RU2737576C1 - Boiler with fire tubes - Google Patents

Abstract

FIELD: fuel combustion devices.SUBSTANCE: invention relates to boiler with smoke tubes. Boiler comprises mixing chamber located on combustion chamber and having space for mixing, in which combustion gas and air are mixed, and flat-plate burner is mixed. Unit of ignition electrodes is made with possibility of passage through one side section of mixing chamber for further assembly and passage in direction downwards from burner of flat-plate type along upper section of combustion chamber. Sealing device is configured to block leakage of the gas mixture from the mixing space and the combustion gas from the combustion chamber to the outside through the gap between the mixing chamber and the ignition electrode assembly.EFFECT: technical result is creation of boiler with fire tube, which prevents leakage of gas mixture and combustion gas through gap between mixing chamber and assembly of ignition electrodes.30 cl, 37 dwg

Description

The technical field to which the invention relates

The present invention relates to a flue tube boiler, and in particular to a flue tube boiler, having a structure that prevents the gas mixture and combustion gas from escaping, thermal damage to the ignition electrode assembly and corrosion due to stagnant condensate, and reliably block the leak condensate when connecting the unit of ignition electrodes through one side section of the mixing chamber, which includes a flat-type burner.

State of the art

As a rule, the boiler includes a heat exchanger, in which heat exchange is carried out between the combustion gas released during fuel combustion and a heat carrier for heating or hot water supply using a heated heat carrier. Such a boiler may include a heat exchanger part in which a heat exchanger is provided, a burner mounted on the heat exchanging part, and a combustion chamber provided between the burner and the heat exchanger to which combustion gas and combustion air are supplied.

1 is a view schematically illustrating the configuration of a conventional fire tube boiler.

A conventional fire tube boiler includes a fan 10 configured to supply combustion gas and air, a cylindrical burner 20 configured to burn a mixed air of combustion gas and air, a combustion chamber 30 in which the mixed air is ignited by a burner 20, a heat exchanger 40 in which heat is exchanged between the combustion gas discharged from the combustion chamber 30 and the heat carrier, an insulating material 50 configured to prevent the transfer of heat received from the combustion chamber 30 to the upper side adjacent to the cylindrical burner 20, and an electrode 60 ignition, installed using insulating material 50 and configured to ignite the mixed air.

The heat exchanger 40 may include an outer cylinder 41, a plurality of tubes 42 formed therein and through which the combustion gas discharged from the combustion chamber 30 flows, and a water tank 43 in which the heat transfer medium is placed outside the tubes 42.

According to the configuration of the conventional fire tube boiler, since the cylindrical burner 20 is elongated in the vertical direction, the overall height of the boiler increases significantly, so the boiler cannot be made compact. Accordingly, there is a problem that the installation space is limited.

In addition, in the conventional fire tube boiler, when the ignition electrode 60 is installed through the combustion chamber cover 12 installed between the fan 10 and the cylindrical burner 20, an insulating material 50 is used to prevent heat transfer to the ignition electrode 60.

However, the insulating material 50 cracks due to heating during combustion or breaks up into fine granular particles, causing a problem such as clogging of the tubes 42, which are the paths for the combustion gas of the heat exchanger 40, and when the cover 12 of the combustion chamber and the mixing chamber 11, including cylindrical burner 20, disassembled for maintenance, damage to the insulating material 50 is inevitable.

Meanwhile, when the ignition electrode 60 is installed in the heat exchanger 40, the manufacturing process increases due to the addition of unnecessary processes and components, and there is a risk of leakage of the heating medium.

As described above, the prior art, which relates to the structure of an ignition electrode assembly on a combustion chamber cover, is disclosed in Registered Patent No. 10-0575187 and Registered Patent No. 10-0581580.

In addition, in the case where a flat-type burner having better combustion performance than a cylindrical burner 20 is used, a heat exchanger is connected to one side of the mixing chamber to which a flat-type burner is connected, and a combustion chamber is formed between the mixing chamber and the heat exchanger. In this case, when the ignition electrode assembly is connected to the mixing chamber by passing through one side portion, unburned gas mixture may leak out through the gap between the mixing chamber and the ignition electrode assembly. When such unburned gas mixture (natural gas) seeps out, a problem arises that leads to a deadly threat to the human body.

When a sealing means is installed, configured to prevent leakage of the above-described gas mixture, since the high-temperature heat from the combustion chamber is transferred to the sealing means, and thus the sealing means can easily deteriorate due to wear, a problem arises that the sealing means are difficult to install. preventing failure due to wear.

Meanwhile, in the fire tube heat exchanger disclosed in EP 2508834 and EP 2437022, an outer cylinder that serves as a water tank in which a heat transfer medium is placed is formed outside the tube. An upper tube sheet forming the upper surface of the water tank and supporting the upper end portion of the outer cylinder is attached to the upper end of the tube, and the lower tube sheet forming the lower surface of the water tank and supporting the lower end of the outer cylinder is attached to the lower end of the tube ...

In the case of the fire tube heat exchanger described above, since the heat transfer medium disposed in the water tank applies high hydraulic pressure to the lower tubesheet, it is necessary for the lower tubesheet to withstand high hydraulic pressure to maintain service life.

However, the bottom tube sheet provided in the conventional fire tube heat exchanger is not configured sufficiently to distribute the hydraulic pressure, and thus has a short service life.

In addition, the conventional smoke tube boiler is designed as a structure provided with a condensate trap under the bottom tube sheet and a sealing member configured to prevent condensate from leaking between the edge section of the bottom tube sheet and the edge section of the condensate trap, and a sealing member configured to support the bottom end a section of the side surface of the lower tube sheet.

However, according to the sealing design of the sealing member between the bottom tube sheet and the condensate trap, the condensate generated in the fire tube heat exchanger stagnates between the lower end portion of the side surface portion of the bottom tube sheet and the sealing member, causing corrosion of the bottom tube sheet, and when the sealing member is conventional therefore, condensate leakage cannot be reliably blocked. The prior art to which the sealing structure of a conventional condensate trap belongs is disclosed in Korean Patent Laid-Open No. 10-2005-0036152 and the like.

The essence of the invention

Technical challenge

The present invention is directed to providing a fire tube boiler capable of preventing the gas mixture and combustion gas from leaking through the gap between the mixing chamber and the ignition electrode assembly.

In addition, the present invention is directed to providing a fire tube boiler including cooling means capable of significantly reducing the size of the insulating material to prevent blockage of the flow due to damage to the insulating material and configured to block heat transfer to the ignition electrode assembly or the sealing means. ignition electrodes near the ignition electrode assembly when installing the ignition electrode assembly through the mixing chamber.

In addition, the present invention is directed to providing a fire tube boiler having a structure capable of increasing the pressure resistance of the bottom tubesheet water, preventing corrosion due to condensate stagnation in the bottom tubesheet and reliably blocking condensate leakage.

In addition, the present invention is directed to providing a fire tube boiler having a reduced height and capable of improving heat exchange efficiency over a conventional boiler.

Technical solution

One aspect of the present invention provides a fire tube boiler, including: a mixing chamber having a mixing space in which combustion gas and air are mixed and a flat-type burner disposed on the combustion chamber; an ignition electrode assembly configured to pass through one side portion of the mixing chamber to be assembled and extend downwardly from the flat-type burner along the upper portion of the combustion chamber; and sealing means configured to block leakage of the gas mixture from the mixing space and the combustion gas from the combustion chamber to the outside through the gap between the mixing chamber and the ignition electrode assembly.

A mixing chamber flange and a burner flange may be provided on one side portion of the mixing chamber to be connected to each other to seal the mixing space, and the ignition electrode assembly may pass through the mixing chamber flange and the burner flange at a location spaced from the mixing chamber. mixing, for further assembly.

The sealing means may include a first sealing member provided at a portion in which the mixing chamber flange and the burner flange are connected to each other to prevent leakage of the gas mixture.

An insulating material adapted to block the transmission of the heat of combustion coming from the combustion chamber may be provided on the first sealing element. The size of the insulating material can be significantly reduced in contrast to the prior art.

A connecting plate through which the ignition electrode assembly passes for connection thereto may be provided in one side portion of the mixing chamber, and the sealing means may include a second sealing member provided between the upper portion of one side portion of the mixing chamber and the connecting plate to prevent leakage combustion gas.

A plurality of outwardly protruding contact protrusions may be provided at predetermined intervals on the outer side surface of the second sealing member.

The ignition electrode assembly may include an ignition electrode and a flame sensor, an ignition electrode connection plate through which the ignition electrode passes for connection, a flame sensor connection plate through which the flame sensor passes for connection to it, may be provided on one side a portion of the mixing chamber, and a sealing means may be provided between the upper portion of one side portion of the mixing chamber and the connecting plate of the ignition electrodes and between the upper portion of one side of the mixing chamber and the connecting plate for the flame sensor.

The fire tube boiler may further include cooling means configured to block the transfer of combustion heat from the combustion chamber (C) to the sealing means.

The cooling means may include air-type cooling means and water-type cooling means.

A mixing chamber flange and a burner flange can be provided on one side of the mixing chamber to be connected to each other to seal the mixing space, the ignition electrode assembly can pass through the mixing chamber flange and burner flange for further assembly, and the mixing chamber flange and burner flange can be cooled with a gas mixture introduced into the mixing space in an air-type cooling means.

