FI109554B - Heat source - Google Patents

Description

109554 Heat production device

TECHNICAL FIELD The present invention relates to a heat production device of the kind specified in the preamble of claims 1.

5 Older technology

It is generally known that the efficiency of heat production or boiler plants can be substantially increased by the connection of so-called condensers as ancillary equipment. In a conventional condenser, the water vapor that the hot gases of the heat production or boiler plant exhibit is cooled to a temperature below its day temperature by means of various heat exchange constructions, usually convection surfaces of different kinds exhibited by the condenser.

The heat energy bound by the flue gas is released during this cooling as well as at the transition of the water meadow from its gas phase to its liquid phase.

Boilers with subsequent condenser easily become Large and heavy as they require considerable convection surfaces. Thus, the boilers also become expensive. The known solutions also offer a low temperature difference and low k values of the convection surfaces, which results in a poor heat transfer.

In a particular embodiment of the condenser, a so-called spray condenser, on the other hand, the heat bound to the hot gases is transferred directly to small liquid droplets produced in a nozzle exhibited by the condenser. However, known spray condenser designs are complicated in their design: V: and usually space-consuming. Furthermore, since well-known constructions are usually • optimized for washing the hot gases, which mainly comprise smokers, they are also subjected to considerable soiling. This soiling on · ···. Of course, the efficiency of the condenser is negatively affected, whereby the repetitive cleaning of the condenser required to ensure its operation is costly.

Due to their space-demanding constructions, current condensers are usually also intended to be used primarily in an industrial environment, whereby they can be adapted to small heat plants or panels intended for small-scale heat production.

• ·

PROBLEMS * With the present invention, the problems of the previous solutions can be substantially avoided, while at the same time an easy-to-use, relatively small and, above all, light heat production device with an integrated condenser can be obtained.

This is achieved by means of a heat production device having the features defined in the claims of the present invention.

Particular features of the invention are the features mentioned in the characterizing part of claim 1.

Essentially new in this invention is that the combination of an inventive boiler part and a condenser lying on top of it makes the total material heat transfer surfaces smaller and the heat production device thereby easier. This can be attributed to the fact that the heat transfer of a certain heat effect from hot gases to that in the heat production device - a circulating heat absorbing medium - often water - occurs very quickly in the initial part of the heat production device, the boiler part. This is naturally due to the large heat differences that initially exist between the hot gases and the heat absorbing medium. The heat transfer (generally denoted Q) is hereby dependent on the heat transfer surface (denoted A) multiplied by the heat transfer number (k value) of the device multiplied by the temperature difference of the hot gases and the heat absorbing medium (denoted At), i.e. Q = A * k * At. In a heat transfer between a gas and a liquid medium, the heat transfer rate is relatively low compared to a heat transfer between two liquid media - about a tenth of this value - but very much added - about one hundredth according to empirical experiments - compared to a heat transfer between a gas and a tile of this introduced spray of liquid droplets. Heat throughput figures for different cases are given in the heat: 25 technical papers.

According to tests performed, 50% - 90% of the total heat output of the gases is transferred into a boiler part according to the present invention. This means that the gases are cooled down to a temperature of about 200 ° - 500 °. The gases are then directed to the condenser located above the boiler section where a heat exchange with high heat · ···. The throughput number can be utilized as well in the nozzle portion of the condenser at a heat exchange. ···, between gases and injected liquid droplets, as at a heat exchange 'l' between two liquid media in the lower part of the condenser, where connected heat exchanger is used to cool the coolant extracted from the spray part, the so-called nozzle liquid. If such a liquid is used: v. 35 is usually water.

3 109554

This rapid heat transfer thus results in the fact that considerably smaller heat transfer surfaces are required in a heat production device according to the present invention. Since such heat transfer surfaces are often made of high-alloy steel, this means at the same time considerable savings in construction costs due to a smaller raw material supply but also a shorter construction time.

Thus, it is characteristic of a device according to the present invention to be able to handle high incoming gas temperatures which can be conducted to an inventive boiler part in order to quickly and efficiently utilize the heat energy extracted from the fuel. After a heat exchange in the boiler part's water tank, the still hot gas is circulated to the condenser for further closed-loop heat recovery.

