CN109964088B

CN109964088B - Smoke tube type boiler

Info

Publication number: CN109964088B
Application number: CN201780070818.2A
Authority: CN
Inventors: 朴焌圭; 朴德植; 金政禹
Original assignee: Kyungdong Navien Co Ltd
Current assignee: Kyungdong Navien Co Ltd
Priority date: 2016-12-30
Filing date: 2017-12-29
Publication date: 2021-08-17
Anticipated expiration: 2037-12-29
Also published as: RU2737576C1; CA3047961C; CN109964088A; CA3047961A1; KR102136170B1; KR20180079205A

Abstract

The invention aims to provide a flue tube boiler which can prevent mixed gas and exhaust gas from leaking through a gap between a mixing chamber and an ignition rod assembly. The flue tube boiler of the present invention for achieving the object comprises: a mixing chamber disposed on the upper side of the combustion chamber, and provided with a mixing space for mixing combustion gas and air, and a flat burner; an ignition rod assembly which penetrates through one side part of the mixing chamber for assembly and crosses the upper part of the combustion chamber to extend to the lower side of the flat burner; and a sealing unit for blocking the mixed gas of the mixing space and the exhaust gas of the combustion chamber from leaking to the outside through a gap between the mixing chamber and the ignition bar assembly.

Description

Smoke tube type boiler

Technical Field

The invention relates to a smoke tube type boiler, in particular to a smoke tube type boiler which is composed of the following structures: when the ignition rod assembly is connected by penetrating one side part of a mixing chamber provided with a flat burner, leakage of mixed gas and exhaust gas is prevented, thermal damage of the ignition rod assembly is prevented, corrosion caused by accumulation of condensed water is prevented, and leakage of the condensed water is reliably blocked.

Background

Generally, a boiler is equipped with a heat exchanger for exchanging heat between combustion gas generated by burning fuel and a heat medium, so as to perform heating or hot water supply using the heated heat medium. Such a boiler may include: a heat exchange unit having a heat exchanger therein; a burner assembled on the upper part of the heat exchange part; and a combustion chamber which is located between the burner and the heat exchanger and which is supplied with combustion gas and air for combustion.

Fig. 1 is a diagram schematically showing the structure of a conventional flue-tube boiler.

The existing flue tube boiler includes: a blower 10 for supplying combustion gas and air; a cylindrical burner 20 for burning a mixed gas of a combustion gas and air; a combustion chamber 30 for combusting the mixed gas by the burner 20; a heat exchanger 40 for exchanging heat between the combustion gas generated in the combustion chamber 30 and the heat medium; a heat insulating material 50 for preventing heat generated in the combustion chamber 30 from being transferred to an upper side around the cylindrical burner 20; and an ignition rod 60 that is provided through the heat insulating material 50 and ignites the mixed gas.

The heat exchanger 40 may include: an outer cylinder 41; a plurality of tubes 42 provided inside the outer cylinder 41, and through which the combustion gas generated in the combustion chamber 30 passes; and a water tank 43 for accommodating a heating medium outside the pipe 42.

According to the structure of the conventional flue-tube boiler as described above, since the cylindrical burner 20 having a vertically long shape is provided, the height of the entire boiler is greatly increased, and thus a small boiler cannot be manufactured, which causes a problem of limited installation space.

In the conventional flue-pipe boiler, when the ignition rod 60 is provided to penetrate the combustion chamber cover 12 disposed between the blower 10 and the cylindrical burner 20, the heat insulator 50 is used to prevent heat from being conducted to the ignition rod 60.

However, the heat insulating material 50 is broken or broken into a small particle form due to heat during combustion, thereby causing problems such as clogging of the tube 42 of the heat exchanger 40 as a combustion gas passage, and in the case where the combustion chamber cover 12 and the mixing chamber 11 including the cylindrical combustor 20 are decomposed for maintenance, there is a problem that damage to the heat insulating material 50 is inevitably caused.

In addition, when the ignition rod 60 is provided on the heat exchanger 40 side, unnecessary steps and parts are added, which increases the number of manufacturing steps and also brings about a risk of leakage of the heat medium.

Korean patent No. 10-0575187 and korean patent No. 10-0581580 disclose prior arts related to the structure of assembling an ignition rod to a combustion chamber cover as described above.

Also, in the case of applying a flat burner having combustion performance superior to that of the cylindrical burner 20, a heat exchanger is combined to a mixing chamber to which the flat burner is combined and a side of the mixing chamber, so that a combustion chamber is formed between the mixing chamber and the heat exchanger. In this case, when the ignition rod assembly penetrates one side portion of the mixing chamber and is coupled to the mixing chamber, there is a possibility that the mixed gas in an unburned state leaks to the outside through a gap between the mixing chamber and the ignition rod assembly. If the mixed gas in an unburned state (unburned gas) as described above leaks to the outside, there is a fatal risk to the human body.

In the case where the sealing unit for preventing the leakage of the mixture gas as described above is provided, since the high-temperature heat of the combustion chamber is transferred to the sealing unit, the sealing unit may be easily broken due to the thermalization, so that there is a problem in that it is not easy to provide the sealing unit in the case of preventing the breakage due to the thermalization.

Further, the flue-tube heat exchanger disclosed in european patent publication No. EP 2508834 and european patent publication No. EP2437022 includes: and an outer cylinder provided with a water tank for accommodating a heating medium on the outside of the pipe. An upper tube plate that forms an upper surface of the water tank and supports an upper end portion of the outer tube is coupled to an upper end portion of the tube, and a lower tube plate that forms a floor surface of the water tank and supports a lower end portion of the outer tube is coupled to a lower end portion of the tube.

In the flue tube heat exchanger configured as described above, since the heat medium contained in the water tank exerts a high water pressure on the lower tube plate, a water pressure resistance capable of withstanding a high water pressure is required to maintain the durability of the lower tube plate.

However, the lower tube plate provided in the conventional flue tube heat exchanger has a problem of poor durability because it does not have a structure capable of dispersing water pressure.

Further, the conventional flue-tube boiler has the following structure: the condensate receiver is provided at a lower side of the lower tube plate, and a sealing member for preventing leakage of condensate is provided between an edge of the lower tube plate and an edge of the condensate receiver. The sealing member is configured to support a lower end portion of a side surface portion of the lower tube plate.

However, according to the structure in which the seal member is coupled between the lower tube plate and the condensate receiver, the condensate generated in the flue-tube heat exchanger accumulates between the lower end portion of the side surface portion of the lower tube plate and the seal member, and this causes a problem of corrosion of the lower tube plate. Korean laid-open patent No. 10-2005-0036152 and the like disclose related art related to a sealing structure of an existing condensate water receiver.

Disclosure of Invention

Technical problem

The present invention has been made to solve the above problems, and an object of the present invention is to provide a flue-tube boiler capable of preventing a mixed gas and an exhaust gas from leaking through a gap between a mixing chamber and an ignition rod assembly.

Another object of the present invention is to provide a flue tube boiler comprising: when the ignition bar assembly is provided to penetrate the mixing chamber, the size of the heat insulating material is greatly reduced to prevent the flow path from being blocked due to the damage of the heat insulating material, and a cooling unit for blocking the heat transfer to the ignition bar assembly and the ignition bar sealing unit near the ignition bar assembly is provided.

It is still another object of the present invention to provide a flue tube boiler constructed as follows: the water pressure resistance of the lower tube plate can be improved, corrosion caused by accumulation of condensed water on the lower tube plate can be prevented, and leakage of the condensed water can be reliably blocked.

It is still another object of the present invention to provide a flue tube boiler capable of reducing the height of the boiler and improving heat exchange efficiency as compared to the existing boiler.

Technical scheme

The flue tube boiler of the present invention for achieving the above objects comprises: a mixing chamber disposed on the upper side of the combustion chamber, and provided with a mixing space for mixing combustion gas and air, and a flat burner; an ignition rod assembly which penetrates through one side part of the mixing chamber for assembly and crosses the upper part of the combustion chamber to extend to the lower side of the flat burner; and a sealing unit for blocking the mixed gas of the mixing space and the exhaust gas of the combustion chamber from leaking to the outside through a gap between the mixing chamber and the ignition bar assembly.

The mixing space may be sealed by disposing a mixing chamber flange and a burner flange on one side of the mixing chamber in contact with each other, and the ignition rod assembly may be assembled by passing through the mixing chamber flange and the burner flange at a position spaced apart from the mixing space.

The sealing unit may include: and a first sealing member provided at a portion where the mixing chamber flange meets the burner flange, for preventing leakage of the mixed gas.

The first sealing member may be provided at an upper portion thereof with a heat insulating material for blocking heat transfer of combustion heat generated in the combustion chamber. The insulation material is different from the prior art, so that the size of the insulation material is remarkably reduced.

A coupling plate for penetrating and coupling the ignition bar assembly may be provided at an upper portion of one side portion of the mixing chamber, and the sealing unit may include: a second sealing member provided between an upper portion of one side portion of the mixing chamber and the coupling plate, for preventing leakage of the exhaust gas.

The second sealing member may be formed with a plurality of contact protrusions protruding outward on an outer surface thereof at predetermined intervals.