The mixing chamber flange and the burner flange can be formed on the same side section of the mixing chamber for connection to each other in order to seal the mixing space, the ignition electrode assembly can pass through the mixing chamber flange and the burner flange for further assembly, and the top flange of the tube sheet made with the possibility of contacting the heat transfer medium of the heat exchanger provided under the combustion chamber, may be provided in order to come into contact with the burner flange for cooling the burner flange in the water-type cooling means.

A plurality of cooling fins may be provided on one side portion of the mixing chamber where the ignition electrode assembly is assembled along the edge of the ignition electrode assembly.

The smoke tube boiler may include an outer cylinder provided at the edge of the tube through which the combustion gas flows inside it to form an outer wall of a water tank in which the heat transfer medium is placed outside the tube, and a bottom tube sheet having a tube sheet structure and formed from a horizontal section configured to support the lower end section of the tube and form the bottom surface of the water tank, a vertical section connected to the outer side surface of the lower end section of the outer cylinder, and a circular section configured to connect the outer end of the horizontal section and the lower end section a vertical section and having a convex outward curved shape for distributing the hydraulic pressure of the heat carrier.

The vertical portion of the lower tube sheet may be attached to abut the outer side surface of the lower end portion of the outer cylinder.

A flange portion configured to extend outwardly for a predetermined length can be formed on a vertical portion of the bottom tube sheet, and the flange portion and the outer side surface of the outer cylinder can be welded together.

The smoke tube boiler may include a condensate trap provided under the bottom tubesheet to collect condensate formed on the bottom tubesheet, and a leakage prevention member provided between the edge portion of the bottom tubesheet and the edge portion of the condensate trap to prevent condensate from leaking out.

The leakage prevention member can be provided in a shape that encloses the lower portion of each circular portion and the vertical portion of the lower tubesheet, and the condensate formed in the horizontal portion of the lower tubesheet can be blocked from moving laterally when the leakage prevention member is locked, and can be drained downward.

It is envisaged that the side wall of the condensate trap can be located near the boundary between the horizontal section and the circular section of the bottom tube sheet to guide the condensate drops.

A contact protrusion configured to protrude towards the outer side surface of the bottom tube sheet may be formed on the inner side surface of the leak prevention member.

The plurality of contact protrusions may be formed at locations vertically spaced from the inner side surface of the leak prevention member.

A first flange portion configured to extend outwardly from the upper end of the side wall of the condensate trap to support the lower portion of the leakage prevention member may be provided on the edge portion of the condensate trap, and the attachment protrusion and the attachment groove attached to each other at respective locations may be are provided on the leakage prevention member and the first flange portion.

The fire tube boiler may further include an elongated portion configured to extend upwardly from the outer end of the first flange portion and come into intimate contact with the outer side surface of the leak prevention member, and a second flange portion configured to extend outwardly from the end of the elongated portion at the edge portion of the condensate trap, where a locating protrusion and a locating groove, which are inserted into each other at their respective locations, can be formed on the upper portion of the leakage prevention member and the second flange portion in order to block condensate leakage and fix the location of the leakage prevention member ...

The condensate trap can be provided with an outlet guide having a plurality of perforations formed therein so that the combustion gas that passes through the heat exchanger is evenly distributed over the entire area of the condensate trap from which the condensate is to be drained.

A stepped portion configured to direct the combustion gas flow that passes through the outlet guide to the condensate drain hole can be formed on the bottom surface of the condensate trap so that the direction of the condensate drain and the direction of the combustion gas flow can be the same in the condensate trap.

The mixing chamber may include a flat-shaped mixing chamber body and a flat-type burner disposed horizontally on the combustion chamber.

The separation space between the lower surface of the mixing chamber body and the upper surface of the flat-type burner may be formed as a flat disc.

The smoke tube boiler may further include a heat exchanger in which heat is exchanged between the combustion heat of the combustion chamber and the heat transfer medium, the heat exchanger may include an outer cylinder through which the heat transfer medium is introduced and removed and which forms the outer wall of the water tank in which a coolant is placed, an upper tube sheet having a tube sheet structure attached to the inner side of the outer cylinder and forming a combustion chamber in such a way that a path is formed for the coolant between the upper tube sheet and the outer cylinder, a plurality of tubes, each of which has a flat shape in order to so that the combustion gas discharged from the combustion chamber carries out heat exchange with a coolant that flows from the outside, while flowing around the inner sides of the tubes, a turbulator connected to the inner sides of the tubes to create turbulence in the combustion gas flow, a multilayer diaphragm, viewed between the outer cylinder and the tube for directing the coolant so that the flow direction of the coolant alternately changes inward and outward in the radial direction, and a lower tube sheet having a tube sheet structure configured to support the lower end sections of the tubes and form the lower surface of the water tank ...

The upper tube sheet flange may be configured to protrude outward from the upper end of the circular section, and the ratio of the difference in diameters between the outer diameter of the upper tube sheet flange and the inner diameter of the lower end of the circular section may be less than or equal to 20%.

The height between the bottom surface of the flat-type burner inserted into the top tube sheet and the bottom surface of the top tube sheet can be adjusted so that the tip of the flame emerging from the flat-type burner can be located at a predetermined distance from the bottom surface of the top tube sheet, preferably , at a height of approximately 80 mm.

The turbulator may include an upper turbulator attached to the inner side of the upper portion of the tube adjacent to the combustion chamber to provide surface contact with the tube to increase thermal conductivity and create turbulence in the combustion gas stream, and a lower turbulator attached to the inner side of the tube in the direction down from the upper turbulator to create turbulence in the combustion gas stream.

Beneficial effects

In the fire tube boiler of the present invention, by installing the ignition electrode assembly through one side portion of the mixing chamber to use a flat-type burner, which is simple to manufacture and has a higher output than a cylindrical burner, the gas mixture and combustion gas can be prevented from escaping.

In addition, when using a flat-type burner having a combustion zone formed to be larger than that of a cylindrical burner, a cooled structure for an ignition electrode assembly connected through one side portion of the mixing chamber is preferable by gas and air. into the combustion zone, and the service life can be increased by preventing damage due to wear.

In addition, since the bottom tube sheet configured to encompass the outer side surface of the outer cylinder and the convex, curved, rounded section is formed at a corner configured to connect the horizontal section and the vertical section of the bottom tube sheet in order to distribute hydraulic coolant pressure, it is possible to increase the service life by increasing the resistance to water pressure of the bottom tube sheet, while minimizing deformation.

In addition, since the bottom tube sheet of the fire tube heat exchanger is configured to enclose the outer side surface of the outer cylinder, the leakage prevention member is configured to enclose the bottom section of the vertical section of the bottom tube sheet and the circular section, and the side wall of the condensate trap is located so as to be close to the boundary between the horizontal section and the circular section of the bottom tube sheet so as to guide the discharge of condensate, corrosion due to stagnant condensate can be prevented.

In addition, since contact protrusions configured to protrude towards the outer side surface of the bottom tube sheet are formed on the inner side surface of the leakage prevention member, the contact protrusion of the leakage prevention member configured to protrude in a direction opposite to the direction in which hydraulic pressure, comes into contact with the outer side surface of the bottom tube sheet to prevent condensate from leaking when hydraulic pressure is applied. In addition, when a plurality of contact protrusions are formed at locations vertically spaced from each other, leakage of condensate can be prevented more reliably.

In addition to this, since a flat mixing chamber body and a flat-type burner are provided, the upper tube sheet made in the tube sheet structure is reduced to the minimum height at which the mixed air is completely burned and the heat exchange efficiency of the heat exchanger is increased, the boiler height can be reduced by compared with a traditional boiler, it is therefore possible to design a tube boiler with high efficiency and compact size.

Brief Description of Drawings

Fig. 1 is a view schematically illustrating the configuration of a conventional fire tube boiler.

Fig. 2 is a perspective view of the outside of a tube boiler according to an embodiment of the present invention.

FIG. 3 is a perspective view of the bottom surface of the mixing chamber shown in FIG. 2. FIG.

4 is an exploded perspective view illustrating the structure in which the ignition electrode assembly is connected to the mixing chamber.

5 is an enlarged perspective view of the connecting portion of the ignition electrode assembly.

Fig. 6 is a front view of Fig. 2.

FIG. 7 is a partial cross-sectional perspective view taken along line A-A in FIG. 6. FIG.

FIG. 8 is an enlarged, partial cross-sectional view taken along line A-A in FIG. 6.

9 is a partial perspective view of a portion of a boiler having a fire tube heat exchanger according to an embodiment of the present invention.

10 is an exploded perspective view of a main portion of a boiler having a fire tube heat exchanger according to an embodiment of the present invention.

Fig. 11A is a top view of the leakage prevention member, and Fig. 11B is an enlarged cross-sectional view taken along line B-B of Fig. 11A.

FIG. 12 is a cross-sectional view of part A of FIG. 1.

13 is a perspective view of the outside of a tube boiler according to another embodiment of the present invention.

14 is a perspective view of a mixing chamber.

15 is a perspective view of the bottom surface of the mixing chamber.

Fig. 16 is an exploded perspective view illustrating a structure in which an ignition electrode and a flame sensor are connected to the mixing chamber.

Fig. 17 is a top view of the mixing chamber and heat exchanger.

FIG. 18 is a partially cross-sectional perspective view along line C-C in FIG. 17.

