. Material to achieve the invention in a variety of forms.

Claims (1)

Elements of Ld after the description of the invention » The elements of protection are as follows: ¢ A method for recovering heat from the combustion products (flue gases) of combustion 1-1 at a higher temperature to another liquid at a relatively lower temperature that includes the following steps: Increasing the vectorial velocity of the hot flue gases » from the combustion of the fuel » the rate is ) 1; more multifold than is currently possible; By feeding compressed air supplied with energy. By means of the turbocharger / turbo compressor to the fuel in the combustion stage 0 . ?) Exposing high-pressure air to the combustion step in a closed space + adjusting the fuel combustion rate according to the air quantity / pressure in order to achieve combustion conditions (* . A constant A Lede (length and diameter) that is smaller than what can currently be sled producing a flame with (+4) . In the aforementioned closed space for combustion 11 | #) recovering a small part of the heat of combustion and converting it indirectly into an external fluid 1 relatively prominent suspended around the missing space of combustion . 1" 1) Passage of combustion products through the first heat exchanger 4 #) Recovery of a major part of the heat of combustion products and their conversion indirectly 0 in a supportive manner by means of the convective heat transfer in the said first heat exchanger 0 to the liquid External » which is the same liquid surrounding the enclosed space for combustion 1 or a different liquid LS (A VA) The passage of partially heat-exhausted flue gases exiting from the aforementioned first heat exchanger through the turbine of the turbocharger / turbo compressor and inverting the heat energy content 0 Partial flue gases are converted into mechanical energy in the supercharger turbine [ou A] the turbocharger YY compressor which in turn is used to compress the air compressor to high pressure in the YY compressor of the turbocharger / turbocompressor mounted on the same shaft as the turbocharger with the YY turbo compressor to be used as combustion air in the burner in dedicated applications and then “yy - ve” through the second heat exchanger. Yo +) receiving heat from said heat exhausted flue gases the second heat exchanger YY and transferring it indirectly to the external fluid which is same as said fluid Lt 7" in the enclosed space of combustion and the first heat exchanger or totally different fluid. (01 YA) recover substantially all residual heat by means of the second heat exchanger and by means of ya by means of the convection heat converter as well” and finally; (VY ©) allow all heat depleted flue gases to pass into the exhaust/stack. 1 ?- The method as stated in Claim 1 » where the compressed old turbine is a maximum pressure of J CO bar and the directional velocity of the flue gases in the heat transfer Y section is between Youn = .8 m / s » It is preferable that the rate of compressed air feeding the fuel at the combustion stage be in the proportion of .0:1 Veo: 1 1 #- the method as stated in the protection element?), where the fuel protection is from HSDLDO/FO/LSHS "H" But it is not limited to that » or gaseous fuels such as 6/ YT natural gas, etc. It is ignited by a pilot gas burner, which in turn is ignited with the help of sparks ¢ by means of a transformer ignition. 1 4- The method as stated in the protection element? Where the air is fed to the combustion torch at different steps in the enclosed space of the aforementioned combustion. 1#- A system for converting heat from combustion products (flue gases) to fuel in the Y section radiant and two steps in the convection section implicitly. / when operating in the upstream direction with the turbocharger (Jal) of the fuel burner assembly (1) the turbo compressor with the starting mechanism » and is connected to / ou A); the turbo compressor » and the lower-current supercharger with a conversion and recovery system old is supplied with the aforementioned fuel burner group for operating in the heat that contains one or more heat exchangers, preferably two; Of type 0 thermal allowance for convection and an exhaust or chimney for the removal of used flue gases; Said starter device includes air outlet assembly » feed line for outside air supply; A Jai source for external fuel supply » water/gas fuel burner and mixing chamber set 9 When operating said starter device with turbocharger / turbo compressor and 0 mentioned heat recovery » The said fuel burner assembly includes a pilot burner; 11 ignition source such as the ignition transformer ¢ the intake pipe of the compressed air turbine » 1 primary housing for the burner rod housing and a set of nozzles and a secondary housing made of the combustion chamber; Contains 64 mixing kits 1 +- The system as stated in the protection element H, where the two heat exchangers mentioned for the load and the mentioned combustion chamber Lg are fixed in order to house a general liquid in the same closed space or different liquids as mentioned above in separate closed spaces to absorb heat from; Convection heat exchanger route. cor A system as stated in Claim 0 and + which is » Steam Generator » Water Generator 7-1 Thermal Liquid Heater » Brigade Heater » Hot Gas Generator » Direct Burning Heat Pump for Water Absorption or similar equipment or unions Among them, but the y column is not limited to that, in order to contain the numerous arrangements of heat transfer surfaces, including Turkish flue pipe, but it is not limited to that ° DC 1 8- The system as stated in Claims 0 Hv 7; 1 4- The system as stated in the elements of protection is CA, where the said housing (SH) contains a curved front section; the mentioned section contains with a set of orifices or ? with fuel in the manner described above » includes the YT air supply assembly as the outlet device; feed line for external air supply; source of supply EXTERNAL FUEL » STARTING BURNER AND MIXING CHAMBER ASSEMBLY AT STARTING UP AT THE SAME STARTING DEVICE WITH THE SAME TURBO CHARGER / COMPRESSOR AND THE SAME HEAT RECOVERY SYSTEM. de putt 11-1 Burner for use in a system for converting and recovering heat from combustion products (flue gases) of fuels in the manner described above Led; includes pilot burner; “ignition source such as ignition transformer” compressed air inlet pipe ; A primary housing for the burner bar SU ds pasty and a secondary housing housing containing with a group 0 secondary air mixing in oll updraft and an air diffusion group. 1-1 Burner group as mentioned in the protection element VY, whereby the place of residence of the “burner group” shall be provided with a flame detection device and a viewing hole at appropriate places. — Y Y _— 1 burner group as stated in Claims 11 and 17 » where the aforementioned “secondary housing” contains a divided front section » the said section contains a group of ¥ openings or vents 1 4- The Jed method and the recovery of heat from the combustion products (flue gases) of fuel Y as mentioned above essentially. 1 1 Operation ey device for use 3 The aforementioned system Laud ¢ Jad and recover heat Y from the combustion products (flue gases) of the fuel as above Y substantially; with reference to Figure C of Attached Drawings 11-1 The burner assembly for use in the aforementioned system for transferring and recovering heat from “combustion products (flue gases) of the fuel” as mentioned above Ld substantially with reference to Figure B of the attached drawings. -17 1 A system for transferring and recovering heat from combustion products (flue gases) of fuel Y as mentioned.