JPH10111087A - Indirect hot air generator - Google Patents

Abstract

(57) [Summary] [PROBLEMS] To provide an indirect hot air generator that is small in size and has high efficiency of recovery of thermal energy. SOLUTION: A furnace body 10 and a combustion chamber 2 provided therein.
1 and a plate fin heat exchanger 3 provided in the combustion chamber 21
And a regenerative burner 41 having a regenerator and a combustor for injecting a flame 40 into the combustion chamber 21.
The plate fin heat exchanger 3 has a heated gas passage 31 through which the heated gas 81 passes and a flue gas passage through which the flue gas 82 passes, and both are arranged without conducting each other.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

TECHNICAL FIELD The present invention relates to an indirect hot air generator that can be used as a heat source for a drying oven or the like.

[0002]

2. Description of the Related Art Conventionally, the following apparatus is known as an indirect hot air generator for burning a gas to be heated by using a combustion exhaust gas generated by burning a gas burner in a combustion chamber and obtaining hot air.

As shown in FIGS. 13 and 14, the indirect hot air generator 9 includes a furnace body 90 and a combustion chamber 92 provided therein.
And a gas burner 94 for injecting the flame 40 into the combustion chamber 92. A heated gas chamber 112 is provided between the furnace body 90 and the combustion chamber 92, and a plate fin heat exchanger 93 is provided in the heated gas chamber 112. The heated gas chamber 112 is provided with a blower 91 via a heated gas inlet 111. Then, air as the heated gas 81 is sent into the heated gas chamber 112 by the blower 91.

As shown in FIGS. 13 and 14, the plate fin heat exchanger 93 includes a heated gas passage 31 through which a heated gas 81 passes, and a flue gas passage 3 through which a flue gas 82 passes.
2 are arranged without conducting each other. The heated gas passage 31 opens to the heated gas chamber 112, and the combustion exhaust gas passage 32 opens to the combustion chamber 92. The heated gas passage 31 is open to a hot air outlet 114 via a hood 113, while the combustion exhaust gas passage 32 is open to a waste cylinder 99.

In the indirect hot air generator 9, hot air 81
0 occurs as shown below. As shown in FIG.
The gas burner 94 burns in the combustion chamber 92.
The flue gas 82 generated thereby rises inside the combustion chamber 92 and is introduced into the flue gas passage 32 of the plate fin heat exchanger 93. On the other hand, the blower 9
1 through the heated gas introduction port 111
Is introduced into the heated gas chamber 112. Thereafter, the heated gas 81 is introduced into the heated gas passage 31 in the plate fin heat exchanger 93.

As a result, heat is exchanged between the adjacent heated gas passage 31 and the combustion exhaust gas passage 32,
The heated gas 81 becomes hot air 810 and the hood 113
Through the hot air discharge port 114 to the outside of the furnace body 90. On the other hand, the heated gas 81 is deprived of the retained heat and becomes a waste gas 820, and is discarded from the waste cylinder 99 to the outside of the furnace body 90. Thus, hot air 810 can be obtained.

[0007]

However, the indirect hot air generator 9 has the following problems. As shown in FIGS. 13 and 14, the temperature of the tip of the flame 40 generated in the gas burner 94 becomes close to 2000 ° C. For this reason, in the said indirect hot-air generator 9, the plate fin heat exchanger 93 cannot be provided directly with respect to the combustion chamber 92, but the said plate fin heat exchanger 93 is always provided in a place different from the combustion chamber 92. Needed. Therefore, the indirect hot air generator 9 is a large-sized device.

Further, as shown in FIGS. 13 and 14, the flue gas 82 is supplied to the plate fin heat exchanger 93 by the
The gas is introduced by a combustion air blower (not shown) attached to the gas burner 94. Generally, the wind power is small, and the flow velocity of the combustion exhaust gas 82 in the combustion exhaust gas passage 32 is small like natural convection. Therefore, the overall heat transfer coefficient in the plate fin heat exchanger 93 is small, and the plate fin heat exchanger 93 on the inlet side of the combustion exhaust gas 82 is provided.
Of the plate fin heat exchanger 9
A temperature gradient is generated inside 3 and the entire heat transfer area is not used effectively. Therefore, the efficiency of heat energy recovery was low.

Furthermore, in the indirect hot air generator 9, the efficiency of heat energy recovery can be improved, but in this case, a larger plate fin heat exchanger 93 must be used. This method is not preferable because the size of the indirect hot air generator 9 is further increased.