FIG. 19 is a partial cross-sectional view taken along line C-C in FIG. 17.

Fig. 20 is a cross-sectional view illustrating the joint structure between the top tube sheet and the burner.

Fig. 21 is a perspective view of a heat exchanger.

Fig. 22 is an exploded perspective view of a heat exchanger.

Fig. 23 is a front view in a state where the tube assembly and the multilayer diaphragm are connected to each other.

Fig. 24A is a top view of Fig. 23, Fig. 24B is a cross-sectional view taken along line D-D of Fig. 23, and Fig. 24C is a cross-sectional view taken along line E-E of Fig. 23.

Fig. 25 is a top view of the heat exchanger.

FIG. 26 is a partially cross-sectional perspective view taken along line F-F in FIG. 25.

Fig. 27 is a perspective view illustrating an embodiment of a tube assembly.

Fig. 28 is an exploded perspective view of the tubing assembly.

Fig. 29 is a front view of the upper turbulator and the lower turbulator.

FIG. 30 is an enlarged perspective view of the upper turbulator shown in FIG. 29.

Fig. 31 is a top plan view of the upper turbulator shown in Fig. 30.

Fig. 32A is a cross-sectional view taken along line G-G of Fig. 31, and Fig. 32B is a partially cross-sectional perspective view taken along line G-G in Fig. 31.

FIG. 33 is a left side view of the upper turbulator shown in FIG. 30.

Fig. 34 is a perspective view of a tube boiler according to another embodiment of the present invention.

Fig. 35 is an exploded perspective view of a tube boiler according to another embodiment of the present invention.

Fig. 36A is a top view of the leakage preventing member, and Fig. 36B is a cross-sectional view taken along line H-H of Fig. 36A and an enlarged view.

Fig. 37 is a cross-sectional view illustrating a sealing structure and a condensate drain structure of a fire tube boiler according to another embodiment of the present invention.

Reference positions

10 - fan

11 - mixing chamber

12 - combustion chamber cover

20 - cylindrical burner

30 - combustion chamber

40 - heat exchanger

41 - outer cylinder

42 - tube

43 - water tank

50 - insulating material

60 - ignition electrode

1, 1 '- boilers with smoke tubes

100 - mixing chamber

110 - branch pipe for mixed air supply

120 - mixing chamber flange

130 - flat-type burner

131 - plate with a hole for the flame

131a - flame hole

132 - metal fiber

133 - burner flange

140 - unit of ignition electrodes

141 - the first ignition electrode

142 - second ignition electrode

143 - flame sensor

141a, 142a, 143a - insulators

141b, 142b, 143b - bushings

144 - connecting plate

144a, 144b, 144c - connection holes

150 - connecting part of the ignition electrode assembly

151 - landing part of the connecting plate

152 - seating part of the second sealing element

153 - through hole

154 - cooling rib

160 - the first sealing element

170 - insulating material

180 - second sealing element

181 - contact ledge

190 - sealing element

200 - heat exchanger

210 - outer cylinder

220 - top tube sheet

221 - hole for tube insertion

222 - tube sheet top flange

230 - tube

240 - water tank

300 - condensate trap

400 - element of the exhaust duct

500 - leakage prevention element

510 - building

510a - Inner side surface of leak prevention element

520, 521, 522, 523, 524 - contact tabs

530 - Bottom section of leak prevention element

531 - mounting groove

540 - Top of Leak Prevention Element

541 - locating protrusion

1000 - mixing chamber

1100 - mixing chamber housing

1110 - mixing chamber flange

1200 - branch pipe for mixed air supply

1300 - flat-type burner

1310 - plate with a hole for the flame

1330 - burner flange

1400 - unit of ignition electrodes

1410 - ignition electrode

1420 - flame sensor

1500 - connecting part of the ignition electrode assembly

1600 - first sealing element

1700 - second sealing element

1800 - third sealing element

1900 - sealing element

2000 - heat exchanger

2100 - outer cylinder

2110 - hole for inlet of the coolant

2120 - hole for the outlet of the coolant

2200 - top tube sheet

2240 - round section

2300 - tube

10000 - tube assembly

2400 - upper turbulator

2500 - lower turbulator

2610 - upper diaphragm

2620 - medium aperture

2630 - lower diaphragm

2640 - Support Tool

2700 - lower tubesheet

3000 - condensate trap

3100 - condensate drain hole

3200 - leakage prevention element

3300 - outlet guide

3310 - perforation hole

4000 - exhaust air duct

5000 - premix chamber

6000 - mixed air control unit

7000 - fan.

Detailed description of the invention

Next, the configuration and operation of an embodiment of the present invention will be described in detail with reference to the accompanying drawings.

As shown in FIGS. 2-8, a fire tube boiler 1 according to an embodiment of the present invention includes a mixing chamber 100 having a mixing space S in which combustion gas and air supplied through the mixed air supply pipe 110 are mixed. to the fan, and a flat-flame burner 130, configured to burn mixed air and located in the combustion chamber C, a heat exchanger 200 in which heat exchange between the coolant and the combustion gas is carried out, a condensate collector 300 configured to collect condensate formed during the condensation of steam, which passes through the heat exchanger 200 and is included in the combustion gas, and an exhaust duct 400 connected to one side of the condensate collector 300 so that combustion gas is discharged, which passes through the heat exchanger 200.

In addition, the smoke tube boiler 1 includes an ignition electrode assembly 140 configured to pass through one side portion of the mixing chamber 100 for further assembly and extend along the top portion of the combustion chamber C to the bottom side of the flat-type burner 130, and a sealing means, configured to block leakage of the gas mixture from the mixing space S and the combustion gas from the combustion chamber C to the outside through the gap between the mixing chamber 100 and the ignition electrode assembly 140.

The burner used in the present invention is a flat-type burner 130, and includes a flame hole plate 131 having a flat shape and in which a plurality of flame holes 131a are formed, and a metal fiber 132 attached to the flame hole plate 131 ... The flat flame burner 130 covers the entire area of the mixing space S and is thus preferred for an air-cooled design with gas and air introduced into it, and since the combustion zone expands in order to reduce the load per unit area, it is possible to reduce emission of pollutants such as CO, NOx, etc., and improve combustion performance.

The ignition electrode assembly 140 passes through one side portion of the mixing chamber 100 for further assembly. The ignition electrode assembly 140 may include a first ignition electrode 141, a second ignition electrode 142, and a flame sensor 143. Insulators 141a, 142a, and 143a are made of insulating material, connected to the outer side surfaces of the first ignition electrode 141, the second ignition electrode 142 and the flame sensor 143, respectively, and bushings 141b, 142b and 143b are connected to the outer side surfaces of the insulators 141a, 142a and 143a , respectively, to maintain tightness.

The first ignition electrode 141, the second ignition electrode 142, the flame sensor 143, the insulators 141a, 142a and 143a and the bushings 141b, 142b and 143b connected to the outer side surfaces of the first ignition electrode 141, the second ignition electrode 142 and the flame sensor 143 are connected to each the other by passing through the connection holes 144a, 144b and 144c formed in the connection plate 144.

Insulators 141a, 142a, and 143a are isolation means designed to prevent sparking due to excitation during ignition, and bushings 141b, 142b, and 143b are configured to seal gaps between the outer side surfaces of insulators 141a, 142a and 143a and the connection holes 144a, 144b and 144c.

As shown in FIGS. 4 and 5, a connecting portion 150 of the ignition electrode assembly configured to assemble the ignition electrode assembly 140 is provided on one side portion of the mixing chamber 100. The connecting portion 150 of the ignition electrode assembly includes a connecting plate seat 151 formed in the form of a groove so that the connecting plate 144 is inserted therein, the seating portion 152 of the second sealing member facing inwardly relative to the seating portion 151 of the connecting plate so that the second sealing member 180 is inserted therein, and a through hole 153 through which the first an ignition electrode 141, a second ignition electrode 142 and a flame sensor 143. In addition, a plurality of cooling fins 154 configured to emit combustion heat are provided around the connecting portion 150 of the ignition electrode assembly.

As shown in FIGS. 6-8, a mixing chamber flange 120 and a burner flange 133 coupled to an edge portion of a flat-type burner 130 to support an edge portion of a flat-type burner 130 are provided on one side portion of the mixing chamber 100 to be connected to each other to sealing the mixing space S, and the ignition electrode assembly 140 passes through the mixing chamber flange 120 and the burner flange 133 for further assembly at a location spaced from the mixing space S.

The sealing means may include a first sealing member 160 provided at an area where the mixing chamber flange 120 and the burner flange 133 are in contact with each other to prevent the gas mixture introduced into the mixing space S from escaping to the outside, and the first sealing member 160 can be made of heat-resistant graphite material. In addition, an insulating material 170 configured to block transmission of the combustion heat from the combustion chamber C is provided on the first sealing member 160.

In addition, the sealing means may include a second sealing member 180 provided between the upper portion of one side portion of the mixing chamber 100 and the connecting plate 144 to prevent the combustion gas discharged from the combustion chamber C to the outside, and the second sealing member 180 may be made of rubber material. In addition, a plurality of contact protrusions 181, configured to protrude outwardly, may be provided at predetermined intervals on the outer side surface of the second sealing member 180 and may come into tight contact with the bottom surface of the connecting plate 144 and the top surface of the seating portion 152 a second sealing element to further improve the tightness.