The ignition bar assembly may include an ignition bar and a flame sensing bar, an ignition bar coupling plate for coupling the ignition bar and a flame sensing bar coupling plate for coupling the flame sensing bar are disposed at an upper portion of one side portion of the mixing chamber, and the sealing unit is disposed between the ignition bar coupling plate and the upper portion of one side portion of the mixing chamber and between the flame sensing bar coupling plate and the upper portion of one side portion of the mixing chamber.

The flue tube boiler may further include: a cooling unit for blocking heat transfer of combustion heat generated in the combustion chamber C to the sealing unit.

The cooling unit may include an air-cooling type cooling unit and a water-cooling type cooling unit.

The mixing space may be hermetically sealed by providing a mixing chamber flange and a burner flange on one side of the mixing chamber in a manner to be in contact with each other, the ignition rod assembly may be assembled by penetrating the mixing chamber flange and the burner flange, and the air-cooling type cooling unit may cool the mixing chamber flange and the burner flange by the mixture gas flowing into the mixing space.

In the water-cooled cooling unit, an upper tube plate flange of the heat exchanger disposed at a lower side of the combustion chamber and contacting a heat medium may be disposed so as to contact the burner flange, thereby cooling the burner flange.

A plurality of fins may be provided along the circumference of the ignition bar assembly at one side portion of the mixing chamber in which the ignition bar assembly is assembled.

The flue tube boiler may include: an outer cylinder which is arranged on the periphery of a pipe for allowing combustion gas to pass through, and forms the outer wall of a water tank for accommodating a heating medium on the outer side of the pipe; the lower pipe plate of the hard plate structure comprises a horizontal part, a vertical part and an arc-shaped part, wherein the horizontal part supports the lower end part of the pipe and forms the bottom plate surface of the water tank, the vertical part is combined with the outer side surface of the lower end part of the outer cylinder, and the arc-shaped part is connected with the outer side end of the horizontal part and the lower end part of the vertical part and forms a shape which is convexly bent towards the outer side, so that the water pressure of the heat medium is dispersed.

The vertical portion of the lower tube plate may be inserted into and coupled to an outer side surface of the lower end portion of the outer tube.

A flange portion extending outward by a predetermined length may be formed at an upper end of the vertical portion of the lower tube plate, and the flange portion may be welded to an outer surface of the outer cylinder.

The flue tube boiler may include: a condensed water receiver provided at a lower side of the lower tube plate to collect condensed water generated at the lower tube plate; and a water leakage preventing member interposed between an edge portion of the lower tube plate and an edge portion of the condensed water receiver, for preventing leakage of condensed water.

The water leakage preventing member may be provided in a form of surrounding the arc-shaped portion and the lower portion of the vertical portion of the lower tube plate, and condensed water condensed at the horizontal portion of the lower tube plate may be laterally blocked by the water leakage preventing member, so that movement in a lateral direction may be blocked and may fall downward.

The sidewall of the condensed water receiver may be provided to be located near an interface of the horizontal portion and the arc portion of the lower tube sheet, thereby guiding the falling of the condensed water.

The inner side surface of the water leakage preventing member may be formed with a contact protrusion protruding in a direction toward the outer side surface of the lower tube sheet.

The plurality of the contact protrusions may be formed at positions spaced apart from each other in the vertical direction on the inner surface of the water leakage preventing member.

The condensed water receiver may be provided at an edge portion thereof with: and a first flange portion extending outward from an upper end of a sidewall of the condensate receiver to support a lower portion of the water leakage preventing member, wherein the water leakage preventing member and the first flange portion are formed with a fastening protrusion and a fastening groove fastened to corresponding positions.

The edge portion of the condensate receiver may further include: an extension part extending from the outer end of the first flange part to the upper side and closely attached to the outer side surface of the water leakage preventing part; and a second flange part extending outward from the end of the extension part, wherein an insertion protrusion and an insertion groove are formed at the upper part of the water leakage preventing part and the second flange part, and the insertion protrusion and the insertion groove are inserted into corresponding positions, so that leakage of condensed water is blocked, and the position of the water leakage preventing part is fixed.

An exhaust guide formed with a plurality of punched holes may be provided inside the condensate water receiver to uniformly distribute the combustion gas passing through the heat exchanger over the entire area of the condensate water receiver to be discharged.

A stepped portion may be formed on a bottom surface of the condensate receiver, and the stepped portion guides the flow of the combustion gas passing through the exhaust guide to the condensate water discharge side, so that the condensate water is discharged in the same direction as the flow of the combustion gas inside the condensate receiver.

The mixing chamber may include a mixing chamber body having a flat shape and the flat plate-shaped burner disposed at an upper side of the combustion chamber in a horizontal direction.

The space where the bottom surface of the mixing chamber body is spaced apart from the upper surface of the flat burner may be formed in a flat disc shape.

The flue tube boiler may further include: a heat exchanger for exchanging heat between combustion heat of the combustion chamber and a heat medium, the heat exchanger comprising: an outer cylinder forming an outer wall of a water tank for allowing and discharging a heat medium and accommodating the heat medium; an upper tube plate of a hard plate structure coupled to an inner side of the outer tube to form a heat medium flow path between the upper tube plate and the outer tube and to form the combustion chamber; a plurality of tubes configured in a flat shape for allowing the combustion gas generated in the combustion chamber to flow along the inside of the plurality of tubes and to exchange heat with a heat medium flowing outside; a turbulator coupled to an inside of the tube to guide generation of turbulent flow in a flow of the combustion gas; a multi-stage diaphragm disposed between the outer cylinder and the pipe to guide the flow direction of the heating medium to be alternately changed to the inner side and the outer side in the radial direction; and a lower pipe plate of a hard plate structure supporting a lower end portion of the pipe and constituting a bottom surface of the water tank.

The flange of the upper tube plate may be formed to protrude outward at an upper end of the arc portion, and a ratio of a diameter difference between an outer diameter of the flange of the upper tube plate and an inner diameter of a lower end of the arc portion to the outer diameter of the flange of the upper tube plate is 20% or less.

The height between the bottom surface of the flat plate-shaped burner inserted into the upper tube sheet and the bottom surface of the upper tube sheet may be set such that the end of the flame generated at the flat plate-shaped burner is spaced apart from the bottom plate surface of the upper tube sheet by a predetermined distance, and preferably may be set to a height of about 80 mm.

The turbulator may include: an upper turbulator bonded to an upper inner side of the tube near the combustion chamber in surface contact with the tube, thereby improving heat conductivity and guiding generation of turbulence in a flow of the combustion gas; and a lower turbulator coupled to an inner side of the tube at a lower side of the upper turbulator, thereby inducing turbulence in a flow of the combustion gas.

Advantageous effects

According to the flue pipe boiler of the present invention, in order to apply the flat burner which is easy to manufacture and superior in productivity as compared with the cylindrical burner, when the ignition rod assembly is provided to penetrate one side portion of the mixing chamber, leakage of the mixed gas and the exhaust gas can be prevented.

In addition, when a flat burner having a wider combustion region than a cylindrical burner is used, the gas and air flowing into the combustion region contribute to a cooling structure for the ignition rod assembly that penetrates through one side portion of the mixing chamber and is joined thereto, and the ignition rod assembly can be prevented from being damaged by heating, thereby improving durability.

Further, the lower tube plate is formed to surround the outer side surface of the outer cylinder, and an arc-shaped portion convexly curved outward is formed at a corner connecting the horizontal portion and the vertical portion of the lower tube plate, so that the water pressure of the heat medium is dispersed, whereby the water pressure resistance of the lower tube plate can be improved, deformation can be minimized, and durability can be improved.

Further, the lower tube plate of the flue-tube heat exchanger is configured to surround the outer side surface of the outer cylinder, the water leakage preventing member is configured to surround the lower portion and the arc portion of the vertical portion of the lower tube plate, and the side wall of the condensed water receiver is disposed so as to be located in the vicinity of the boundary between the horizontal portion and the arc portion of the lower tube plate, thereby guiding the condensed water to fall down.

And, through forming the protruding hugging closely of direction of the lateral surface of the lower tube sheet in the medial surface of the leak protection parts, when having acted on water pressure according to this, along the protruding hugging closely of lateral surface of the lower tube sheet of the protruding leak protection parts of direction opposite to the direction that water pressure acted on to can prevent the phenomenon of revealing of the comdenstion water. Further, if a plurality of the contact protrusions are formed at positions spaced apart vertically, leakage of the condensed water can be prevented more reliably.

Further, by providing the mixing chamber body having a flat shape and the flat burner and reducing the height of the upper tube plate having a hard plate structure to the lowest height at which the mixed gas can be completely combusted to improve the heat exchange efficiency of the heat exchanger, the height of the boiler can be reduced compared to the conventional heat exchanger, and a small-sized flue-tube boiler having high efficiency can be provided.

Drawings

Fig. 1 is a view schematically showing the structure of a conventional flue-tube boiler.

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

Fig. 3 is a bottom side perspective view of the mixing chamber shown in fig. 2.

Fig. 4 is an exploded perspective view showing a structure in which the ignition bar assembly is coupled to the mixing chamber.

Fig. 5 is an enlarged perspective view of the joint portion of the ignition bar assembly.

Fig. 6 is a cross-sectional view of fig. 2.

Fig. 7 is a partially sectional perspective view taken along line a-a of fig. 6.

Fig. 8 is a partially enlarged sectional view taken along line a-a of fig. 6.