The present invention has been made in view of the above-mentioned problems, and an object thereof is to provide an indirect hot air generator which is small in size and has a high efficiency of recovering thermal energy.

[0011]

According to the first aspect of the present invention, there is provided a furnace body, a combustion chamber provided therein, a plate fin heat exchanger provided in the combustion chamber, and a combustion chamber for injecting a flame into the combustion chamber. The plate fin heat exchanger has a heated gas passage through which the gas to be heated is passed, and a flue gas passage through which the flue gas is passed. The indirect hot air generator is characterized in that both are arranged without conducting each other.

The regenerative burner burns in a combustor to generate a flame, introduces flue gas generated by the combustion in the combustor into a regenerator, and recovers heat held by the flue gas. It is a burner with a configuration. Note that as the heat storage body, a ceramic honeycomb, a granular body, or the like can be used.

The operation of the present invention will be described below. In the indirect hot air generator of the present invention, a regenerative burner is used as a burner for blowing out a flame into the combustion chamber. The flame formed by the regenerative burner does not have a local high-temperature portion. Therefore, in the indirect hot air generator according to the present invention, the plate fin heat exchanger can be arranged in the combustion chamber to directly take in the combustion exhaust gas. For this reason, the size of the indirect hot air generator can be reduced.

When the regenerative burner burns, combustion exhaust gas is generated from the combustor in the combustion state, and the combustion exhaust gas flows into the heat storage body in the heat storage state. Therefore, there is always a forced convection of the combustion exhaust gas due to a large wind force between the two. In the present invention, since the flue gas in such a state is introduced into the heat exchanger, the flow velocity thereof is increased, so that the overall heat transfer coefficient in the plate fin heat exchanger can be increased. Further, since the flow direction of the combustion exhaust gas is periodically inverted with respect to the heat exchanger, the entire heat exchanger is heated, and the temperature becomes high and uniform. Therefore, the efficiency of heat energy recovery is high.

Further, in the indirect hot air generator according to the present invention, the heat energy retained in the combustion exhaust gas can be recovered by the regenerative burner. For this reason, it is possible to use a plate fin heat exchanger having a smaller size and a smaller heat transfer area than that of the conventional plate fin heat exchanger, that is, a plate fin heat exchanger having poor heat energy recovery efficiency. That is, since the heat that could not be recovered in the plate fin heat exchanger can be recovered in the heat storage body of the regenerative burner, there is no need to stick to the efficiency of the plate fin heat exchanger. Therefore, the size of the indirect hot air generator can be further reduced.

As described above, according to the present invention, it is possible to provide an indirect hot air generator which is small in size and has a high efficiency of recovering thermal energy.

Next, as in the second aspect of the present invention, the combustion chamber is divided into a first combustion chamber and a second combustion chamber by a partition, and the plate fin heat exchanger is provided in each of the combustion chambers. It is preferable that the regenerative burners are provided in each of the combustion chambers (see Embodiment 1).

As the regenerative burner in the above configuration, one that functions as a pair of two burners can be used. One regenerative burner is used as the first combustion chamber, and the other is used as the regenerative burner. It can be arranged in two combustion chambers. That is, when one of the first regenerative burners is in a combustion state, combustion exhaust gas discharged from the furnace is introduced into the other second regenerative burner. Thereby, the heat storage body provided in the second regenerative burner is in a heat storage state in which the heat retained by the combustion exhaust gas is stored.

Thereafter, the second regenerative burner is brought into a combustion state. At this time, the combustion air is fed into the second regenerative burner, and the combustion air is supplied to the combustor through the regenerator. Therefore, the combustion air is heated by the heat storage body, and high-temperature combustion air can be supplied. At this time, the combustion exhaust gas from the combustion chamber is introduced into the first regenerative burner, and heat is stored in the heat storage body of the first regenerative burner.

Accordingly, when the first regenerative burner in the first heating chamber is in a combustion state, forced convection of the combustion exhaust gas from the first heating chamber to the second heating chamber occurs, and the second convection in the second heating chamber. When the double regenerative burner is in a combustion state, forced convection of the combustion exhaust gas from the second heating chamber to the first heating chamber is generated, contrary to the above.

As a result, forced convection of the combustion exhaust gas occurs between the first combustion chamber and the second combustion chamber, and the forced convection of the combustion exhaust gas is rectified. By providing a plate-fin heat exchanger for each of the combustion chambers, the heat exchanger can be disposed at the center of the rectified forced convection. Therefore, it is possible to easily introduce the combustion exhaust gas into the plate fin heat exchanger.