In addition, as described above, in the ignition electrode assembly 140, since the bushings 141b, 142b and 143b are connected to the outer side surfaces of the insulators 141a, 142a and 143a, respectively, it is possible to block the combustion gas or gas mixture from escaping through the connecting holes 144a again. , 144b and 144c of the connecting plate 144.

Next, with reference to FIGS. 7 and 8, the configuration and operation of the cooling means configured to block the transfer of combustion heat to the seal means and the emission of combustion heat will be described.

The cooling means is configured to block the transfer of the heat of combustion coming from the combustion chamber C to the sealing means configured to prevent the heat of combustion from escaping through the gap between the mixing chamber 100 and the ignition electrode assembly 140, and may include air-type cooling means and cooling water type.

As described above, the mixing chamber flange 120 and the burner flange 133 may be provided on one side portion of the mixing chamber 100 for connecting to each other to seal the mixing space S, the ignition electrode assembly 140 extends through the mixing chamber flange 120 and the burner flange 133 to further assembly, and the air-type cooling means can be configured such that the mixing chamber flange 120 and the burner flange 133 are convectively cooled by the gas mixture introduced into the mixing space S.

Meanwhile, heat exchanger 200 may include a fire tube heat exchanger and may include an outer cylinder 210, an upper tube sheet 220 defining a lower surface of the combustion chamber C and an upper surface of heat exchanger 200, a plurality of tubes 230 having upper end portions passing through a tube insertion hole 221 made on the upper tube sheet 220 for further connection and through which the combustion gas flows through their interior and a water tank 240 located on the outer sides of the tubes 230 and in which the heat transfer medium is placed in the outer cylinder 210. The heating medium can be heating water used for heating or warm water used for hot water supply.

In a water-type cooling means, since the top flange 222 of the tube sheet, configured to contact the heat transfer medium of the heat exchanger 200 provided below the combustion chamber C, is configured to contact the burner flange 133, the burner flange 133 and the sealing member 190 can be cooled by thermal conduction ...

In addition, as described above, a plurality of cooling fins 154 are provided in one side portion of the mixing chamber 100 where the ignition electrode assembly 140 is assembled along the edge of the ignition electrode assembly 140, and they also serve as cooling means.

As described above, according to the present invention, since the sealing means and the cooling means are provided when the ignition electrode assembly 140 passes through one side portion of the mixing chamber 100 having a flat burner 130 for further assembly, it is possible to block the gas mixture and combustion gas from escaping. , and heat loss of the sealing means due to the heat of combustion can be prevented. In addition, since the problem of blocking the tube due to the insulating material installed on one side of the lower end zone of the conventional mixing chamber can be avoided, and due to the fact that the insulating material 170 is used only in a portion of the lower end of the ignition electrode assembly 140, it can be reduced to By minimizing the use of insulating material, the ignition electrode assembly 140 can be reliably assembled, and the gas mixture and combustion gas can be prevented from escaping due to damage to the sealing means.

As shown in FIGS. 9 to 12, the fire tube boiler 1 according to an embodiment of the present invention further includes a leakage prevention member 500 connected to a connecting portion between the above-described heat exchanger 200 and the condensate trap 300 to prevent condensate from leaking out.

As shown in FIG. 9, the heat exchanger 200 includes an outer cylinder 210 through which a heating medium is introduced and discharged, and which forms the outer wall of a water tank (S in FIG. 12) in which the heating medium is accommodated, a plurality of pipes 220 configured to the flow of the combustion gas generated during the ignition of the burner in the mixing chamber 100 along their inner part and heat exchange with the coolant, the upper tube sheet 230, configured to support the upper end portions of the tubes 220 and form the upper surface of the water tank S, the lower tube sheet 240, configured to support the lower end portions of the tubes 220 and form the bottom surface of the water tank S, and a support plate 250 attached to locations vertically located at a certain distance from the outer side surfaces of the tubes 220 to fix the locations of the tube 220 and having a path for moving the coolant executed in it.

As shown in FIG. 10, the bottom tube sheet 240 is formed in a shape in which the top portion is open for attachment while enclosing the lower outer side surface of the outer cylinder 210, and includes a horizontal portion 241 having a plurality of tube insertion holes 241a formed thereon through which the lower end portions of the tubes 220 extend to support the lower end portions of the tubes 220 and form the lower surface of the water tank S, a vertical portion 242 connected to the outer side surface of the lower end portion of the outer cylinder 210, and a circular portion 243, configured to connect the outer end of the horizontal portion 241 and the lower end portion of the vertical portion 242, and formed in a convex outwardly curved shape for distributing the hydraulic pressure of the heat transfer medium disposed in the water tank S.

As shown in FIG. 12, a vertical portion 242 of the bottom tube sheet 240 may be attached to abut the outer side surface of the lower end portion of the outer cylinder 210, a flange portion 244 configured to extend outwardly for a predetermined length is provided at the upper end the vertical portion 242 of the bottom tube sheet 240, and the flange portion 244 and the outer side surface of the outer cylinder 210 can be welded together.

In the heat exchanger 200, since the bottom tube sheet 240 is connected to the outer cylinder 210 to encompass the bottom outer side surface of the outer cylinder 210, and a circular portion 243 having a convex curved shape outwardly is formed at the corner of the bottom tube sheet 240 which connects the horizontal section 241 and the vertical section 242, the hydraulic pressure of the heating medium can be distributed, and thus the service life can be increased by increasing the water pressure resistance of the bottom tube sheet 240 while minimizing deformation of the bottom tube sheet 240.

A connecting structure provided between the above-described heat exchanger 200, the condensate trap 300, and the leakage preventing member 500 will be described below.

As shown in FIGS. 11 and 12, the leakage preventing member 500 is provided between the edge portion of the bottom tube sheet 240 and the edge portion of the condensate trap 300 to prevent condensate from leaking out. Since the body 510 of the leakage prevention member 500 is shaped to enclose the bottom portion of each circular portion 243 and the vertical portion 242 of the bottom tube sheet 240, condensate CW generated in the horizontal section 241 of the bottom tube sheet 240 can be blocked from moving laterally. direction by blocking the lower portion 530 of the body 510 and can drain downward.

The side wall 310 of the condensate trap 300 may be configured to be located close to the boundary between the horizontal portion 241 and the circular portion 243 of the bottom tube sheet 240 to guide the discharge of condensate.

As described above, since the inner end of the lower portion 530 of the leak preventing member 500 and the side wall 310 of the condensate trap 300 are located near the boundary between the horizontal portion 241 and the circular portion 243 of the bottom tube sheet 240, condensate CW generated on the bottom surface of the horizontal section 241 of the bottom tube sheet 240 can collect in the condensate trap 300 by flowing downwardly through the inner end of the lower portion 530 of the leak prevention member 500 and the side wall 310 of the condensate trap 300 even when it moves laterally, and accordingly, stagnation of CW condensate and corrosion of the bottom tube sheet 240 can be prevented. in accordance with the above.

Meanwhile, a contact protrusion 520 configured to protrude towards the outer side surface of the bottom tube sheet 240 may be formed on the inner side surface 510a of the leak preventing member 500. The plurality of contact protrusions 521, 522, 523, and 524 may be formed at locations vertically spaced from the inner side surface 510a of the leak prevention member 500.

According to the configurations of the above-described contact protrusions 520, the contact protrusions 520 of the leakage preventing member 500, configured to protrude in a direction opposite to the direction in which the hydraulic pressure acts, can come into contact with the outer side surface of the bottom tube sheet 240 to prevent the phenomenon when in which CW condensate seeps between the bottom tube sheet 240 and the leakage prevention member 500 with the possibility of leakage. In addition, when a plurality of contact protrusions 520 are formed at locations vertically spaced from each other, leakage of condensate CW can be prevented in a more reliable manner.

Meanwhile, since the first flange portion 320 configured to extend outwardly from the upper end of the side wall 310 of the condensate trap 300 to support the lower portion, 530 of the leakage prevention member 500 is formed on the edge portion of the condensate trap 300, and the attachment protrusion 321 and the attachment groove 531 attached to each other at respective locations are provided in the lower portion 530 of the leakage preventing member 500 and the first flange portion 320, it is possible to block the leakage of condensate CW, and the location of the leak preventing member 500 can be fixed.

In addition, since the edge portion of the condensate trap 300 includes an elongated portion 330 configured to extend upwardly from the outer end of the first flange portion 320 and come into close contact with the outer side surface of the leak prevention member 500, and the second flange portion 340, configured to extend outwardly from the end of the elongated portion 330, and the locating protrusion 541 and the locating groove 341 are mated to each other at respective locations, formed on the upper portion 540 of the leak preventing member 500 and the second flange portion 340, it is possible to block the leakage of condensate CW and the location of the leakage preventing member 500 can be fixed.

In the fire tube boiler 1 according to the embodiment of the present invention, as described above, the hydraulic pressure resistance and service life can be increased by the connection structure between the bottom tube sheet 240 and the outer cylinder 210 and by the bottom tube sheet structure 240 including a circular portion 243, stagnation of CW condensate can be prevented by the relative location of the leakage preventing member 500 disposed between the edge portion of the bottom tube sheet 240 and the edge portion of the condensate trap 300, and the condensate CW can be effectively prevented from leakage by the configuration of the shoulder 520 provided on the member 500 prevent leakage.