Fig. 9 is a partial perspective view of a boiler equipped with a smoke tube heat exchanger according to an embodiment of the present invention.

Fig. 10 is an exploded perspective view of a main portion of a boiler equipped with a smoke tube type heat exchanger according to an embodiment of the present invention.

Fig. 11 (a) is a plan view of the water leakage preventing member, and fig. 11 (B) is a cross-sectional view and an enlarged view taken along line B-B of fig. 11 (a).

Fig. 12 is a sectional view of the portion "a" of fig. 2.

FIG. 13 is a perspective view of the external appearance of a flue tube boiler according to another embodiment of the present invention.

Fig. 14 is a perspective view of the mixing chamber.

Fig. 15 is a bottom-side perspective view of the mixing chamber.

Fig. 16 is an exploded perspective view of a structure in which an ignition rod and a flame sensing rod are combined in a mixing chamber.

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

Fig. 18 is a partial sectional perspective view taken along line C-C of fig. 7.

Fig. 19 is a partial sectional view taken along line C-C of fig. 7.

Fig. 20 is a sectional view showing a coupling structure of an upper tube plate and a burner.

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

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

Fig. 23 is a sectional view showing a case where the tube assembly is joined to the multi-stage diaphragm.

Fig. 24 (a) is a plan view of fig. 23, (b) is a sectional view taken along line D-D of fig. 23, and (c) is a sectional view taken along line E-E of fig. 23.

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

Fig. 26 is a sectional perspective view taken along line F-F of fig. 25.

FIG. 27 is a perspective view showing an embodiment of a tube assembly.

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

FIG. 29 is a front view of an upper turbulator and a lower turbulator.

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

Fig. 31 is a plan view of fig. 30.

Fig. 32 (a) is a sectional view taken along line G-G of fig. 31, and (b) is a sectional perspective view taken along line G-G of fig. 31.

Fig. 33 is a left side view of fig. 30.

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

FIG. 35 is an exploded perspective view of a flue tube boiler in accordance with another embodiment of the present invention.

Fig. 36 (a) is a plan view of the water leakage preventing member, and fig. 36 (b) is a cross-sectional view and an enlarged view taken along the line H-H in fig. 36 (a).

FIG. 37 is a sectional view showing a sealing structure and a condensed water drain structure of a flue-tube boiler according to another embodiment of the present invention.

Description of the symbols

10: the blower 11: mixing chamber

12: combustion chamber cover 20: cylindrical burner

30: the combustion chamber 40: heat exchanger

41: outer cylinder 42: pipe

43: water tank 50: heat insulating material

60: ignition bar 1, 1': smoke tube type boiler

100: mixing chamber 110: mixed gas inlet

120: mixing chamber flange 130: flat-plate-shaped combustor

131: the flame orifice plate 131 a: flame hole

132: metal fibers 133: burner flange

140: ignition rod assembly 141: first ignition rod

142: second ignition bar 143: flame sensing rod

141a, 142a, 143 a:

insulators

141b, 142b, 143 b: bushing

144:

bonding plates

144a, 144b, 144 c: combining hole

150: ignition bar assembly coupling portion 151: mounting portion of joint plate

152: second seal member seating portion 153: through hole

154: the heat sink 160: first seal member

170: heat insulating material 180: second seal member

181: the close contact projection 190: sealing member

200: heat exchanger 210: outer cylinder

220: the upper tube plate 221: pipe insertion hole

222: upper tube sheet flange 230: pipe

240: a lower tube plate 300: condensate water receiver

400: exhaust pipe 500: water leakage prevention part

510: main body 510 a: inner side surface of the water leakage preventing part

520. 521, 522, 523, 524: the close fitting projection 530: lower part of water leakage prevention part

531: fastening groove 540: upper part of the water leakage preventing part

541: insertion projection 1000: mixing chamber

1100: mixing chamber body 1110: mixing chamber flange

1200: mixed gas inflow port 1300: flat-plate-shaped combustor

1310: the flame orifice plate 1330: burner flange

1400: ignition rod assembly 1410: ignition rod

1420: flame sensing rod 1500: ignition rod assembly joint

1600: first seal member 1700: second seal member

1800: third seal member 1900: sealing member

2000: heat exchanger 2100: outer cylinder

2110: heat medium inflow port 2120: heat medium outlet

2200: upper tube sheet 2240: arc-shaped part

2300: tube 10000: pipe assembly

2400: upper turbulator 2500: lower turbulator

2610: upper diaphragm 2620: middle part diaphragm

2630: lower diaphragm 2640: supporting table

2700: lower tube sheet 3000: condensate water receiver

3100: condensate drain 3200: water leakage prevention part

3300: exhaust guide 3310: punching hole

4000: exhaust pipe 5000: premixing chamber

6000: mixed gas adjusting unit 7000: air blower

Detailed Description

Hereinafter, the configuration and operation of the preferred embodiment of the present invention will be described in detail with reference to the drawings.

Referring to fig. 2 to 8, a flue tube boiler 1 according to an embodiment of the present invention includes: a mixing chamber 100 disposed at an upper side of the combustion chamber C, and provided with a mixing space S for mixing the combustion air supplied through a mixed gas inflow port 110 connected to the blower with the gas, and a flat burner 130 for burning the mixed gas; a heat exchanger 200 for exchanging heat between the heat medium and the combustion gas; a condensed water receiver 300 for collecting condensed water generated by condensing water vapor contained in the combustion gas through the heat exchanger 200; and an exhaust pipe 400 connected to one side of the condensed water receiver 300 such that the combustion gas passing through the heat exchanger 200 is discharged.

And, includes: an ignition rod assembly 140 which penetrates one side portion of the mixing chamber 100, is assembled, and extends to the lower side of the flat burner 130 across the upper portion of the combustion chamber C; and a sealing unit for blocking the mixed gas of the mixing space S and the exhaust gas of the combustion chamber C from leaking to the outside through a gap between the mixing chamber 100 and the ignition bar assembly 140.

The burner to which the present invention is applied is a flat plate type burner 130, including: a flat plate-shaped porthole plate 131 in which a plurality of portholes 131a are formed; and metal fibers 132 coupled to the flame orifice plate 131. Since the flat burner 130 is disposed across the entire region of the mixing space S as described above, the gas and air flowing into the flat burner 130 are advantageous to the air-cooling type structure, and the combustion region is expanded to reduce the load per unit area, so that the emission of pollutants such as CO and NOx can be reduced, thereby improving the combustion performance.

The ignition rod assembly 140 penetrates one side portion of the mixing chamber 100 to be assembled. The ignition bar assembly 140 may include a first ignition bar 141, a second ignition bar 142, and a flame sensing bar 143.

Insulators

141a, 142a, and 143a made of an insulating material are coupled to outer surfaces of the first ignition rod 141, the second ignition rod 142, and the flame sensing rod 143, and

bushings

141b, 142b, and 143b for maintaining airtightness are coupled to outer surfaces of the

insulators

141a, 142a, and 143 a.

The first ignition rod 141, the second ignition rod 142, the flame sensing rod 143, and the

insulators

141a, 142a, and 143a and the

bushings

141b, 142b, and 143b coupled to the outer surfaces thereof penetrate through

coupling holes

144a, 144b, and 144c formed in the coupling plate 144 to be coupled thereto.

The

insulators

141a, 142a, and 143a are insulating means for preventing sparks generated by current supply at the time of ignition, and the

bushings

141b, 142b, and 143b are configured to seal gaps between outer surfaces of the

insulators

141a, 142a, and 143a and the

coupling holes

144a, 144b, and 144 c.

Referring to fig. 4 and 5, an ignition bar assembly coupling portion 150 for assembling the ignition bar assembly 140 is provided at one side portion of the mixing chamber 100. The ignition bar assembly engaging portion 150 includes: a coupling plate seating part 151 configured in a groove shape to seat the coupling plate 144; a second sealing member seating part 152 formed at an inner side of the coupling plate seating part 151 to seat the second sealing member 180; the through hole 153 is penetrated by the first ignition rod 141, the second ignition rod 142, and the flame sensing rod 143. A plurality of fins 154 for radiating combustion heat are provided around the ignition bar assembly coupling portion 150.

Referring to fig. 6 to 8, a mixing chamber flange 120 and a burner flange 133 supporting and connecting an edge portion of a flat burner 130 are provided in contact with each other at one side portion of the mixing chamber 100 to seal the mixing space S, and the ignition rod assembly 140 is assembled through the mixing chamber flange 120 and the burner flange 133 at a position spaced apart from the mixing space S.

The sealing unit includes: a first sealing member 160 is provided at a portion where the mixing chamber flange 120 meets the burner flange 133, for preventing the mixture gas flowing into the mixing space S from leaking to the outside. The first sealing member 160 may be formed of a heat-resistant graphite material. An insulating material 170 for blocking heat transfer of combustion heat generated in the combustion chamber C is provided on the first sealing member 160.

And, the sealing unit includes: and a second sealing member 180 provided between an upper portion of one side portion of the mixing chamber 100 and the coupling plate 144 for preventing exhaust gas generated in the combustion chamber C from leaking to the outside. The second sealing member 180 may be formed using a rubber material. Further, a plurality of contact protrusions 181 formed to protrude outward may be formed on the outer side surface of the second sealing member 180 with a predetermined interval, and the contact protrusions 181 are brought into contact with the bottom surface of the coupling plate 144 and the upper surface of the second sealing member seating portion 152, thereby further improving sealing performance.