Further, in the above-mentioned regenerative burner, the basic configuration is a method in which two pairs of the first regenerative burner and the second regenerative burner are paired, and both are used alternately in a combustion state and a heat storage state. However, a third, fourth or more regenerative burners are provided as appropriate, and a part of them is used as a combustion state and the other is used as a heat storage state. You can also.

Next, as in the third aspect of the invention, during the same time period, the regenerative burner in the combustion state and the regenerative burner in the regenerative state are separately provided in a plurality toward the combustion chamber. Preferably. This facilitates the introduction of the combustion exhaust gas into the plate fin heat exchanger, as in the second aspect.

Next, as in the fourth aspect of the present invention, it is preferable that the regenerative burner is a regenerative single burner capable of simultaneously operating the combustion state and the heat storage state (see Embodiment 2). . Thereby, the regenerative burner can be made smaller and the installation area of the burner can be reduced. Therefore, the indirect hot air generator can be made smaller.

Next, it is preferable that the combustion chamber is provided on both sides of the plate fin heat exchanger, as in the fifth aspect of the present invention. This facilitates the introduction of the combustion exhaust gas into the plate fin heat exchanger, as in the second aspect.

Although the plate fin heat exchanger is used in the indirect hot air generator of the present invention, a heat exchanger having another structure, for example, a heat exchanger using a radiant tube or the like may be used. Further, the hot air generated by the indirect hot air generator of the present invention can be used as a heat source for a drying oven or the like.

[0027]

BEST MODE FOR CARRYING OUT THE INVENTION

First Embodiment An indirect hot air generator according to an embodiment of the present invention will be described with reference to FIGS. Indirect hot air generator 1 of this example
As shown in FIG. 1, FIG. 2, and FIG. 6, a furnace body 10, first and second combustion chambers 21 and 22 provided therein, and a plate fin heat source provided over the combustion chambers 21 and 22 are provided. The exchanger 3, the combustors 411 and 421 for injecting the flame 40 into the first and second combustion chambers 21 and 22, and the regenerator 4
First and second regenerative burners 4 having 12,422
1,42.

Then, as shown in FIGS. 3, 4, and 5,
The plate fin heat exchanger 3 has a heated gas passage 31 for passing a heated gas 81 and a combustion exhaust gas passage 32 for passing a combustion exhaust gas 82, and both are arranged without conduction. In addition, the air to be heated 81 used in this example is the air taken in by the blower 91 through the heated gas inlet 111.

As shown in FIG. 1, a heated gas inlet 1 is provided between the furnace body 10 and the first and second combustion chambers 21 and 22.
A heated gas chamber 112 in which the heated gas 81 introduced from 11 is stored is provided. The above plate fin heat exchanger 3
The heated gas passage 31 in FIG.
And the opening of the plate fin heat exchanger 3
At the lower end.

As shown in FIG. 1, above the heated gas chamber 112, a hood 113 and a hot air discharge port 114 connected to the heated gas passage 31 of the plate fin heat exchanger 3 are provided. is there. Reference numeral 810 is the obtained hot air. As shown in FIG. 2, a partition 15 is provided between the first combustion chamber 21 and the second combustion chamber 22. The plate fin heat exchanger 3 is provided on both sides of the partition 15 respectively. It is provided.

The plate fin heat exchanger 3 will be described. As shown in FIG. 5, the plate fin heat exchanger 3 is composed of a large number of heated gas passages 31 which are alternately provided adjacently and which penetrate vertically and a flue gas passage 32 which penetrates horizontally. . As shown in FIGS. 3 and 4, the heated gas passage 31 is connected to the heated gas chamber 112.
And the hood 113. The flue gas passage 32 is open to the first and second combustion chambers 21 and 22, respectively.

The first and second regenerative burners 41, 4
2 will be described. As shown in FIG. 6, the first regenerative burner 41 and the second regenerative burner 42 have the same structure, and the combustors 411 and 421 and the combustors 411 and 42 have the same structure.
1. Fuel supply pipes 413, 423 for injecting fuel gas into
And an air supply pipe 44 for supplying combustion air.

On the upstream side of the combustors 411 and 421, heat storage bodies 412 and 4 made of ceramic honeycomb are provided.
22 are provided. The first and second regenerative burners 4
The air supply pipes 44 connected to the air supply pipes 1 and 42 are both connected to one air supply blower 49. A switching valve 48 is provided between the blower 49 and the air supply pipe 44 for switching the supply destination of the combustion air to the first and second regenerative burners 41 and 42.