In addition, a device according to the present invention has a device for collecting, separating and purifying the coolant used in the condenser.

Advantageous embodiments of the invention are the subject matter of the appended independent claims.

In a description of the present invention, the term "convection heating system" refers to a system of radiators which may be as well wall-mounted as are preferably built into the floor. The term "heat exchange means" refers to various types of circulating vessels arranged in the boiler portion in which various liquid media are circulated to collect heat energy. Such liquid media are referred to as "utility water" and can be made of both tap water, radiator water as well known in the art: liquid medium used for heat distribution, such as, for example, glycol.

In the following description, the terms "up", "" down "," above "," below "and further directions in relation to the heat production device or its structural details are further referred to as shown in the accompanying figures.

. * ··. With the device described in the present invention, up ···. nose several significant advantages over the prior art. The design of the heat production device thus makes it possible to achieve maximum efficiency with minimized heat transfer surfaces, so-called convection surfaces, with a very: · ·· compact heat production device. Thus, the burn: v. The gas in new heat production plants is connected to the combustion space of the boiler part which has, on either side, annular convection surfaces which give good heat exchange properties.

In addition, by utilizing a condenser which is advantageously equipped with two nozzle systems in the heat production device, the draw is improved through the boiler part as well as the condenser. This means that high chimneys and soot can be avoided to a considerable extent. Also, since an inventive use of nozzles or nozzle systems improves drag, no condensing of the condenser is needed, something that makes the design substantially more manageable than competing products. The arrangement with an overhead condenser also results in smaller heat losses from the top of the boiler.

By using high alloy steel in the design of the heat exchange means, leaching problems that occur, for example, in traditional tap water loops, are avoided. In this way, a tap water is obtained which is healthier, while the construction of the tap water to its pour strength is substantially better than traditional solutions.

BRIEF DESCRIPTION OF THE DRAWINGS The invention will now be described in more detail with reference to a preferred embodiment of the accompanying drawing, wherein | Fig. 1 schematically visualizes a condenser-provided heat production device according to the invention; Fig. 2 shows a cross-section of an advantageous embodiment of the boiler part of the heat production device; Fig. 3 shows a cross-section of a boiler part according to Fig. 2 taken along line A-A. Fig. 4 shows a cross-section of a second advantageous embodiment of the boiler part of the heat production device, and Fig. 5 shows a cross-section of a boiler part according to Fig. 4 taken along the line BB.

Preferred Embodiment

An advantageous design of a heat production device for combustion of fuel is exemplified in the following, wherein the structural parts of the heat production device are indicated by reference numerals corresponding to the reference numerals indicated in the figures.

/ 5 109554

A heat production device for combustion of fuel thus comprises a lower so-called boiler part 1 and an advantageous top of this connected condenser 2. The boiler part has a burner (not shown) which starts in contact with a combustion chamber 3 via a connection channel 4. combustion chambers have heat exchange means 5 and 6, that is, kari for receiving liquid - drinking water - to be circulated, for example, in a convection heating system, and kari for, for example, heating hot domestic hot water. These vessels are hereinafter referred to as radiator water vessels 5 and tap water vessels 6. The use water thus advantageously comprises ordinary water, but may also consist of, for example, glycol, whereby an efficient heat exchange can be obtained in the radiator vessels.

In the preferred embodiment shown in the figures, the boiler part 1 comprises a substantially cylindrical structure having a center axis 7 arranged in a substantially vertical direction. Hereby, the radiator water vessels 5 and the tap water vessel 6 are advantageously arranged concentrically in the boiler part around this center axis. Thus, the tap water vessel advantageously forms a core in the boiler part, the tap water vessel being arranged to be at least partially surrounded by an inner radiator water vessel. In addition, according to Figures 1 and 2, the tap water vessel is advantageously arranged to be in contact with the hot gases circulating in the combustion chamber at its bottom 8. However, the bottom can also be at least partially common with the inner radiator water vessel.