Further, as described above, the

bushings

141b, 142b, and 143b are coupled to the outer surfaces of the

insulators

141a, 142a, and 143a of the ignition bar assembly 140, so that leakage of the exhaust gas or the mixed gas through the

coupling holes

144a, 144b, and 144c of the coupling plate 144 can be blocked again.

Hereinafter, the configuration and operation of the cooling unit for blocking the transfer of combustion heat to the sealing unit and dissipating the heat will be described with reference to fig. 7 and 8.

The cooling unit is constructed to block heat transfer to a sealing unit, which may include an air-cooling type cooling unit and a water-cooling type cooling unit, wherein the sealing unit is used to prevent combustion heat generated in the combustion chamber C from leaking through a gap between the mixing chamber 100 and the ignition rod assembly 140

As described above, the mixing chamber flange 120 and the burner flange 133 are provided in contact with each other at one side of the mixing chamber 100 to seal the mixing space S, the ignition rod assembly 140 is assembled by penetrating the mixing chamber flange 120 and the burner flange 133, and the air-cooling type cooling unit may be configured to cool the mixing chamber flange 120 and the burner flange 133 by convection of the mixture gas flowing into the mixing space S.

In addition, the heat exchanger 200 may be configured as a smoke tube type heat exchanger, and may include: an outer tub 210; an upper tube plate 220 constituting a bottom plate surface of the combustion chamber C and an upper surface of the heat exchanger 200; a plurality of tubes 230 whose upper end portions penetrate and are coupled to tube insertion holes 221 formed in the upper tube plate 220, and through which combustion gas flows; and a water tank B for accommodating the heating medium in the outer cylinder 210 outside the pipe 230. The heating medium may be heating water or hot water for heating or for use as hot water.

In the water-cooled cooling unit, the upper tube plate flange 222 of the heat exchanger 200 disposed under the combustion chamber C, which is in contact with the heat medium, is disposed in contact with the burner flange 133, so that the burner flange 133 and the sealing member 190 can be cooled by conduction.

Further, as described above, a plurality of fins 154 are provided along the periphery of the ignition rod assembly 140 at one side portion of the mixing chamber 100 in which the ignition rod assembly 140 is assembled, and the fins 154 may also function as a cooling means.

As described above, according to the present invention, when the ignition rod assembly 140 is assembled by penetrating it to one side of the mixing chamber 100 in which the flat burner 130 is installed, the sealing means and the cooling means are provided, so that leakage of the mixture gas and the exhaust gas can be blocked, and the sealing means can be prevented from being thermally damaged by the heat of combustion. Further, it is possible to prevent a problem of pipe blockage due to a heat insulating material provided at one side of the lower end region of the conventional mixing chamber, and to minimize the use of the heat insulating material, since the heat insulating material 170 is used only at a portion of the lower end of the ignition rod assembly 140, the ignition rod assembly 140 can be safely assembled, and leakage of the mixture gas and the exhaust gas due to damage of the sealing unit can be prevented.

Referring to fig. 9 to 12, the flue tube boiler 1 according to an embodiment of the present invention further includes: the water leakage preventing member 500 is coupled to a connection portion between the heat exchanger 200 and the condensate receiver 300 to prevent leakage of the condensate.

Referring to fig. 9, the heat exchanger 200 includes: an outer cylinder 210 constituting an outer wall of a water tank B (see fig. 12) into and from which a heat medium flows and which accommodates the heat medium; a plurality of tubes 230 such that combustion gas generated in the mixing chamber 100 by the ignition of the burner flows along the inside of the plurality of tubes and exchanges heat with the heating medium; an upper tube plate 220 supporting the upper end portions of the tubes 230 and constituting an upper surface of the water tank B; a lower tube plate 240 supporting the lower end portions of the tubes 230 and constituting a floor surface of the water tank B; and a support plate 250 coupled to the pipe 230 at positions spaced apart up and down on an outer side surface of the pipe 230 to fix the position of the pipe 230 and to form a moving path of the heating medium.

Referring to fig. 10, the lower tube plate 240 is configured in an upper open shape to surround and combine the lower outer side of the outer tube 210, and includes: a horizontal part 241 having a plurality of pipe insertion holes 241a formed therethrough by the lower end of the pipe 230 to support the lower end of the pipe 230 and form a floor surface of the sink B; a vertical part 242 coupled to an outer surface of a lower end of the outer cylinder 210; and an arc part 243 connecting an outer end of the horizontal part 241 and a lower end of the vertical part 242, and formed in a shape of being convexly curved outward, thereby dispersing a water pressure of the heat medium received in the water tank B.

Referring to fig. 12, the vertical portion 242 of the lower tube plate 240 may be inserted into and coupled to an outer surface of a lower end portion of the cylinder 210, and a flange portion 244 extending outward by a predetermined length may be formed at an upper end of the vertical portion 242 of the lower tube plate 240, and the flange portion 244 may be welded to the outer surface of the outer cylinder 210.

The heat exchanger 200 is coupled in such a manner that the lower tube plate 240 surrounds the lower outer side surface of the outer tube 210, and an arc part 243 having a shape convexly curved toward the outside is formed at a corner connecting the horizontal part 241 and the vertical part 242 of the lower tube plate 240, so that the water pressure of the heating medium can be dispersed, and the water pressure resistance of the lower tube plate 240 can be improved, and the durability can be improved by minimizing the deformation of the lower tube plate 240.

The following describes a coupling structure of the heat exchanger 200, the condensate receiver 300, and the water leakage preventing member 500 configured as described above.

Referring to fig. 11 and 12, the water leakage preventing member 500 is interposed between an edge portion of the lower tube plate 240 and an edge portion of the condensate receiver 300 to prevent leakage of the condensate. The body 510 of the water leakage preventing part 500 is provided in a form of surrounding the lower portions of the arc-shaped part 243 and the vertical part 242 of the lower tube plate 240, so that the condensed water CW condensed at the horizontal part 241 of the lower tube plate 240 can be laterally blocked by the lower portion 530 of the body 510, thereby being blocked from moving in a lateral direction and falling downward.

The sidewall 310 of the condensate receiver 300 may be provided to be located near the boundary of the horizontal portion 241 and the arc-shaped portion 243 of the lower tube sheet 240, thereby guiding the dropping of the condensate.

As described above, since the inner end of the lower part 530 of the water leakage prevention member 500 and the side wall 310 of the condensate receiver 300 are located near the boundary between the horizontal part 241 and the arc-shaped part 243 of the lower tube plate 240, the condensate CW condensed on the bottom surface of the horizontal part 241 of the lower tube plate 240 can flow downward along the inner end of the lower part 530 of the water leakage prevention member 500 and the side wall 310 of the condensate receiver 300 even if it moves in the lateral direction, and is collected in the condensate receiver 300, thereby preventing the accumulation of the condensate CW and the corrosion of the lower tube plate 240 caused thereby.

In addition, a contact protrusion 520 protruding toward the outer surface of the lower tube plate 240 may be formed on the inner surface 510a of the water leakage preventing member 500. The contact protrusion 520 may be formed as a plurality of

contact protrusions

521, 522, 523, 524 at positions spaced apart vertically on the inner surface 510a of the water leakage preventing member 500.

According to the above-described structure of the close fitting projection 520, when water pressure is applied, the close fitting projection 520 of the water leakage prevention member 500 projecting in the direction opposite to the direction in which the water pressure is applied is closely fitted to the outer surface of the lower tube plate 240, and thus it is possible to effectively prevent the condensed water CW from penetrating into the gap between the lower tube plate 240 and the water leakage prevention member 500 and leaking. Further, when the contact protrusion 520 is formed in a plurality of positions spaced apart vertically, leakage of the condensed water CW can be prevented more reliably.

In addition, the condensed water receiver 300 is provided at an edge portion thereof with: the first flange 320 extends outward from the upper end of the sidewall 310 of the condensate receiver 300 to support the lower portion 530 of the water leakage preventing member 500. The lower portion 530 and the first flange portion 320 of the water leakage preventing member 500 are formed with fastening protrusions 321 and fastening grooves 531 fastened to corresponding positions, so that the position of the water leakage preventing member 500 can be fixed while blocking leakage of the condensed water CW.

Further, the condensed water receiver 300 includes, at an edge portion thereof: an extension part 330 extending upward from the outer end of the first flange part 320 and closely attached to the outer surface of the water leakage preventing member 500; and a second flange portion 340 extending outward from a distal end of the extension portion 330. An insertion protrusion 541 and an insertion groove 341 are formed at the upper part 540 and the second flange part 340 of the water leakage preventing member 500 to be inserted into corresponding positions, so that the position of the water leakage preventing member 500 can be fixed while blocking leakage of the condensed water CW.

As described above, in the flue-tube boiler 1 according to the embodiment of the present invention, the pressure resistance and durability can be improved by the coupling structure between the lower tube plate 240 and the outer tub 210 and the structure of the lower tube plate 240 including the arc-shaped portion 243, the accumulation of the condensed water CW can be prevented by the positional relationship with the water leakage preventing member 500 interposed between the edge portion of the lower tube plate 240 and the edge portion of the condensed water receiver 300, and the leakage of the condensed water CW can be effectively prevented by the structure of the close contact protrusion 520 formed on the water leakage preventing member 500.