Below, with reference to FIGS. 13 to 37, the configuration and operation of the fire tube boiler 1 'according to another embodiment of the present invention will be described.

A smoke tube boiler 1 'according to another embodiment of the present invention includes: a mixing chamber 1000 having a mixing space S in which combustion gas and air are mixed, a mixing chamber housing 1100 formed in a flat shape, and a flat-type burner 1300, located on the combustion chamber C in a horizontal direction; heat exchanger 2000, where heat exchanger 2000 includes an outer cylinder 2100 through which a heating medium is introduced and removed and which forms the outer wall of a water tank B in which the heating medium is placed, an upper tube sheet 2200 having a tube sheet structure attached to the inside of the outer cylinder 2100 and forming a combustion chamber C so that a path for a heating medium is formed between the upper tube sheet 2200 and the outer cylinder 2100, a plurality of tubes 2300, each of which is formed in a flat shape, so that the combustion gas discharged from the combustion chamber C performs heat exchange with a coolant that flows from the outside, while flowing around the inner sides of the tubes 2300, turbulators 2400 and 2500, attached to the inner sides of the tubes 2300 to create turbulence in the combustion gas flow, multilayer diaphragms 2610, 2620 and 2630 provided between the outer cylinder 2100 and the tubes 2300 for the direction of heat transfer so that the direction of flow of the coolant alternately changes inward and outward in the radial direction, and a lower tube sheet 2700 having a tube sheet structure configured to support the lower end portions of the tubes 2300 and form the lower surface of the water tank B; and a condensate trap 3000 configured to collect condensate CW formed on the bottom tube sheet 2700 for directing the condensate CW into a condensate drain hole 3100 formed on one side thereof and directing the combustion gas that passes through pipes 2300 into the exhaust duct 4000 connected to the top side of the condensate drain hole 3100 and provided on one side of the outer cylinder 2100.

In addition, the present invention further includes a premixing chamber 5000 in which combustion gas and air supplied to the mixing chamber 1000 are premixed, and a mixed air control unit 6000 configured to open and close a path for the flow of air and gas, which passes through the premix chamber 5000 to regulate the flow rate of the supplied mixed air.

As shown in FIGS. 13-19, the mixing chamber 1000 includes a mixing chamber body 1100 that is convex in an upward direction and has a flat shape, an ignition electrode assembly 1400 configured to pass through one side portion of the mixing chamber body 1100 to further assembly and continue downwardly from the flat-type burner 1300 along the upper portion of the combustion chamber C, and sealing means 1600, 1700 and 1800 configured to block the gas mixture from the mixing space S and combustion gas from the combustion chamber C to the outside through the gap between mixing chamber 1000 and node 1400 ignition electrodes.

The burner used in the present invention is a flat-type burner 1300 and includes a plate 1310 with flame holes, the plate has a flat shape in which a plurality of flame holes 1310a are formed, and a metal fiber 1320 is attached to the plate 1310 with holes for flame. The mixing space S between the lower surface of the mixing chamber body 1100 and the upper surface of the flat-type burner 1300 can be configured as a flat disc to form the mixing chamber 1000 with a low height.

In addition, unlike the conventional cylindrical burner, since the flat-type burner 1300 is formed in the entire region of the mixing space S, and thus the gas and air that is introduced into it are supplied to its edge portion, that is, to the places adjacent to the locations where the sealing means 1600, 1700 and 1800 are provided, the sealing means 1600, 1700 and 1800 can be cooled by air cooling with gas or air, and as the combustion zone is expanded to reduce the load per unit area, the emission of pollutants can be reduced substances such as CO, NOx, etc., thereby improving the combustion performance.

An ignition electrode assembly 1400 configured to pass through one side portion of the mixing chamber 1000 for further assembly may include an ignition electrode 1410 and a flame sensor 1420, and an ignition electrode 1410 may include a first ignition electrode 1410-1 and a second electrode 1410 -2 ignition. Insulators 1410a and 1420a are made of insulating material, are attached to the outer side surfaces of the ignition electrode 1410 and the flame sensor 1420, respectively, and bushings 1410b and 1420b are attached to the outer side surfaces of the insulators 1410a and 1420a, respectively, to maintain tightness.

Ignition electrode 1410, insulator 1410a, and sleeve 1410b are attached to the connection plate 1430 of the ignition electrodes, and the flame sensor 1420, insulator 1420a, and sleeve 1420b are attached to the connection plate 1440 of the flame sensor. Insulators 1410a and 1420a are insulation means configured to prevent sparking due to excitation when ignition is performed, and bushings 1410b and 1420b are configurations for sealing gaps between the outer surfaces of insulators 1410a and 1420a, ignition electrode connection plate 1430, and flame sensor connecting plate 1440.

As shown in FIG. 16, a connection portion 1500 of the ignition electrode assembly configured to assemble the ignition electrode assembly 1400 is provided on one side portion of the mixing chamber 1000. The connection portion 1500 of the ignition electrode assembly includes a second sealing member seating portion 1510 formed in in the form of a groove, so that the connecting plate 1430 of the ignition electrodes and the second sealing member 1700 connected to the lower side of the connecting plate 1430 of the ignition electrodes are received therein, and the third sealing member 1520 is formed in the form of a groove, so that the connecting plate 1440 of the flame sensor and a third sealing member 1800 attached to the underside of the flame sensor connecting plate 1440 is housed therein. In addition, a plurality of cooling fins 1530 configured to emit combustion heat are provided at the edge of the connecting portion 1500 of the ignition electrode assembly.

As shown in FIGS. 17-19, a mixing chamber flange 1110 and a burner flange 1330 coupled to an edge portion of a flat-type burner 1300 to support an edge portion of a flat-type burner 1300 are provided on one side portion of the mixing chamber 1000 to be connected to each other to sealing the mixing space S, and the ignition electrode assembly 1400 passes through the mixing chamber flange 1110 and the burner flange 1330 for further assembly at a location spaced from the mixing space S.

The sealing means may include a first sealing member 1600 provided at a portion where the mixing chamber flange 1110 and the burner flange 1330 are connected to each other to prevent the gas mixture introduced into the outside of the mixing space S from escaping, and the first sealing member 1600 may be made of heat-resistant graphite material.

In addition, the sealing means may include a second sealing member 1700 provided between the mixing chamber flange 1110 and the ignition electrode connecting plate 1430 to prevent the combustion gas discharged from the combustion chamber C to the outside and the third sealing member 1800 provided between the mixing chamber flange 1110. the chamber and the connection plate 1440 of the flame sensor to prevent the combustion gas from escaping from the combustion chamber C to the outside. In addition, the second sealing member 1700 and the third sealing member 1800 can be made of a rubber material and can be manufactured separately as separate components and subsequently assembled, while minimizing deformation of the rubber material due to high temperature.

In addition, a plurality of protruding contact protrusions 1710 may be provided at a predetermined interval on the outer side surface of each of the second sealing member 1700 and the third sealing member 1800, and may come into tight contact with the bottom surface of the electrode connecting plate 1430 ignition, the upper surface of the second sealing member 1700, the lower surface of the connecting plate 1440 of the flame sensor and the upper surface of the third sealing member 1800 in order to further improve the tightness.

In addition, as described above, in the ignition electrode assembly 1400, since the sleeves 1410b and 1420b are attached to the outer side surfaces of the insulators 1410a and 1420a, respectively, it is possible to block the combustion gas or gas mixture from escaping to the outside from the mixing chamber 1000.

Below, with reference to FIGS. 18 and 19, the configuration and operation of the cooling means configured to block the transfer of combustion heat to the seal means and the emission of combustion heat will be described.

The cooling means is configured to block the transfer of the heat of combustion coming from the combustion chamber C to the sealing means configured to prevent the heat of combustion from escaping through the gap between the mixing chamber 1000 and the ignition electrode assembly 1400, and may include air-type cooling means and cooling water type.

As described above, the mixing chamber flange 1110 and the burner flange 1330 may be provided on one side portion of the mixing chamber 1000 to be connected to each other to seal the mixing space S, the ignition electrode assembly 1400 extends through the mixing chamber flange 1110 and the burner flange 1330 to further assembly, and the air-type cooling means can be configured such that the mixing chamber flange 1110 and the burner flange 1330 are convectively cooled by the gas mixture introduced into the mixing space S.

Meanwhile, heat exchanger 2000 may include a fire tube heat exchanger and may include an outer cylinder 2100, an upper tube sheet 2200 defining a lower surface of the combustion chamber C and an upper surface of heat exchanger 2000, a plurality of tubes 2300 having upper end portions that are connected through an opening 2210a for inserting a tube provided on the upper tube sheet 2200 and through which the combustion gas flows through its interior, and a water tank B located on the outer sides of the tubes 2300 and in which the heating medium is placed in the outer cylinder 2100. The heating medium may be heating water used for heating, or warm water used for hot water supply.

In the water-type cooling means, the top flange 2230 of the tube sheet, configured to contact the heat transfer medium of the heat exchanger 2000 provided under the combustion chamber C, is configured to come into surface contact with the burner flange 1330 and the burner flange 1330, and the sealing means 1600, 1700 and 1800 can be cooled by the heating medium stored in the water tank B by conduction.