The combustion chamber 3 consists of a substantially cylindrical chamber to which the burner is connected substantially in the tangential direction of the chamber. The combustion chamber is hereby limited by radiator water vessels 5 arranged at the casing surfaces of the boiler part, that is, at the side wall 9, bottom 10 and top 11 of the boiler part as shown in the figures. Furthermore, the combustion chamber is limited by the above-described tap water vessel and the inner radiator water vessel arranged therewith according to the figures. The combustion chamber can also be arranged to surround several internal radiator water vessels 5a according to Figures 4 · · ·. 30 and 5. In this case, the combustion chamber has one or more substantially cylindrical. dangerously annular radiator vessels arranged outside the inner radiator water vessel.

Thus, the combustion chamber according to, for example, the figures exhibits essentially cylindrical annular gaps 12 extending between the heat exchange / means and receives it in the tangential direction of the combustion chamber: Containing hot gases, which at least partly comprise hot flue gases. Such a concentric design of the boiler part's structures enables a high efficiency both in the combustion of the gases and in the heat transfer and ash separation of the same led into the combustion chamber from the burner.

The radiator water vessels 5, 5a are advantageously joined together to make circulation of the heated liquid possible and in this way equalize the temperature of the liquid. Thus, the radiator vessels can be connected to each other via specially arranged pipe lines 13 according to Figure 1 or via common upper and / or lower circulation parts 14 and 15 according to figures 2 and 4. The radiator water vessels and the tap water vessel 6 are further provided with pipes 16 and 17 respectively for circulation of the radiator fluid. and the tap water 10 to the respective radiators and taps (not shown). These pipelines have valves and thermostats 18 and 19 for controlling the flow of liquid.

The thermostats 18 and 19 are arranged to close in contact with the burner connected to the heat production device and thus regulate the burner's operation to avoid overheating the use water in the heat exchange vessels 5 and 6.

The hot gases produced during combustion are arranged that from the combustion chamber 3 is passed through at least one flue 20 to a condenser 2 advantageously connected to the top 11 of the boiler part 1. The top of the boiler will thus simultaneously constitute the bottom of the condenser which further improves the heat exchange in the condenser. . The smoke duct extends thereto to the upper part 21 of the condenser in accordance with Figure 1. The condenser thus comprises a substantially U-shaped structure which, in addition to the upper part, has a:; nozzle portion 22 to which the hot gases consumed via the flue are controlled. Underneath the nozzle portion is a bottom portion 23 provided by the condenser which is joined to the seal portion as well as the outlet portion 24 shown by the condenser. The condenser may comprise a structure according to Figure 1 having two substantially parallel cylindrical portions joined together. oriented towards the bottom of the condenser than -: * '\ · da. However, the condenser may, however, comprise a cylindrical or geometrically differently shaped structure which is divided into two with a partition; * ·. Substantially vertical portions joined in their orientation towards the bottom of the condenser. ···. all the way.

The gases flowing into the nozzle part 22 are arranged to pass through a member shown by the nozzle part, a primary nozzle or nozzle system 25, whereby the nozzle part is supplied with finely divided coolant 26, so-called nozzle liquid. At this stage, the gases flowing down into the '··' of the condenser bottom portion 23 come downstream. contact with small coolant droplets secreted downstream of the nozzle. A sufficient atomization of the coolant is provided by a circulation pump 27 connected to the nozzle. This circulation pump is thus arranged to control the pressure of the coolant flowing through the nozzle and further to the nozzle and gases flowing therein. The pump pressure should be as high as possible to give as small liquid drops as possible. The smaller the droplets of coolant that are excreted in the gases, the more efficient the heat transfer between the gases and the coolant becomes. Advantageously, the volume of the liquid stream through the nozzle is controlled so that a required amount of heat can be absorbed without the cooling fluid being extended.

Also in the nozzle portion 22, some flue gas components, including solid particles, such as soot particles, are transferred to the droplets of the cooled liquid, after which they can be recovered in a collection vessel exhibited by the lower end of the nozzle, a so-called insert 28. can be removed from the condenser 2 through a cleaning flap provided therewith.

The gases washed in the nozzle part are then arranged to flow from the nozzle part further to a construction part substantially parallel to the nozzle part, the outlet part 24. The outlet part hereby communicates with the nozzle part through openings at the insert 28. The outlet part is advantageously provided with a damper 29 for a retardation or throttling of the gases flow rate in the nozzle portion which affects the heat transfer from the gases to the coolant droplets in a very positive manner.