The structure and operation of a flue-tube boiler 1' according to another embodiment of the present invention will be described below with reference to fig. 13 to 37.

The flue tube boiler 1' according to another embodiment of the present invention includes a mixing chamber 1000, a heat exchanger 2000 and a condensate receiver 3000. Wherein the mixing chamber 1000 is equipped with a mixing space S for mixing combustion gas with air, a mixing chamber body 1100 of a flat shape, and a flat plate-shaped burner 1300 arranged in a horizontal direction at an upper side of the combustion chamber C. The heat exchanger 2000 is provided with: an outer cylinder 2100 constituting an outer wall of a water tank B for allowing and discharging a heat medium and accommodating the heat medium; an upper pipe plate 2200 of a hard plate structure coupled to an inner side of the outer tube 2100 to form a heat medium flow path with the outer tube 2100 and to form the combustion chamber C; a plurality of tubes 2300 formed in a flat shape such that the combustion gas generated in the combustion chamber C flows along the inside of the plurality of tubes 2300 and exchanges heat with a heat medium flowing outside; turbulators 2400 and 2500 coupled to the inside of the pipe 2300 and guiding the flow of the combustion gas to generate turbulence; a plurality of stages of diaphragms 2610, 2620, and 2630 provided between the outer tube 2100 and the tube 2300 to guide the flow direction of the heating medium to be alternately changed to the inside and the outside in the radial direction; a lower tube plate 2700 of a rigid plate structure supports a lower end of the tube 2300 and forms a floor surface of the water tub B. The condensate receiver 3000 collects the condensate CW generated in the lower tube plate 2700 and guides the condensate to a condensate discharge port 3100 formed at one side, and guides the combustion gas passing through the tube 2300 to an exhaust pipe 4000 connected to an upper side of the condensate discharge port 3100 and provided at one side of the outer cylinder 2100.

Furthermore, the present invention includes: a premixing chamber 5000 for premixing combustion air and gas supplied to the mixing chamber 1000; the mixed gas adjusting unit 6000 opens and closes a flow path of the air and the gas passing through the premixing chamber 5000 to adjust a supply flow rate of the mixed gas.

Referring to fig. 13 to 19, the mixing chamber 1000 includes: a mixing chamber body 1100 protruding upward and configured in a flat shape; an ignition rod assembly 1400 which is assembled to penetrate one side portion of the mixing chamber body 1100 and extends to the lower side of the flat burner 1300 across the upper portion of the combustion chamber C; and sealing

units

1600, 1700, 1800 for blocking the mixture gas of the mixing space S and the exhaust gas of the combustion chamber C from leaking to the outside through a gap between the mixing chamber 1000 and the ignition bar assembly 1400.

The burner to which the present invention is applied is a flat plate type burner 1300 including: a flat plate-shaped flame hole plate 1310 formed with a plurality of flame holes 1310 a; and a metal fiber 1320 coupled to the flame hole plate 1310. The spaced mixing space S between the bottom surface of the mixing chamber body 1100 and the upper surface of the flat plate-shaped burner 1300 is formed in a flat disc shape, so that it can be formed to reduce the height of the mixing chamber 1000.

Further, unlike the conventional cylindrical burner, since the flat plate burner 1300 is provided over the entire region of the mixing space S, the gas and air flowing into the flat plate burner 1300 are supplied to the edge portion of the flat plate burner 1300, that is, the position close to the position where the

seal units

1600, 1700, 1800 are provided, and thus the air-cooled cooling of the

seal units

1600, 1700, 1800 is achieved by the gas and air, the combustion region is expanded to reduce the load per unit area, and the emission of pollutants such as CO and NOx can be reduced, thereby improving the combustion performance.

The ignition rod assembly 1400 assembled through one side of the mixing chamber 1000 may include an ignition rod 1410 and a flame sensing rod 1420, the ignition rod 1410 including a first ignition rod 1410-1 and a second ignition rod 1410-2.

Insulators

1410a and 1420a made of an insulating material are coupled to outer surfaces of the ignition rod 1410 and the flame sensing rod 1420, and

bushings

1410b and 1420b for maintaining airtightness are coupled to outer surfaces of the

insulators

1410a and 1420 a.

The ignition rod 1410, the insulator 1410a, and the bushing 1410b are fixed to an ignition rod coupling plate 1430, and the flame sensing rod 1420, the insulator 1420a, and the bushing 1420b are fixed to a flame sensing rod coupling plate 1440. The

insulators

1410a and 1420a are insulating means for preventing sparks from being generated due to energization at the time of ignition, and the

bushings

1410b and 1420b are configured to seal gaps between the outer side surfaces of the

insulators

1410a and 1420a and the ignition rod coupling plate 1430 and the flame sensing rod coupling plate 1440.

Referring to fig. 16, an ignition bar assembly coupling portion 1500 for assembling an ignition bar assembly 1400 is provided at one side portion of the mixing chamber 1000. The ignition bar assembly coupling portion 1500 includes: a second sealing member seating part 1510 configured in a groove shape to seat the ignition bar coupling plate 1430 and a second sealing member 1700 coupled to a lower side thereof; the third sealing member installation part 1520 is configured in a groove shape to install the flame sensing rod combination plate 1440 and the third sealing member 1800 combined to the lower side thereof. A plurality of fins 1530 for radiating combustion heat are provided around the ignition bar assembly coupling portion 1500.

Referring to fig. 17 to 19, a mixing chamber flange 1110 and a burner flange 1330 supporting and connecting an edge portion of a flat burner 1300 are provided in contact with one side portion of the mixing chamber main body 1100 to seal the mixing space S, and the ignition rod assembly 1400 is assembled through the mixing chamber flange 1110 and the burner flange 1330 at a position spaced apart from the mixing space S.

The sealing unit includes: a first sealing member 1600 provided at a portion where the mixing chamber flange 1110 meets the burner flange 1330 for preventing the mixture gas flowing into the mixing space S from leaking to the outside. The first sealing member 1600 may be formed using a heat-resistant graphite material.

And, the sealing unit includes: a second sealing member 1700 provided between the mixing chamber flange 1110 and the ignition bar combining plate 1430 for preventing exhaust gas generated in the combustion chamber C from leaking to the outside; a third sealing member 1800 provided between the mixing chamber flange 1110 and the flame sensing rod combining plate 1440 for preventing exhaust gas generated in the combustion chamber C from leaking to the outside. The second sealing member 1700 and the third sealing member 1800 may be formed of a rubber material, and the second sealing member 1700 and the third sealing member 1800 may be assembled by separate manufacturing of separate members, thereby minimizing deformation of the rubber material due to high temperature.

Furthermore, a plurality of sticking protrusions 1710 formed to protrude outward may be formed on the outer side surface of the second sealing member 1700 and the outer side surface of the third sealing member 1800 to be spaced apart from each other at predetermined intervals, and the sticking protrusions 1710 may be closely attached to the bottom surface of the ignition rod coupling plate 1430, the upper surface of the second sealing member 1700, the bottom surface of the flame sensing rod coupling plate 1440, and the upper surface of the third sealing member 1800, so that sealing performance may be further improved.

As described above, the

bushings

1410b and 1420b are coupled to the outer surfaces of the

insulators

1410a and 1420a of the ignition rod assembly 1400, so that the leakage of the exhaust gas and the mixed gas to the outside of the mixing chamber 1000 can be blocked again.

Hereinafter, the configuration and operation of the cooling unit for blocking the transfer of combustion heat to the sealing unit and dissipating the heat will be described with reference to fig. 18 and 19.

The cooling unit is configured to block heat transfer to a sealing unit, and may include an air-cooling type cooling unit and a water-cooling type cooling unit, wherein the sealing unit is configured to prevent combustion heat generated in the combustion chamber C from leaking through a gap between the mixing chamber 1000 and the ignition bar assembly 1400.

As described above, the mixing chamber flange 1110 and the burner flange 1330 are provided in one side portion of the mixing chamber 1000 so as to be in contact with each other, the mixing space S is sealed, the ignition rod assembly 1400 is assembled by penetrating the mixing chamber flange 1110 and the burner flange 1330, and the air-cooling type cooling unit may be configured to cool the mixing chamber flange 1110 and the burner flange 1330 by convection of the mixture gas flowing into the mixing space S.

In addition, the heat exchanger 2000 may be configured as a smoke tube type heat exchanger, and may include: an outer barrel 2100; an upper tube plate 2200 constituting a bottom plate surface of the combustion chamber C and an upper surface of the heat exchanger 2000; a plurality of tubes 2300 having upper ends penetrating and coupled to tube insertion ports 2210a formed in the upper tube plate 2200, and through which the combustion gas flows through the insides of the plurality of tubes 2300; and a water tank B for accommodating a heat medium in the outer tube 2100 outside the tube 2300. The heating medium may be heating water or hot water for heating or for use as hot water.

In the water-cooled cooling unit, the upper tube plate flange 2230 of the heat exchanger 2000 disposed under the combustion chamber C, which is in contact with the heat medium, is disposed in surface contact with the burner flange 1330, so that the burner flange 1330 and the sealing

members

1600, 1700, 1800 can be configured to be cooled by a conduction method of the heat medium stored in the water tank B.