In addition, as described above, a plurality of cooling fins 1530 are provided on one side portion of the mixing chamber body 1100 on which the ignition electrode assembly 1400 is assembled along the edge of the ignition electrode assembly 140, and they also serve as cooling means.

As described above, according to the present invention, since the mixing chamber 1000 includes a flat-type mixing chamber body 1100 and a flat-type burner 1300, the height of the mixing chamber 1000 can be significantly reduced as compared with a conventional cylindrical burner structure.

In addition, since the sealing means and the cooling means are configured to pass the ignition electrode assembly 1400 through one side portion 1100 of the mixing chamber having a flat-type burner 1300 for further assembly, it is possible to block the gas mixture and combustion gas from escaping, and thermal damage can be prevented. sealing means due to the heat of combustion. Accordingly, since no insulating material is used in the mixing chamber 1000 having a flat-type burner 1300, the ignition electrode assembly 1400 can be reliably assembled and the gas mixture and combustion gas can be blocked from leaking while preventing thermal damage to the sealing means.

Meanwhile, as shown in FIG. 20, the upper tubesheet 2200 includes a lower portion 2210 defining a lower surface of the combustion chamber C, a side wall portion 2220 defining a side wall of the combustion chamber C, a circular portion 2240 including an upper flange 2230 tube plate, on which the burner flange 1330 is located, and configured to connect the upper end of the sidewall portion 2220 and the inner end of the upper tube sheet flange 2230, and a circular portion 2250 configured to connect the outer end of the lower portion 2210 and the lower end of the sidewall portion 2220 walls.

As described above, since the upper tubesheet 2200 includes circular portions 2240 and 2250, the hydraulic pressure of the heat transfer medium stored in the water tank B can be distributed in order to increase the service life of the upper tubesheet 2000. Diameter difference ratio between outer diameter d1 of the upper tube sheet flange 2230 and the inner diameter d2 of the lower end of the circular portion 2240 may be less than or equal to 20%. When the top flange 2230 of the tubesheet and the circular portion 2240 are formed with the difference in diameter ratio as described above, the flow rate and temperature of the water placed in the water tank B can be uniformly controlled.

In addition, the height h between the bottom surface of the flat-type burner 1300, which is inserted into the upper tubesheet 2200, and the lower surface of the upper tubesheet 2200, can be set such that the tip of the flame generated at the outlet of the flat-type burner 1300 can be located at a predetermined distance from the bottom surface of the top tube sheet 2200, and the height h can be set to about 80 mm based on the length of the flame from the flat-type burner 1300. As described above, the tip of the flame is positioned to be at a predetermined distance from the bottom surface of the top tube sheet 2200, since the condition that nitrogen oxide (NOx) and carbon monoxide (CO) are experimentally minimized can be achieved if when a predetermined gap is provided between the tip of the flame generated at the outlet of the flat-type burner 1300 and the lower surface of the top tube plate 2200.

In addition, as described above, since the height h of the upper tube sheet 2200 is designed to be low, the height of the combustion chamber C becomes low, and thus the overall height of the fire tube boiler 1 'can be reduced. That is, when a conventional cylindrical burner is used, the height between the lower surface of the burner and the lower surface of the upper tube sheet is approximately 190 mm, but in the case of the present invention, since the height can be reduced to approximately 80 mm, the height can be reduced by approximately 40 % compared to conventional prior art.

Meanwhile, in an embodiment, the ignition electrode assembly 1400 is formed at a location adjacent to one side of the mixed air supply duct 1200 connected to a fan 7000 configured to supply mixed air to the mixing chamber 1000. In this case, since a worker can easily access to the ignition electrode assembly 1400 through the mixed air supply 1200 can improve serviceability.

In another embodiment, as shown in FIG. 2 above, the ignition electrode assembly 1400 may be located on the opposite side of the mixed air supply pipe 1200. In this case, since the mixed air supplied from the fan 7000 is directly supplied to the ignition electrode unit 1400, ignition delay can be prevented.

As shown in FIGS. 21-26, the heat exchanger 2000 includes an outer cylinder 2100 having a heating medium inlet 2110 and a heating medium outlet 2120 and through which heat medium is introduced and removed, an upper tube sheet 2200 attached to the inner side of the outer cylinder 2100 and forming a combustion chamber C of a flat-type burner 1300 mounted thereon so as to form a path for a heating medium between the upper tube sheet 2200 and the outer cylinder 2100, a plurality of tubes 2300, each of which is formed in a flat shape, so that the combustion gas discharged from the combustion chamber C, carries out heat exchange with the coolant as it flows along the inner parts of the tubes 2300, a tube assembly 10,000 having turbulators 2400 and 2500 connected to the inner sides of the tubes 2300 to create turbulence in the combustion gas stream and configured to support the tubes 2300, and a lower tube board 2700, made with the possibility of under Holder for 10,000 tubes and connected to condensate trap 3000.

Multilayer diaphragms 2610, 2620 and 2630 are provided on the outer side surfaces of the tubes 2300, which will be vertically spaced apart, to direct the coolant to the coolant flow so that the direction of the coolant flow alternately changes inward and outward in the radial direction, and multilayer diaphragms 2610, 2620, and 2630 are fixed and supported by 2640 support. The plurality of tubes 2300 are vertically mounted so that the combustion gas discharged from the combustion chamber C flows downwardly, and the plurality of tubes 2300 are spaced apart from each other in the circumferential direction to be radially arranged.

In an embodiment, multilayer diaphragms include an upper diaphragm 2610, a middle diaphragm 2620, and a lower diaphragm 2630, each of which is plate-shaped. As shown in FIG. 24A, the upper diaphragm 2610 is provided with tube insertion holes 2610a into which tubes are inserted, and an orifice portion 2610b is formed in the center through which the heat medium flows. As shown in Fig. 24B, in the middle diaphragm 2620, since the tube insertion hole 2620a is formed with a gap from the outer side surfaces of the tubes 2300, the heat medium flows through the gap between the tube insertion hole 2620a and the tubes 2300. The center portion 2620b of the middle diaphragm 2620 is formed in a block design. In an embodiment, the tube insertion hole 2620a may be a structure in which two tubes 2300 are spaced apart in the direction of both sides to be inserted into the tube insertion hole 2620a. As shown in FIG. 24C, a tube insertion hole 2630a having the same structure as the upper diaphragm 2610 is formed in the lower diaphragm 2630, and a hole portion 2630b is formed in the center.

In accordance with the designs of the above-described multilayer diaphragms 2610, 2620 and 2630, as shown by the arrows in FIGS. 25 and 26, the heating medium introduced into the outer cylinder 2100 through the heating medium introduction hole 2110 flows towards the hole portion 2630b formed in the center of the lower diaphragm 2630 radially inward, the heat transfer medium that flows through the orifice portion 2630b to flow upwardly from the lower diaphragm 2630 is distributed in the spacer space of the tube insertion hole 2620a radially formed in the middle diaphragm 2620 to flow outwardly in the radial direction, and the heat transfer medium that flows through the tube insertion hole 2620a to flow upwardly from the middle diaphragm 2620 towards the hole portion 2610b formed in the center of the upper diaphragm 2610 inwardly in the radial direction, and then passes through the portion 2610b holes for dal The latest assembly through the hole 2120 for the outlet of the coolant, made on one side of the upper section of the outer cylinder 2100.

As described above, since the flow direction of the heating medium alternately changes inward and outward in the radial direction, the flow distance of the heating medium increases, and thus, the heat exchange efficiency of the heat exchanger 2000 can be improved, and since highly efficient heat exchange characteristics can be obtained even when the height of the heat exchanger 2000 becomes smaller than a conventional heat exchanger, the height of the heat exchanger 2000 can be reduced. In addition, the flow rate of the heating medium can be increased to prevent the boiling phenomenon due to partial overheating caused by the stagnation of the heating medium.

Next, with reference to FIGS. 27 to 33, the configuration and operation of the tube assembly 10000 will be described.

The tube assembly 10000 according to an embodiment of the present invention includes a tube 2300 having a flat shape so that the combustion gas discharged from the combustion chamber C flows through the interior of the tube 2300, which is to exchange heat with a heat transfer medium that flows from the outside of the upper turbulator 2400 attached to the inner side of the upper portion of the tube 2300 adjacent to the combustion chamber to provide surface contact with the tube 2300 in order to increase thermal conductivity and create turbulence in the combustion gas flow, and the lower turbulator 2500 attached to the inner side of the tube 2300 in a downward direction from the top turbulator 2400 to create turbulence in the combustion gas stream.

Upper turbulator 2400 includes tube contact surfaces 2410a and 2410b (2410) that come into close contact with inner side surfaces of tube 2300, and pressure maintaining portions 2420a and 2420b (2420) configured to flex away from cut portions 2430a and 2430b (2430) on the contact surfaces 2410a and 2410b (2410) tubes.

The tube contact surface 2410 includes a structure in which a first tube contact surface 2410a configured to come into surface contact with an inner side surface of one side portion of the tube 2300, and a second tube contact surface 2410b configured to surface contact with the inner the lateral surface of the other lateral portion of the tube 2300 are symmetrical.

The pressure maintaining portion 2420 is configured to prevent deformation and damage of the tube 2300 due to the hydraulic pressure of the coolant, and includes a first pressure holding portion 2420a in which a portion of the first cut portion 2430a of the first contact surface 2410a of the tube is bent in such a manner, to protrude towards the second tube contact surface 2410b, and a second pressure maintaining portion 2420b in which a portion of the second cut portion 2430b of the second tube contact surface 2410b is bent to protrude toward the first tube contact surface 2410a.