The switching valve 48 is provided with a waste gas pipe 46, from which the heat storage elements 412, 422
Then, the combustion exhaust gas 82 after the heat has been recovered, that is, the waste gas 820 is discarded. Further, the air supply blower 49 can also serve as the blower 91 for the gas to be heated. In this case, the indirect hot air generator 1 according to the present embodiment can be made smaller.

Next, the operation of the indirect hot air generator 1 will be described. First, as shown in FIG. 6, combustion air and fuel gas are supplied to the first regenerative burner 41, and the combustor 411 is brought into a combustion state. Thereby, as shown in FIGS. 1, 2, and 4, the flame 40 is placed in the first heating chamber 21.
Squirts.

At the same time, the second regenerative burner 4
The combustion exhaust gas 82 is introduced into the second heat storage body 422.
As a result, the heat storage body 422 stores the heat held by the combustion exhaust gas 82 and enters a heat storage state.

As described above, when the first regenerative burner 41 is in the combustion state and the second regenerative burner 42 is in the heat storage state, as shown in FIG. The exhaust gas 82 passing through the exhaust gas passage 32 of the plate fin heat exchanger 3
Forced convection occurs. In addition, the above-mentioned heated gas inlet 1
The heated gas 81 introduced from the heating gas chamber 1
12, the gas is introduced into the heated gas passage 31 of the plate fin heat exchanger 3.

As a result, heat is exchanged between the adjacent heated gas passage 31 and the combustion exhaust gas passage 32,
The gas to be heated 81 rises as hot air 810, passes through the hood 113, and is led out of the furnace body 10 through the hot air outlet 114. The flue gas 82 that has passed through the plate fin heat exchanger 3 is then introduced into the regenerator 422 of the second regenerative burner 42, where the retained heat is removed. Thereafter, the combustion exhaust gas 82 becomes a waste gas 820, and is discharged from the waste gas pipe 46 to the outside of the furnace body 10 through the switching valve 48.

Next, 30 seconds after ignition of the first regenerative burner 41 (this time is 10 to 6 hours depending on the performance of the regenerator).
The selection can be made in a range of 0 seconds, but in this example, 30 seconds will be described. ), The switching valve 48 is switched to stop supplying the combustion air and the fuel gas to the first regenerative burner 41, and instead supply them to the second regenerative burner 42. As a result, the combustor 422 of the second regenerative burner 42 enters a combustion state.

At this time, the combustion air supplied to the second regenerative burner 42 is heated by the regenerator 422 previously stored by the combustion exhaust gas 82 and has a high temperature. At the same time, the first regenerative burner 41 is used.
The combustion exhaust gas 82 is introduced into the heat storage body 412. As a result, the heat storage body 412 stores the heat held by the combustion exhaust gas 82 and enters a heat storage state.

As a result, forced convection from the second combustion chamber 22 to the first combustion chamber 21 via the flue gas passage 32 of the plate fin heat exchanger 3 is generated. And
As in the above case, hot air 810 is obtained by heat exchange between the adjacent heated gas passage 31 and the combustion exhaust gas passage 32 inside the plate fin heat exchanger 3.

After the switching of the switching valve 48 and the ignition of the second regenerative burner 42 for 30 seconds, the switching valve 4 is switched again.
8 is switched to the state shown in FIG. As a result, the supply of the combustion air and the fuel gas to the second regenerative burner 42 is stopped, and this is brought into a heat storage state. On the other hand, these are supplied again to the first regenerative burner 41, and are brought into a combustion state.

Thereafter, by repeating this operation, the first regenerative burner 41 and the second regenerative burner 42 are alternately brought into a combustion state. The forced convection of the combustion exhaust gas 82 from the first combustion chamber 21 to the second combustion chamber 22 and the combustion exhaust gas 82 from the second combustion chamber 22 to the first combustion chamber 21
And forced convection are generated alternately.

Next, the operation and effect of this embodiment will be described. In the indirect hot air generator 1, the first and second regenerative burners 41 and 42 are used as burners for blowing out the flame 40 to the first and second combustion chambers 21 and 22. And the first and second regenerative burners 41, 4
Since the flame 40 formed by 2 changes its position every 30 seconds, it does not have a local high temperature part. Therefore, in the indirect hot air generator 1, the plate fin heat exchanger 3 is disposed in the first and second combustion chambers 21 and 22, where the high temperature combustion exhaust gas 82 can be directly taken in. Therefore, the size of the indirect hot air generator 1 can be reduced.