Further, as described above, a plurality of heat radiation fins 1530 are provided along the periphery of the ignition bar assembly 1400 at one side portion of the mixing chamber main body 1100 to which the ignition bar assembly 1400 is assembled, and the heat radiation fins 1530 may function as a cooling means.

As described above, according to the present invention, by providing the mixing chamber 1000 to include the mixing chamber body 1100 having a flat shape and the flat plate-shaped burner 1300, the height of the mixing chamber 1000 can be greatly reduced compared to the conventional structure provided with the cylindrical burner.

Further, when the ignition rod assembly 1400 is assembled by penetrating it to one side of the mixing chamber main body 1100 provided with the flat burner 1300, the sealing means and the cooling means are provided, so that leakage of the mixture gas and the exhaust gas can be blocked, and the sealing means can be prevented from being thermally damaged by the heat of combustion. Therefore, the ignition bar assembly 1400 can be safely assembled without using a heat insulating material in the mixing chamber 1000 equipped with the flat burner 1300, and the heat damage of the sealing unit can be prevented, so that the leakage of the mixed gas and the exhaust gas can be blocked.

In addition, referring to fig. 20, the upper tube plate 2200 includes: a bottom plate 2210 forming a bottom surface of the combustion chamber C; a side wall portion 2220 forming a side wall of the combustion chamber C; an upper tube sheet flange 2230 in which the burner flange 1330 is seated; an arcuate portion 2240 connecting an upper end of the side wall portion 2220 and an inboard end of the upper tube panel flange 2230; an arc 2250 connecting an outer end of the bottom plate 2210 with a lower end of the side wall portion 2220.

As described above, the upper pipe plate 2200 includes the

arc parts

2240 and 2250, so that the water pressure of the heating medium stored in the water tank B can be dispersed, thereby improving the durability of the upper pipe plate 2200. The ratio of the difference in diameter between the outer diameter d1 of the upper tube sheet flange 2230 and the inner diameter d2 of the lower end of the arcuate portion 2240 to the outer diameter d1 of the upper tube sheet flange 2230 is preferably 20% or less. In the case of the configuration of the diameter difference ratio as described above, the flow rate and temperature of the water contained in the water tank B can be uniformly controlled.

And, a height h between the bottom surface of the flat burner 1300 inserted into the upper tube plate 2200 and the bottom plate surface of the upper tube plate 2200 is set such that the end of the flame generated at the flat burner 1300 is spaced apart from the bottom plate surface of the upper tube plate 2200 by a predetermined distance, and the height h is preferably set to a size of about 80mm when considering the length of the flame of the flat burner 1300. The reason why the tip end of the flame is spaced apart from the bottom plate surface of the upper tube plate 2200 by the predetermined distance as described above is that a predetermined space needs to be secured between the tip end of the flame generated by the flat burner 1300 and the bottom plate surface of the upper tube plate 2200 to ensure conditions for experimentally minimizing nitrogen oxides (NOx) and carbon monoxide (CO).

In addition, by designing the height h of the upper tube plate 2200 to be low as described above, the height of the combustion chamber C is lowered, and the overall height of the flue-tube boiler 1' can be reduced. That is, in the case of applying the conventional cylindrical burner, the height between the bottom surface of the burner and the bottom plate surface of the upper tube plate is about 190mm, but in the present invention, the height can be reduced to about 80mm, and thus, the height can be reduced by about 40% compared to the conventional art.

In the present embodiment, the ignition bar assembly 1400 is formed at a position close to the mixed gas inflow port 1200 connected to the blower 7000 that supplies the mixed gas to the mixing chamber 1000. In this case, an operator can easily approach the ignition bar assembly 1400 through the mixed gas inflow port 1200, thereby improving convenience of maintenance.

As another example, as shown in fig. 2, the ignition rod assembly 1400 may be provided on the side opposite to the mixed gas inlet 1200. In this case, since the mixed gas supplied from the blower 7000 is directly supplied to the ignition rod assembly 1400, there is an effect that the delay of ignition can be prevented.

Referring to fig. 21 to 26, the heat exchanger 2000 includes: an outer cylinder 2100 formed with a heat medium inlet 2110 and a heat medium outlet 2120 for allowing a heat medium to flow in and discharge; an upper pipe plate 2200 coupled to the inside of the outer cylinder 2100 to form a flow path of a heating medium with the outer cylinder 2100, and on which the flat burner 1300 is mounted to form a combustion chamber C; a pipe assembly 10000 including a plurality of pipes 2300 and turbulators 2400 and 2500, wherein the plurality of pipes 2300 are formed in a flat shape such that the combustion gas generated in the combustion chamber C flows along the inside of the plurality of pipes 2300 and exchanges heat with the heating medium, and the turbulators 2400 and 2500 are coupled to the inside of the pipes 2300 and induce turbulence in the flow of the combustion gas; and a lower tube plate 2700 supporting the tube assembly 10000 and coupled to the condensate water receiver 3000.

A plurality of stages of

diaphragms

2610, 2620, and 2630 are provided on the outer surface of the pipe 2300 so as to be spaced apart in the vertical direction, and guide the flow direction of the heat medium so that the flow direction of the heat medium is alternately changed between the inside and the outside in the radial direction, and the plurality of stages of

diaphragms

2610, 2620, and 2630 are fixedly supported by a support base 2640. The plurality of tubes 2300 are arranged in a vertical direction such that combustion gas generated in the combustion chamber C flows downward, and are spaced apart in a circumferential direction and arranged in a radial shape.

In the present embodiment, the multi-stage diaphragms include a plate-shaped upper diaphragm 2610, an intermediate diaphragm 2620, and a lower diaphragm 2630. Referring to fig. 24 (a), the upper diaphragm 2610 has a pipe insertion port 2610a for inserting the pipe 2300 and an opening 2610b at the center for passing a heating medium. Referring to fig. 24 (b), the middle portion diaphragm 2620 is formed such that the tube insertion port 2620a is spaced apart from the outer side surface of the tube 2300, and the heating medium flows through the space formed between the tube insertion port 2620a and the tube 2300. The central portion 2620b of the intermediate portion diaphragm 2620 is configured to be closed. In one embodiment, the tube insertion port 2620a may be configured such that two tubes 2300 are inserted while being spaced apart from each other. Referring to fig. 24 (c), the lower diaphragm 2630 has a tube insertion port 2630a having the same structure as the upper diaphragm 2610, and has an opening 2630b at the center.

According to the structure of the

multi-stage diaphragms

2610, 2620, and 2630 as described above, as shown by arrows in fig. 25 and 26, the heat medium flowing into the inner portion of the outer cylinder 2100 through the heat medium inlet 2110 flows radially inward toward the opening 2630b formed in the central portion of the lower diaphragm 2630, and then the heat medium flowing upward through the lower diaphragm 2630 through the opening 2630b is dispersed into the space between the pipe insertion ports 2620a radially formed in the intermediate diaphragm 2620 and flows radially outward, and then the heat medium flowing upward through the pipe insertion ports 2620a toward the opening 2610b formed in the central portion of the upper diaphragm 2610 flows radially inward, and then the heat medium is discharged from the heat medium discharge port 2120 formed in the upper portion of the outer cylinder 2100 through the opening 2610 b.

As described above, since the flow direction of the heat medium is alternately changed to the inner side and the outer side in the radial direction, the flow distance of the heat medium is increased, and the heat exchange efficiency of the heat exchanger 2000 can be improved, and the heat exchange performance can be obtained with high efficiency even if the height is reduced compared to the conventional heat exchanger, thereby having an effect of reducing the height of the heat exchanger 2000. And, the flow velocity of the heating medium is increased, so that the boiling phenomenon caused by local overheating which may be caused when the heating medium stagnates can be prevented.

Hereinafter, the structure and operation of the tube assembly 10000 will be described with reference to fig. 27 to 33.

The tube assembly 10000 according to an embodiment of the present invention includes: a pipe 2300 formed in a flat shape so that the combustion gas generated in the combustion chamber C flows along the inside of the pipe 2300 and exchanges heat with a heat medium flowing outside; an upper turbulator 2400 bonded to an upper inner side of the pipe 2300 near the combustion chamber so as to be in surface contact with the pipe 2300, thereby improving heat conductivity and inducing turbulence in the combustion gas flow; and a lower turbulator 2500 coupled to the inside of the pipe 2300 at a lower side of the upper turbulator 2400, and guiding the generation of turbulence in the flow of the combustion gas.

The upper turbulator 2400 includes: tube-contacting surface 2410: 2410a, 2410b tightly attached to the inner surface of the tube 2300; pressure supporter 2420: 2420a, 2420b, at the tube contacting surface 2410: 2410a, 2410b cut part 2430: 2430a and 2430b are formed by bending.

Of the pipe contact surfaces 2410, a first pipe contact surface 2410a which is in close contact with the inner surface of one side portion of the pipe 2300 and a second pipe contact surface 2410b which is in close contact with the inner surface of the other side portion of the pipe 2300 are configured to be symmetrical.