The cut-out area of the first cut-out portion 2430a is formed larger than the cut-out area of the second cut-out portion 2430b, the protruding end portion of the first pressure maintaining portion 2420a comes into contact with the second contact surface 2410b of the tube, and when the pressure maintaining portion 2420 is inserted into the tube 2300, the protruding end a portion of the second pressure maintaining portion 2420b is configured to come into contact with the inner side surface of the tube 2300 through the first cut portion 2430a.

In accordance with the above, the first pressure maintaining portion 2420a supports the first tube contact surface 2410a and the second tube contact surface 2410b so as to reliably maintain their shapes under hydraulic pressure, and the second pressure maintaining portion 2420b more securely supports the tube 2300 being supported the first tube contact surface 2410a; and the second tube contact surface 2410b.

In addition, as shown in FIG. 33, a plurality of first pressure maintaining portions 2420a and a plurality of second pressure holding portions 2420b are configured to be spaced apart from each other in the forward and backward and vertical directions, the first portion 2420a 'for maintaining the pressure located on the upper side and the first part for maintaining pressure 2420aʺ located on the lower side are provided in the vertical direction at locations that do not overlap each other, and the second part 2420b' for maintaining the pressure located on the upper side, and a second pressure maintaining portion 2420bʺ disposed on the underside are provided in the vertical direction at locations that do not overlap each other. In accordance with the above, since the hydraulic pressure that acts on the tube 2300 due to the first parts 2420a to maintain pressure and the second parts 2420b to maintain pressure, made in a zigzag shape in the forward and backward directions and in the vertical direction over the entire area of the upper turbulator 2400 , distributed evenly, deformation and damage of the 2300 tube can be effectively prevented.

In addition, since each of the first pressure maintaining portion 2420a and the second pressure maintaining portion 2420b is formed as a plate and a structure in which both side surfaces having wide areas are parallel to the direction of flow of the combustion gas as shown by arrows in FIG. 32A, flow resistance can be minimized in a process in which combustion gas passes through first pressure maintaining portions 2420a and second pressure holding portions 2420b as it flows.

As shown in FIG. 29, the lower turbulator 2500 includes a flat surface portion 2510 configured to divide the interior of the tube 2300 on both sides and located in the longitudinal direction of the tube 2300, and a first guide portion 2520 and a second guide portion 2530 spaced apart from each other. from the other in the longitudinal direction from both side surfaces of the flat surface portion 2510 and configured to protrude at an alternating slope.

The first guide portion 2520 is located on one side surface of the flat surface portion 2510 to be tilted to one side, and the second guide portion 2530 is located on the other side surface of the flat surface portion 2510 to be tilted to the other side. Accordingly, the heating medium introduced into the first guide portion 2520 and the second guide portion 2530 sequentially moves into the second guide portion 2530 and into the first guide portion 2520 disposed to abut opposite surfaces of the flat surface portion 2510 in order to alternately flow through both spaces in the flat surface area 2510.

At the end of the heat transfer medium inlet of the first guide portion 2520, a first fluid communication hole 2520b is provided, which is connected to one end side of the flat surface portion 2510 by the first connecting portion 2520a, and in which fluid is hydraulically communicated through both spaces in the flat surface portion 2510 between one the end face of the flat surface portion 2510, the first connecting portion 2520a, and the first guide portion 2520.

At the end of the heat transfer medium inlet of the first guide member 2530, there is a second opening 2530b for hydraulic communication, which is connected to the other end side of the flat surface portion 2510 by a second connecting portion 2530a, and in which fluid communicates through both spaces in the flat surface portion 2510 between the other end side a flat surface portion 2510, a second connecting portion 2530a, and a second guide portion 2530.

The first guide portion 2520 and the second guide portion 2530 may be configured such that portions of the flat portion 2510 can be cut to bend on both sides of the flat portion 2510 and fluid can communicate through both spaces in the flat portion 2510 through cut portions of flat surface portion 2510. In addition, support means 2530a and 2530b (2530) configured to protrude outwardly to engage with the inwardly facing side surfaces of the tube 2300 are provided on both side surfaces of the lower turbulator 2500. In addition, the first a support portion 2550 and a second support portion 2560, vertically spaced from each other in order to come into contact with both side surfaces of the tube 2300 and protrude in the forward and backward directions, are formed on the upper end portion and the lower end portion, respectively, of the lower turbulator 2500 ...

Meanwhile, as shown in FIGS. 34 to 37, the fire tube boiler 1 'includes a condensate collector 3000 in which condensate from condensation of steam that passes through a heat exchanger 2000 and is included in the combustion gas is collected and discharged, and the element 3200 leakage prevention, connected to the lower tubesheet 2700 of the heat exchanger 2000 and the connecting part of the condensate trap 3000 to prevent condensate leakage.

As shown in FIG. 22, the lower tubesheet 2700 is formed as a tube sheet structure and includes a horizontal portion 2710 having a plurality of holes for inserting tubes 2710a through which a lower end portion of tube 2300 formed therein to support the lower end portion passes. tube 2300 and forming the bottom surface of the water tank B, a vertical section 2720 connected to the lower end section of the outer cylinder 2100, and a circular section 2730 configured to connect the outer end of the horizontal section 2710 and the lower end section of the vertical section 2720 and formed into a convex, outwardly curved to distribute the hydraulic pressure of the heating medium.

As described above, since a circular portion 2730 formed in a convex outwardly curved shape is formed at the corner connecting the horizontal portion 2710 and the vertical portion 2720 of the bottom tube sheet 2700, the hydraulic pressure of the heat transfer medium can be evenly distributed, and thus the life can be increased. service by increasing the water pressure resistance of the 2700 bottom tube sheet, while minimizing deformation of the 2700 bottom tube sheet.

Next, a connection structure between the condensate trap 3000 and the leakage preventing member 3200 will be described.

As shown in FIGS. 36 and 37, a leakage preventing member 3200 is provided between the edge portion of the bottom tube sheet 2700 and the edge portion of the condensate trap 3000 to prevent condensate from leaking. Since the body 3210 of the leakage prevention member 3200 is provided in a shape that encloses the bottom portion of each circular portion 2730 and the vertical portion 2720 of the bottom tube sheet 2700, condensate CW generated in the horizontal section 2710 of the bottom tube sheet 2700 can be blocked from lateral movement. by blocking the lower portion 2330 so that it extends to one side of the lower portion of the body 3210 and can drain downward.

Meanwhile, a contact protrusion 3220 configured to protrude towards the outer side surface of the bottom tube sheet 2700 may be formed on the inner side surface 3210a of the leakage preventing member 3200. The plurality of contact protrusions 3220a, 3220b, 3220c, 3220d, 3220e, and 3220f may be formed at locations vertically spaced from the inner side surface 3210a of the leak prevention element 3200.

According to the configuration of the above-described contact protrusions 3220, when the hydraulic pressure acts, the contact protrusions 3220 of the leakage preventing member 3200, configured to protrude in a direction opposite to the direction in which the hydraulic pressure acts, may come into contact with the outer side surface of the bottom tube sheet 2700 to effectively prevent the phenomenon in which CW condensate penetrates into the gap, flowing between the bottom tube sheet 2700 and the leakage prevention member 3200. In addition, when a plurality of contact protrusions 3220 are formed at locations vertically spaced from each other, leakage of condensate CW can be prevented more reliably.

A first flange portion 3010 configured to support the leakage preventing member 3200 is provided at the edge portion of the condensate trap 3000, and the fastening protrusion 3010a and the fastening groove 3230a are attached to each other at respective locations provided on the leakage preventing member 3200 and the first flange portion 3010. In addition, In addition, the edge portion of the condensate trap 300 further includes an elongated portion 3020 configured to extend upwardly from the outer end of the first flange portion 3010 and come into intimate contact with the outer side surface of the leak preventing member 3200, and a second flange portion 3030 formed with being able to extend outwardly from the end of the elongated portion 3020, and the locating protrusion 3240a and the locating groove 3240b, mated to each other at respective locations, are formed on the upper portion of the leakage preventing member 3200 and the second flange portion 3030. According to and with the above, the CW condensate leakage can be blocked, and the location of the leakage preventing member 3200 can be securely fixed.

Meanwhile, as shown in FIG. 35, an outlet guide 3300 is provided in the condensate collector 3000, in which a plurality of perforations 3310a and 3310b (3310) are formed so that the combustion gas that passes through the heat exchanger 2000 is evenly distributed over the entire area of the condensate collector 3000. for further release. Perforations 3310 can be made in various sizes based on the direction of flow of the combustion gas.

In addition, since the stepped portion 3040 configured to direct the combustion gas flow that passes through the outlet guide portion 3300 into the condensate drain hole 3100 provided under one side of the condensate trap 3000 can be formed on the lower surface of the condensate trap 3000, as shown in dashed lines with an arrow that shows the direction of draining the condensate and a solid arrow that shows the direction of flow of the combustion gas (FIG. 37) into the condensate trap 3000, the direction of the drain of the condensate and the direction of flow of the combustion gas may coincide. According to the above configuration, since the condensate is guided in the direction of the combustion gas flow, corrosion of the bottom tubesheet 2700 due to condensate stagnation can be prevented, and the condensate can be directed to the condensate drain hole 3100 to drain it without hindrance.