:; In cases where the temperature of the liquid collected in the bottom portion 23 of the condenser is higher than the dew temperature of the water vapor in the gases: a second means arranged above the damper 29 for bringing the gases into direct contact with coolant 30, i.e. a secondary nozzle or nozzle system 31. This nozzle is also advantageously directed in the direction of flow of the gases. The coolant flowing through the secondary nozzle causes the water vapor in the gases to partially condense in the outlet portion 24. In this way, no new coolant need be added to the device. The coolant flowing. · · ·. through this substantially upright nozzle, it is advantageous to circulate through: the insert to release solid particles from the nozzle fluid.

The cooling liquid 26 and 30 flowing to the nozzle systems 25 and 31 is advantageously arranged to be cooled with at least one heat exchanger 32: *. 35 and / or 33. Particularly important is that the coolant in the tiling of the outlet part is arranged, ···. said secondary nozzle system 31 is sufficiently cooled to obtain as effective condensation as possible. Such a heat exchanger 32 may be arranged to be immersed in the liquid accumulated in the bottom of the condenser, but the heat exchanger 33 may also be arranged outside an outer jacket 34. The heat exchanger comprises an air or air well known in the art. liquid-based heat exchanger.

Since the solid heat transfer surfaces in a heat production device according to the present embodiment are the sum of the heat transfer surfaces in the boiler part (1) - denoted AB - and the heat transfer surfaces in the condenser (2) - denoted Ac - the need for the total amount of heat transfer surfaces A = Ac is thus shown with a calculation example as follows.

With a heating power Q = 100 kW, an input (smoke) gas temperature t = 1000 ° C, an output (smoke) gas temperature tute = 45 ° C, a radiator water temperature tcin = 35 ° C and a condenser temperature of tc = 50 ° C, the following calculations are obtained for various heat effects (0-100 kW) dry-thinking (smoke) gas quantity m ^ = Q / i1 - i ^ (smoke) gas enthalpy out l2 = ((mtrg * l ·,) - QB / rx \ g temperature after boiler part t2 = f (12; λ = 1.5) mean temperature difference. Atm = ((t, - tc) - (t2 - ^)) / ^ ((^ - tc) - (t2 - tc))

the heat transfer surface in the boiler part AB = QB / ks * Atm; then ks = 0.05-0.08 kW / m2oC

j the heat transfer surface in the bottom of the condenser

·: ··: Ac = (Q - QB) / kc * Atmc; where kc = 0.6 kW / m ° C and Atmc = 10 ° C

: 25 total area A = AB + Ac * · Where i1t i2, λ, ks are per se known values.

* ·. ”The results of the calculations can be summarized in the following table: .. · * 30

Qb [kW] AB [m2] Ac [m2] A [m2] 40 0.7 10.0 10.7 Γ \: 60 1.4 6.7 8.1 70 2.2 5.0 7.2 9 109554 80 3.4 3.3 6.7 95 6.7 0.9 7.6 i 100 11.0 - 11.0

This, in turn, can be summarized in a graphical representation in which the ordinate consists of the total heat transfer surface A in relation to the desired heat effect indicated in the abscissa in the boiler part QB. The abscissa can also be made up of (smoke) gas temperature after the boiler part, i.e. t2.

10 \ I

A 8 .. X. I

6 · 5 -1-1-1 1 1-1-1 - (- 1-1— * 10 20 BO 40 50 60 70 Θ0 90 100 I-1-1-1-1-1-> 1000 815 630 4 In its embodiment described above, the outlet portion 24 comprises at least a semi-circular, upright lip 35 with opening at the bottom for intercepting and separating liquid droplets from the passing gases. Above such lips, there is advantageously a dense mesh 36 for separating 5 smaller droplets still exhibited by the gases.The separated droplets are arranged to run down the walls of the outlet part, back to the bottom portion 23 of the condenser, from where the liquid is Afterwards, the cyclone 37 can be connected to the outlet part with which liquid droplets are collected from the passing gas.