The pressure support part 2420 is configured to prevent deformation and damage of the pipe 2300 due to the water pressure of the heating medium, and includes: a first pressure supporter 2420a formed by bending a portion of the first cut-out portion 2430a of the first pipe contact surface 2410a and protruding toward the second pipe contact surface 2410 b; the second pressure supporter 2420b is formed by bending a portion of the second cut 2430b of the second pipe contact surface 2410b to protrude toward the first pipe contact surface 2410 a.

The first cut-out portion 2430a has a larger cut-out area than the second cut-out portion 2430b, the protruding end of the first pressure supporter 2420a contacts the second pipe contact surface 2410b, and when the pressure supporter 2420 is inserted into the pipe 2300, the protruding end of the second pressure supporter 2420b penetrates the first cut-out portion 2430a and contacts the inner surface of the pipe 2300.

According to such a configuration, when water pressure is applied, the first pressure support part 2420a supports the first and second

pipe contact surfaces

2410a and 2410b to firmly hold the pipe, and the second pressure support part 2420b further firmly supports the pipe 2300 supported by the first and second

pipe contact surfaces

2410a and 2410 b.

As shown in fig. 33, the first and second

pressure support parts

2420a and 2420b are provided in plurality at intervals in the front-rear direction and the up-down direction, the first pressure support part 2420a 'located on the upper side and the first pressure support part 2420a ″ located on the lower side are provided at positions not overlapping in the up-down direction, and the second pressure support part 2420b' located on the upper side and the second pressure support part 2420b ″ located on the lower side are also provided at positions not overlapping in the up-down direction. According to such a configuration, the first and second

pressure support parts

2420a and 2420b provided in a zigzag form in the front-rear and vertical directions over the entire area of the upper turbulator 2400 can uniformly distribute the water pressure acting on the tube 2300, thereby effectively preventing deformation and breakage of the tube 2300.

Also, the first and

second pressure supporter

2420a and 2420b are formed in a plate shape, and are formed in a structure in which both side surfaces having a wide area are arranged in parallel to the flow direction of the combustion gas, so that, when the combustion gas flows, the flow resistance in the process in which the combustion gas passes through the first and

second pressure supporter

2420a and 2420b can be minimized, as shown by arrows in fig. 32 (a).

Referring to fig. 29, the lower turbulator 2500 may include: plane portions 2510 which divide an inner space of the tube 2300 into two sides and are arranged in a longitudinal direction of the tube 2300; the first guide piece 2520 and the second guide piece 2530 are formed to protrude at intervals in the longitudinal direction on both side surfaces of the planar portion 2510 and to be alternately inclined.

The first guide piece 2520 is arranged obliquely along one side at one side surface of the planar portion 2510, and the second guide piece 2530 is arranged obliquely along the other side at the other side surface of the planar portion 2510. Therefore, the heat medium flowing into the first guide 2520 and the second guide 2530 is sequentially transferred to the second guide 2530 and the first guide 2520 disposed adjacent to opposite side surfaces of the planar portion 2510, respectively, and alternately flows in both side spaces of the planar portion 2510.

The heat medium inflow end of the first guide 2520 is connected to one end of the planar portion 2510 by a first connection piece 2520a, and a first flow port 2520b capable of flowing a fluid to both side spaces of the planar portion 2510 is provided between the one end of the planar portion 2510 and the first connection piece 2520a and the first guide 2520.

The heat medium inflow end of the second guide piece 2530 is connected to the other side end of the planar portion 2510 by a second connection piece 2530a, and a second circulation port 2530b capable of circulating fluid to both side spaces of the planar portion 2510 is provided between the other side end of the planar portion 2510 and the second connection piece 2530a and the second guide piece 2530.

The first guide piece 2520 and the second guide piece 2530 may be configured as follows: a part of the planar portion 2510 is cut and bent toward both sides of the planar portion 2510, and fluid can flow into spaces on both sides of the planar portion 2510 through the cut portion of the planar portion 2510. Support tables 2540, which protrude outward and are connected to the opposite inner surfaces of the pipe 2300, are formed on both side surfaces of the lower turbulator 2500: 2540a, 2540 b. Further, at the upper end and the lower end of the lower turbulator 2500, there are formed: the first and

second support portions

2550 and 2560 are disposed to protrude forward and backward so as to be in contact with both side surfaces of the pipe 2300 and to be spaced apart from each other in the vertical direction.

In addition, referring to fig. 34 to 37, the flue-tube boiler 1' includes: a condensed water receiver 3000 for collecting condensed water generated by condensing water vapor contained in the combustion gas by the heat exchanger 2000 and discharging the condensed water; and a water leakage preventing member 3200 coupled to a connection portion between the lower tube plate 2700 and the condensate receiver 3000 of the heat exchanger 2000, for preventing leakage of the condensate.

Referring to fig. 22 together, the lower tube sheet 2700 is constructed in a hard sheet structure and includes: a horizontal part 2710 in which a plurality of pipe insertion holes 2710a penetrating through the lower end of the pipe 2300 are formed to support the lower end of the pipe 2300 and to constitute a floor surface of the water tub B; a vertical portion 2720 coupled to a lower end portion of the outer tube 2100; an arc portion 2730 connecting an outer end of the horizontal portion 2710 and a lower end of the vertical portion 2720, and configured to be convexly curved outward, thereby dispersing the water pressure of the heating medium.

As described above, the arc 2730 having a shape convexly curved to the outside is formed at the corner connecting the horizontal part 2710 and the vertical part 2720 of the lower duct plate 2700, so that the water pressure of the heating medium can be dispersed, and the water pressure resistance of the lower duct plate 2700 can be improved, and thus the durability can be improved by minimizing the deformation of the lower duct plate 2700.

Hereinafter, a coupling structure of the condensate receiver 3000 and the water leakage preventing member 3200 will be described.

Referring to fig. 36 and 37, the water leakage preventing member 3200 is interposed between an edge portion of the lower tube plate 2700 and an edge portion of the condensate receiver 3000 to prevent leakage of the condensate. The main body 3210 of the leakage preventing member 3200 is provided in a form of surrounding the lower portions of the curved portion 2730 and the vertical portion 2720 of the lower tube plate 2700, so that the condensed water CW condensed in the horizontal portion 2710 of the lower tube plate 2700 can be laterally blocked by the bottom plate portion 3230 formed to extend from the lower portion of the main body 3210 to one side, and thus, the movement in the lateral direction is blocked and the condensed water is dropped downward.

In addition, an abutting protrusion 3220 protruding in a direction toward the outer side surface of the lower tube plate 2700 may be formed on the inner side surface 3210a of the water leakage preventive member 3200. The contact protrusion 3220 may be formed in a plurality of

contact protrusions

3220a, 3220b, 3220c, 3220d, 3220e, and 3220f at positions spaced apart from each other in the up-down direction on the inner surface 3210a of the water leakage preventing member 3200.

According to the above-described structure of the contact protrusion 3220, when water pressure is applied, the contact protrusion 3220 of the water leakage prevention member 3200 protruding in the direction opposite to the direction in which the water pressure is applied is brought into contact with the outer side surface of the lower tube plate 2700, and thus the phenomenon in which the condensed water CW penetrates through the gap between the lower tube plate 2700 and the water leakage prevention member 3200 to leak water can be effectively prevented. Further, when the contact protrusion 3220 is formed in a plurality of positions spaced apart vertically, leakage of the condensed water CW can be prevented more reliably.

A first flange portion 3010 for supporting the water leakage preventing member 3200 is provided at an edge portion of the condensate receiver 3000, and a fastening protrusion 3010a and a fastening groove 3230a fastened to corresponding positions are formed at the water leakage preventing member 3200 and the first flange portion 3010. Further, the condensed water receiver 3000 includes, at an edge portion thereof: an extension portion 3020 extending upward from an outer end of the first flange portion 3010 and closely attached to an outer surface of the water leakage preventive member 3200; and a second flange portion 3030 extending outward from the distal end of the extension portion 3020. An insertion protrusion 3240a and an insertion groove 3240b are formed at an upper portion of the water leakage preventive member 3200 and the second flange portion 3030 to be inserted into corresponding positions. According to the above configuration, leakage of the condensed water CW can be blocked, and the position of the water leakage preventing member 3200 can be firmly fixed.

In addition, referring to fig. 35, a vent guide 3300 is provided inside the condensed water receiver 3000, and the vent guide 3300 is formed with a plurality of punched holes 3310: 3310a, 3310b so that the combustion gas passing through the heat exchanger 2000 is uniformly distributed over the entire area of the condensed water receiver 3000 to be discharged. The size of the punched holes 3310 may be formed in different sizes from each other in consideration of the flow direction of the combustion gas.

A stepped portion 3040 is formed on the bottom surface of the condensate receiver 3000, and the stepped portion 3040 guides the flow of the combustion gas passing through the exhaust guide 3300 toward the condensate outlet port 3100 formed at the lower portion of the condensate receiver 3000 side, so that the condensate is discharged in the same direction as the flow of the combustion gas inside the condensate receiver 3000 as shown by a dotted arrow showing a direction of discharging the condensate and a solid arrow showing a direction of flowing the combustion gas in fig. 37. According to such a configuration, the condensed water is guided in the direction in which the exhaust gas flows, so that the lower tube plate 2700 can be prevented from being corroded due to the accumulation phenomenon of the condensed water, and the condensed water can be guided to the side of the condensed water discharge port 3100 to be smoothly discharged.