As described above, the present invention is not limited to the above-described embodiments, it should be obvious to those skilled in the art that the present invention can be modified without departing from the spirit of the present invention set forth in the claims, and such modification is included within the scope of the present invention.

Claims (60)

1. A fire tube boiler, comprising: a mixing chamber located on the combustion chamber and having a mixing space in which the combustion gas and air are mixed, and a flat-type burner; an ignition electrode assembly configured to pass through one side portion of the mixing chamber for further assembly and downwardly from a flat-type burner over an upper portion of the combustion chamber; and sealing means configured to block leakage of the gas mixture from the mixing space and combustion gas from the combustion chamber to the outside through the gap between the mixing chamber and the ignition electrode assembly. 2. A fire tube boiler according to claim 1, wherein: a mixing chamber flange and a burner flange are provided on one side portion of the mixing chamber to be connected to each other to seal the mixing space; and the ignition electrode assembly passes through the mixing chamber flange and the burner flange at a point away from the mixing space for further assembly. 3. The fire tube boiler of claim 2, wherein the sealing means includes a first sealing member provided at a portion where the mixing chamber flange and the burner flange are connected to each other to prevent leakage of the gas mixture. 4. A fire tube boiler according to claim 3, wherein an insulating material configured to block the transfer of combustion heat generated from the combustion chamber is provided on the first sealing member. 5. A fire tube boiler according to claim 3, wherein: a connecting plate through which the ignition electrode assembly passes for connection thereto is provided in one side portion of the mixing chamber; and the sealing means includes a second sealing member provided between an upper portion of one side portion of the mixing chamber and a connecting plate to prevent leakage of combustion gas. 6. The fire tube boiler of claim 5, wherein a plurality of outwardly protruding contact projections are provided at predetermined intervals on the outer side surface of the second sealing member. 7. A fire tube boiler according to claim 1 or 3, in which: the ignition electrode assembly includes an ignition electrode and a flame sensor; a connection plate for an ignition electrode through which an ignition electrode passes for connection thereto, and a connection plate for a flame sensor through which a flame sensor passes for connection thereto are provided on one side portion of the mixing chamber; and sealing means is provided between the upper portion of one side portion of the mixing chamber and the connecting plate of the ignition electrode, and between the upper portion of one side portion of the mixing chamber and the connecting plate for the flame sensor. 8. The fire tube boiler according to claim 1, further comprising cooling means configured to block the transfer of combustion heat generated from the combustion chamber (C) to the sealing means. 9. The smoke tube boiler of claim 8, wherein the cooling means include air-type cooling means and water-type cooling means. 10. A fire tube boiler according to claim 9, wherein: a mixing chamber flange and a burner flange are provided on one side portion of the mixing chamber to be connected to each other to seal the mixing space; the ignition electrode assembly passes through the mixing chamber flange and the burner flange for further assembly; and the mixing chamber flange and the burner flange are cooled with a gas mixture introduced into the mixing space in an air-type cooling means. 11. A fire tube boiler according to claim 9, wherein: a mixing chamber flange and a burner flange are provided on one side portion of the mixing chamber to be connected to each other to seal the mixing space; the ignition electrode assembly passes through the mixing chamber flange and the burner flange for further assembly; and the upper flange of the tube sheet made with the possibility of contacting with the heat carrier of the heat exchanger provided under the combustion chamber is intended for contact with the burner flange for cooling the burner flange in a water-type cooling means. 12. The smoke tube boiler of claim 8, wherein a plurality of cooling fins are provided on one side portion of the mixing chamber in which the ignition electrode assembly is assembled along the edge of the ignition electrode assembly. 13. A fire tube boiler according to claim 1, comprising: an outer cylinder provided at the end of the tube through which the combustion gas flows inside it to form an outer wall of the water tank in which the heat transfer medium is placed outside the tube; and a lower tube sheet having a tube sheet structure made of a horizontal section configured to support the lower end section of the tube and form the bottom surface of the water tank, a vertical section connected to the outer side surface of the lower end section of the outer cylinder, and a circular section made with the possibility of connecting the outer end of the horizontal section and the lower end section of the vertical section and having a convex outward curved shape for distributing the hydraulic pressure of the heat carrier. 14. The fire tube boiler of claim 13, wherein the vertical portion of the lower tube sheet is connected to abut against the outer side surface of the lower end portion of the outer cylinder. 15. A fire tube boiler according to claim 13, wherein: a flange portion configured to extend outwardly by a predetermined length is formed on a vertical portion of the bottom tube sheet; and the flange part and the outer side surface of the outer cylinder are welded to each other. 16. A fire tube boiler according to claim 13, comprising: a condensate trap provided under the bottom tube sheet to collect condensate formed on the bottom tube sheet; and a leakage prevention member provided between the edge portion of the bottom tube sheet and the edge portion of the condensate trap to prevent condensate from leaking out. 17. A fire tube boiler according to claim 16, wherein: the leakage prevention member is shaped to enclose the lower portion of each circular portion and the vertical portion of the lower tube sheet; and the condensate formed in the horizontal section of the bottom tube sheet is blocked from lateral movement by blocking the leakage prevention element and flows downward. 18. A fire tube boiler according to claim 17, wherein the side wall of the condensate trap is configured to be located close to the boundary between the horizontal section and the circular section of the bottom tube sheet to direct the condensate discharge. 19. The fire tube boiler of claim 16, wherein a contact protrusion capable of protruding toward an outer side surface of the bottom tube sheet is formed on an inner side surface of the leakage prevention member. 20. The fire tube boiler of claim 19, wherein the plurality of contact protrusions are formed at locations vertically spaced from an inner side surface of the leak prevention member. 21. A fire tube boiler according to claim 19, wherein: a first flange portion configured to extend outwardly from an upper end of a side wall of the condensate trap to support a lower portion of the leakage preventing member is provided on an edge portion of the condensate trap; and a fastening projection and a fastening groove attached to each other at respective locations are provided on the leakage preventing member and the first flange portion. 22. The fire tube boiler of claim 21, further comprising: an elongated portion configured to extend upwardly from the outer end of the first flange portion and come into close contact with the outer side surface of the leak prevention member; and a second flange portion configured to extend outwardly from an end of the elongated portion at the edge portion of the condensate trap, wherein the locating protrusion and the locating groove mating with each other at respective locations are formed on the upper portion of the leakage preventing member and the second flange portion in order to block the leakage of condensate and fix the location of the leakage preventing member. 23. A boiler with fire tubes according to claim 13, in which an outlet guide having a plurality of perforations made therein so that the combustion gas that passes through the heat exchanger is evenly distributed over the entire area of the condensate collector from which the condensate is to be drained is provided in the condensate trap. 24. A fire tube boiler according to claim 23, wherein a stepped portion adapted to direct the combustion gas flow that passes through the outlet guide into the condensate drain hole is formed on the lower surface of the condensate trap so that the condensate trap coincides with the condensate drain direction and the direction of flow of the combustion gas. 25. The smoke tube boiler of claim 1, wherein the mixing chamber includes a flat mixing chamber body and a flat-type burner disposed horizontally on the combustion chamber. 26. A fire tube boiler according to claim 25, wherein the separation space between the lower surface of the mixing chamber body and the upper surface of the flat-flame burner is made in the form of a flat disk. 27. A boiler with fire tubes according to claim 1, further comprising a heat exchanger in which heat exchange is carried out between the heat of combustion of the combustion chamber and the heat carrier, wherein the heat exchanger includes an outer cylinder through which the heat carrier is introduced and removed and which forms the outer wall of the water tank in which the heat carrier is placed, an upper tube sheet having a tube sheet structure attached to the inner side of the outer cylinder and forming a combustion chamber thus, so that a path is formed for the coolant between the upper tube sheet and the outer cylinder, a plurality of tubes, each of which has a flat shape so that the combustion gas generated from the combustion chamber carries out heat exchange with the coolant that flows from the outside, while flowing around the inner sides tubes, a turbulator attached to the inner sides of the tubes to create turbulence in the combustion gas flow, a multilayer diaphragm provided between the outer cylinder and the tube for directing the coolant so that the direction of the coolant flow alternately changes inward and outward in a radial direction pressure, and a bottom tube sheet having a tube sheet structure configured to support the lower end portions of the tubes and form the bottom surface of the water tank. 28. A fire tube boiler according to claim 27, wherein: the flange of the upper tube sheet is configured to protrude outward from the upper end of the circular portion; and the ratio of the difference in diameters between the outer diameter of the upper tube sheet flange and the inner diameter of the lower end of the circular section is less than or equal to 20%. 29. A boiler with smoke tubes according to claim 27, in which the height between the lower surface of the flat-type burner inserted into the upper tube plate and the lower surface of the upper tube plate is set so that the tip of the flame generated from the flat-flame burner is located at a predetermined distance from the bottom surface of the top tube sheet. 30. A fire tube boiler according to claim 27, wherein the turbulator is formed from an upper turbulator connected to the inner side of the upper tube portion adjacent to the combustion chamber to provide surface contact with the tube to increase thermal conductivity and create turbulence in the combustion gas stream, and a lower turbulator connected to the inner side of the tube downwardly from the upper turbulator to create turbulence in the combustion gas stream.

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