After the coolant 26 and 30 have been in contact with the gases and in this way warmed up, the coolant flows down to the bottom part of the condenser 23. In this accumulated heated liquid amount, a heat exchanger 32 is arranged to cool the cooling water here, as described above. Such a heat exchanger may advantageously be arranged to heat the circulation water for a convection heat plant but also to preheat the utility water, which is then circulated to the heat exchange means 5 and 5a of the boiler part 1. The heat exchanger can of course also be intended to cool only the nozzle or coolant.

The coolant 26 and 30 of the condensate collected in the bottom part 23 of the condenser can also be circulated directly in a convection heat plant, without the use of a special heat exchanger 32. However, this requires that the convection heat plant is made of a corrosion-resistant material.

The description above and the figures cited therein are only intended to illustrate the present invention. Thus, the invention is not limited only to the foregoing or to the claims described in the appended claims.

S

in men, without a variety of variations or alternative modes of presentation are possible:. within the idea of the invention described in the appended claims.

* * · ♦ ·

Claims (13)

A heat generating device for heating domestic water by combustion of fuel, said heat generating device comprising a burner for producing hot gases, for example combustion and flue gases, a boiler part (1) having a combustion chamber (3) and heat exchange means (5). 5a, 6) for receiving the gases and a condenser (2) connected to the boiler part for collecting heat energy from gases and purifying them, the gases being arranged to be led from the boiler part to the condenser, which comprises a substantially U-shaped structure having an upper part (21), a bottom part (23) and an outlet part (24), the upper part being arranged to receive the gases and having means (25) for bringing the gases into direct contact with a coolant (26), and which bottom part is arranged to collect the coolant, characterized in that the boiler part (1) for its construction is substantially cylindrical, so that a center axis shown by the boiler part electricity (7) is arranged in a substantially vertical direction, the heat exchange means (5, 5a, 6) provided by the boiler member comprise in the combustion chamber (3) arranged vessels for receiving and circulating the use water, the vessels having casing surfaces which are at least partially 20 direct contact with the gases. 2. Patent tivaatimuksen 1 mukainen lammönntuottolaite, tunnettu siitä, että lammönvaihdinelimissä on yksi tai useampia radiaattorivesiastioita (5, 5a) ja käyttövesiastioita (6). in 2. A heat generating device according to claim 1, characterized in that characterized in that the heat exchange means comprise one or more radiator water vessels (5, 5a) and tap water vessels (6). i * · 3. Patenttivaatimuksen 2 mukainen lammönntuottolaite, tunnettu siitä, one radiaattorivesiastia (5) on sovitettu olennaisesti käyttövesiastian (6) ympärille. 3. A heat generating device according to claim 2, characterized in that a radiator water vessel (5) is arranged to substantially surround the tap water vessel (6). ♦ »*: ... · 4. A heat generating device according to claim 3, characterized in that the combustion chamber (3) is arranged to substantially: '': surround the radiator water vessel (5) arranged to surround the tap water vessel (6). 5. A heat generating device according to any preceding claim, characterized in that the radiator water vessels (5, 5a) for their construction "comprise substantially cylinders and / or annular cylinders at least partially: ...: joined to one another while the tap water vessel (6) 6. A heat production device according to claim 5, characterized in that the combustion chamber (3), the radiator water vessels (5, 5a) and the tap water vessel (6) are concentrically arranged. 4. Patenttivaatimuksen 3 mukainen lammönntuottolaite, tunnettu siitä, one palamiskammio (3) on sovitettu olennaisesti käyttövesiastian (6) ympärille sovitetun radiaattorivesiastian (5) ympärille. 