As described above, the present invention is not limited to the above-described embodiments, and a person having basic knowledge in the technical field to which the present invention belongs can realize obviously modified embodiments, which fall within the scope of the present invention, without departing from the technical idea of the present invention claimed in the claims.

Claims

1. A flue tube boiler, comprising:

a mixing chamber disposed on the upper side of the combustion chamber, and including a mixing space for mixing combustion gas and air, and a flat burner provided so as to span the entire area of the mixing space;

an ignition rod assembly which is assembled by penetrating one side portion of the mixing chamber from one side of the flat burner and extends to the lower side of the flat burner across the upper portion of the combustion chamber;

a sealing unit for blocking the mixed gas of the mixing space and the exhaust gas of the combustion chamber from leaking to the outside through a gap between the mixing chamber and the ignition bar assembly; and

a cooling unit for blocking heat transfer of combustion heat generated in the combustion chamber to the sealing unit.

2. The smoke tube boiler of claim 1,

a mixing chamber flange and a burner flange are provided in a side portion of the mixing chamber so as to be connected to each other, thereby sealing the mixing space,

the ignition rod assembly is assembled by passing through the mixing chamber flange and the burner flange at a position spaced apart from the mixing space.

3. The smoke tube boiler of claim 2,

the sealing unit includes: and a first sealing member provided at a portion where the mixing chamber flange meets the burner flange, for preventing leakage of the mixed gas.

4. The smoke tube boiler of claim 3,

the first sealing member is provided at an upper portion thereof with a heat insulating material for blocking heat transfer of combustion heat generated in the combustion chamber.

5. The smoke tube boiler of claim 3,

a coupling plate for penetrating and coupling the ignition bar assembly is provided at an upper portion of one side portion of the mixing chamber,

the sealing unit includes: a second sealing member provided between an upper portion of one side portion of the mixing chamber and the coupling plate, for preventing leakage of the exhaust gas.

6. The smoke tube boiler of claim 5,

the second seal member has an outer surface on which a plurality of contact protrusions protruding outward are formed with predetermined intervals.

7. The smoke tube boiler of claim 1 or 3,

the ignition rod assembly comprises an ignition rod and a flame sensing rod,

an ignition rod combining plate for penetrating and combining the ignition rod and a flame sensing rod combining plate for penetrating and combining the flame sensing rod are arranged at the upper part of one side part of the mixing chamber,

the sealing units are provided between an upper portion of one side portion of the mixing chamber and the ignition rod coupling plate, and between an upper portion of one side portion of the mixing chamber and the flame sensing rod coupling plate.

8. The smoke tube boiler of claim 1,

the cooling unit comprises an air-cooled cooling unit and a water-cooled cooling unit.

9. The smoke tube boiler of claim 8,

the ignition rod assembly is assembled by penetrating the mixing chamber flange and the burner flange,

the air-cooled cooling unit cools the mixing chamber flange and the burner flange by the mixed gas flowing into the mixing space.

10. The smoke tube boiler of claim 8,

in the water-cooled cooling unit, an upper tube plate flange of the heat exchanger disposed at a lower side of the combustion chamber, which is in contact with the heat medium, is disposed in contact with the burner flange, thereby cooling the burner flange.

11. The smoke tube boiler of claim 1,

a plurality of cooling fins are arranged along the periphery of the ignition rod assembly at one side part of the mixing chamber assembled with the ignition rod assembly.

12. The flue tube boiler of claim 1, comprising:

an outer cylinder which is arranged on the periphery of a pipe for allowing combustion gas to pass through, and forms the outer wall of a water tank for accommodating a heating medium on the outer side of the pipe;

the lower pipe plate of the hard plate structure comprises a horizontal part, a vertical part and an arc-shaped part, wherein the horizontal part supports the lower end part of the pipe and forms the bottom plate surface of the water tank, the vertical part is combined with the outer side surface of the lower end part of the outer cylinder, and the arc-shaped part is connected with the outer side end of the horizontal part and the lower end part of the vertical part and forms a shape which is convexly bent towards the outer side, so that the water pressure of the heat medium is dispersed.

13. The smoke tube boiler of claim 12,

the vertical part of the lower tube plate is inserted into and combined with the outer side surface of the lower end part of the outer cylinder.

14. The smoke tube boiler of claim 12,

a flange part extending outwards for a predetermined length is formed at the upper end of the vertical part of the lower tube plate,

the flange portion is welded to the outer surface of the outer cylinder.

15. The flue-tube boiler of claim 12, comprising:

a condensed water receiver provided at a lower side of the lower tube plate to collect condensed water generated at the lower tube plate; and

and the water leakage prevention part is clamped between the edge part of the lower tube plate and the edge part of the condensed water receiver and is used for preventing the leakage of the condensed water.

16. The smoke tube boiler of claim 15,

the water leakage preventing part is provided in a form of surrounding the lower portions of the arc-shaped part and the vertical part of the lower tube plate,

the condensed water condensed at the horizontal portion of the lower tube sheet is laterally blocked by the water leakage preventing member, so that the movement in the lateral direction is blocked and drops to the lower side.

17. The hookah boiler of claim 16,

the sidewall of the condensed water receiver is provided to be located near an interface of the horizontal portion and the arc portion of the lower tube sheet, thereby guiding the falling of the condensed water.

18. The smoke tube boiler of claim 15,

and the inner side surface of the water leakage preventing part is provided with a clinging bulge which protrudes towards the outer side surface of the lower tube plate.

19. The smoke tube boiler of claim 18,

the plurality of the clinging bulges are formed at the positions which are vertically separated on the inner side surface of the water leakage preventing part.

20. The smoke tube boiler of claim 18,

the condensed water receiver is provided with: a first flange portion extending outward from an upper end of a sidewall of the condensate receiver to support a lower portion of the water leakage preventing member,

the leakage preventing member and the first flange are formed with a fastening projection and a fastening groove which are fastened to corresponding positions with each other.

21. The smoke tube boiler of claim 20,

the edge part of the condensed water receiver further comprises: an extension part extending from the outer end of the first flange part to the upper side and closely attached to the outer side surface of the water leakage preventing part; and a second flange portion extending outward from a distal end of the extension portion,

an insertion protrusion and an insertion groove are formed at the upper portion of the water leakage preventing member and the second flange portion to be inserted into corresponding positions, thereby blocking leakage of condensed water and fixing the position of the water leakage preventing member.

22. The smoke tube boiler of claim 15,

an exhaust guide formed with a plurality of punched holes is provided inside the condensate water receiver to discharge combustion gas passing through a heat exchanger provided at a lower side of the combustion chamber uniformly distributed over an entire area of the condensate water receiver.

23. The smoke tube boiler of claim 22,

a stepped portion is formed on a bottom surface of the condensate receiver, and the stepped portion guides the flow of the combustion gas passing through the exhaust guide to a condensate water discharge side, so that the condensate water is discharged in the same direction as the flow of the combustion gas inside the condensate receiver.

24. The smoke tube boiler of claim 1,

the mixing chamber includes a mixing chamber body having a flat shape and the flat plate-shaped burner disposed at an upper side of the combustion chamber in a horizontal direction.

25. The smoke tube boiler of claim 24,

a space between the bottom surface of the mixing chamber body and the upper surface of the flat burner, which is spaced apart, is formed in a flat disc shape.

26. The flue tube boiler of claim 1, further comprising:

a heat exchanger for exchanging heat between the combustion heat of the combustion chamber and a heat medium,

the heat exchanger includes: an outer cylinder forming an outer wall of a water tank for allowing and discharging a heat medium and accommodating the heat medium; an upper tube plate of a hard plate structure coupled to an inner side of the outer tube to form a heat medium flow path between the upper tube plate and the outer tube and to form the combustion chamber; a plurality of tubes configured in a flat shape for allowing the combustion gas generated in the combustion chamber to flow along the inside of the plurality of tubes and to exchange heat with a heat medium flowing outside; a turbulator coupled to an inside of the tube to guide generation of turbulent flow in a flow of the combustion gas; a multi-stage diaphragm disposed between the outer cylinder and the pipe to guide the flow direction of the heating medium to be alternately changed to the inner side and the outer side in the radial direction; and a lower pipe plate of a hard plate structure supporting a lower end portion of the pipe and constituting a bottom surface of the water tank.

27. The smoke tube boiler of claim 26,

the flange of the upper tube plate is formed by protruding outwards at the upper end of the arc-shaped part,

a ratio of a diameter difference between an outer diameter of the flange of the upper tube sheet and an inner diameter of a lower end of the arc portion to the outer diameter of the flange of the upper tube sheet is 20% or less.

28. The smoke tube boiler of claim 26,

the height between the bottom surface of the flat plate-shaped burner inserted into the upper tube sheet and the bottom plate surface of the upper tube sheet is set such that the end of the flame generated at the flat plate-shaped burner is spaced a predetermined distance from the bottom plate surface of the upper tube sheet.

29. The smoke tube boiler of claim 26,

the turbulator includes: an upper turbulator bonded to an upper inner side of the tube near the combustion chamber in surface contact with the tube, thereby improving heat conductivity and guiding generation of turbulence in a flow of the combustion gas; and

a lower turbulator coupled to an inner side of the pipe at a lower side of the upper turbulator, thereby inducing turbulence in a flow of the combustion gas.