5. Jonkin nobellisen patenttivaatimuksen mukainen lämmönntuottolaite, tunnettu siitä, one rakenteeltaan radiaattorivesiastiat (5, 5a) 14 109554 i 6. Patenttivaatimuksen 5 mukainen lammönntuottolaite, tunnettu siitä, one palamiskammio (3), radiaattorivesiastiat (5, 5a) ja käyttövesiastia (6) ovat sovitettu samankeskisestä 7. Jonkin nobellisen patenttivaatimuksen mukainen lammönntuottolaite, tunnettu siitä, one polttimessa on liitäntäkanava (4), joka on liitetty palamiskammioon (3) sen poikittaissuunnassa. 7. A heat production device according to any preceding claim, characterized in that the burner has a connection channel (4) which is connected to the combustion chamber (3) in its tangential direction. 8. Jonkin nobellisen patenttivaatimuksen mukainen lammönntuottolaite, tunnettu siitä, one palamiskammio (3) on liitetty condensaattoriin (2) yhdellä tai useammalla savukanavalla (20), jotka on sovitettu johtamaan kuumut kaasut condensa. 8. A heat production device according to any preceding claim, characterized in that the combustion chamber (3) is connected to the condenser (2) with one or more smoke ducts (20) arranged to pass the hot gases to the upper part (shown by the condenser). 21). 9. Patent Tivaatimuksen 8 Mukainen Lammönntuottolaite, Tunnettu Siitä, One Condensa Attorissa (2) suunnattu olennaisesti kaasujen virtaussuuntaan. 9. A heat generating device according to claim 8, characterized in that the condenser (2) has means (25, 31) for bringing the gases into direct contact with coolant (26, 30) both in its upper part (21) and in its outlet part (24). ), wherein both means are directed substantially in the direction of flow of the gases. 10. Patenttivaatimuksen 9 mukainen lämmönntuottolaite, tunnettu siitä, one condensaattorissa (2) on keräysastia (28) condensaattorin yläosaan johdetun jäähdytysnesteen (26, 30) keräämiseksi ja puhdistamiseksia, joka in Heat production device according to claim 9, characterized in that the condenser (2) has a collecting vessel (28) for collecting and purifying coolant (26, 30) introduced into the upper part of the condenser, which collecting vessel is arranged to be removed from it by the condenser. hatch. 11. Jonkin nobellisen patenttivaatimuksen mukainen lammönntuottolaite, tunnettu siitä, että condensaattorin (2) pohjaosassa (23) on sinn sovitettu lämmönvaihdin (32). 11. A heat production device according to any one of the preceding claims, characterized in that the condenser (2) in its bottom part (23) has a heat exchanger (32) arranged therein. 11 109554 12. Jonkin nobellisen patenttivaatimuksen mukainen lämmönntuottolaite, tunnettu siitä, one condensaattorin (2) poisto-osassa (24) on sine sovitettu cyclone (37) nesting pisaroids erottamiseksi kaasuista. 12. A heat production device according to any of the previous claims, characterized in that the condenser (2) in its outlet part (24) is mounted; , shows a cyclone (37) arranged thereon for separating liquid droplets from the gases. ! 13. A heat generating device according to any of the previous claims, characterized in that the boiler part (1) and the condenser (2) are suitable. slightly connected that the top of the boiler part (11) is the bottom of the condenser. »109554 13 1 .Lemmöntuottolaite käyttöveden lämmittämiseksi polttamalla polttoainetta, joka lämmöntuottolaite käsittää polttimen kuumien kaasujen, esimerkiksi poltto- ja savukaasujen,! tuottamiseksi, pannuosan (1), jossa on palamiskammio (3) ja lammönvaihdinelimet (5, 5a, 6) kaasujen vastaanottamiseksi sekä pannuosaan liitetty condensaattori (2) n muotoinen hit, jossa on yläosa (21), pohjaosa (23) ja poisto-osa (24), joka yläosa on sovitettu vastaanottamaan kaasut ja jossa on elimet (25) kaasujen saattamiseksi suoraan kosketukseen jäähdytysnesteen (26) sovitettu keräämään jäähdytysnestettä, tunnettu siitä, että pannuosa (1) one rakenteeltaan olennaisesti lieriömäinen site, että pannuosassa oleva Keski akseli (7) on sovitettu olennaisesti kohtisuoraan, pannuosassa olevat lämmönvaihdinelimet (5, 5a, 6) käsittävät palamiskammioon (3) sovitetut astiat käyttöveden vastaanottamiseksi yes kierrettämiseksi, astioid käsittäessä vaippapinnat, jot ka ainakin osittain ovat suorassa kosketuksessa kaasujen kanssa. 13. Jonkin nobellisen patenttivaatimuksen mukainen lammönntuottolaite, tunnettu siitä, etä pannuosa (1) ja condensaattori (2) ovat yhdistetty site, että pannuosan yläpää (11) muodosta condensaattorin pohjan.