The first and second regenerative burners 4
When the combustion of the combustors 41 and 42 is performed,
A combustion exhaust gas 82 is generated from the flames 401, 421, and the combustion exhaust gas 8 is supplied to the heat storage bodies 412, 422 in a heat storage state.
2 flows in. Accordingly, there is a forced convection of the combustion exhaust gas 82 which always reverses the flow direction every 30 seconds.

That is, in this example, forced convection of the combustion exhaust gas 82 exists between the first combustion chamber 21 and the second combustion chamber 22. The plate fin heat exchanger 3 is provided in the forced convection. Therefore, the flue gas 8
By increasing the flow velocity when the gas is introduced into the plate fin heat exchanger 3, the overall heat transfer coefficient in the plate fin heat exchanger 3 can be increased.

The flow direction of the flue gas 82 passing through the flue gas passage 32 of the plate fin heat exchanger 3 is reversed every 30 seconds.
The surface of No. 2 is kept high in temperature and uniform throughout, so that the entire heat transfer area is effectively used for heat exchange. Therefore, the efficiency of heat energy recovery is high.

Therefore, according to the present embodiment, it is possible to provide an indirect hot air generator which is small in size and has a high efficiency of recovering thermal energy.

As shown in FIG. 7, the indirect hot air generator 1 according to the present embodiment has a structure in which a plate fin heat exchanger 3 is provided at the center of one combustion chamber 29 which is not partitioned by a partition wall or the like. Some are.

Embodiment 2 This embodiment is an indirect hot air generator using a regenerative single burner as shown in FIGS. The indirect hot air generator includes a furnace body, a combustion chamber 29 provided therein, a plate fin heat exchanger 3 provided in the combustion chamber 29, and a combustor for injecting a flame 40 into the combustion chamber 29. The heat storage type single burner 5 has a heat storage body 51 and a heat storage body 52.

The plate fin heat exchanger 3 is
It has the same structure as that of the first embodiment, and has a heated gas passage through which a heated gas to be heated passes and a combustion exhaust gas passage through which combustion exhaust gas passes, and both are arranged without conducting each other.

The regenerative single burner 5
9 has a combustor 51, a regenerator 52, and a flow path switching disk 55, and a fuel gas 54 is supplied to the combustor 51 via a fuel gas nozzle 58, as shown in FIG.

The regenerator 52 is composed of regenerators 521 and 522 separated by a partition, and the regenerator 521 is formed in an annular shape by a through hole 551 of a flow path switching disk 55 rotatably provided around the fuel gas nozzle 58. Air chamber 56
The heat storage body 522 is opened to the cylindrical exhaust chamber 57 through the through hole 552 of the flow path switching disk 55. On the other hand, each of the heat storage bodies 521 and 522 on the combustion chamber side is opened to the combustor 51 by a through hole.

The combustion air 53 is supplied to the air chamber 56 by the combustion air blower 49, and further becomes high-temperature air from the through hole 551 of the flow path switching disk 55 via the heat storage 521 and is injected into the combustor 51. Make a flame 40. As shown in FIG. 8, the combustion exhaust gas 82 generated by the flame 40 is returned to the combustor 51 via the plate fin heat exchanger 3 and penetrates from the heat storage body 522 of the heat storage 52 to the passage switching disk 55. The low-temperature combustion exhaust gas 820 is released to the atmosphere via the hole 552 and the exhaust chamber 57.

After a certain period of time, the passage switching disk 55 rotates and the through hole 551 opens to the heat storage body 522, and the through hole 552 opens to the heat storage body 521 to reverse the air flow path and the combustion exhaust gas flow path. . As a result, the combustion air 53 becomes high-temperature air from the air chamber 56 via the through hole 551 and the heat storage 522 and is injected into the combustor 51 to form the flame 40, and the combustion exhaust gas 82 is discharged from the heat storage 522. Through hole 551
And, it becomes low-temperature combustion exhaust gas 820 via the exhaust chamber 57 and is released to the atmosphere. By repeating this operation at a constant cycle, the same heat storage combustion as in the first embodiment is performed.

In the indirect hot air generator of this embodiment, the regenerative burner can be made smaller and the installation area of the burner can be made smaller. Therefore, the indirect hot air generator can be made smaller. Others have the same operation and effects as the first embodiment.

Third Embodiment As shown in FIGS. 10 to 12, this embodiment describes an indirect hot air generator having first and second combustion chambers with a plate fin heat exchanger interposed therebetween. First, in the indirect hot air generator according to FIG. 10, a first combustion chamber 61 and a second combustion chamber 62 are provided on both sides of the plate fin heat exchanger 3. The first combustion chamber 61 and the second combustion chamber 62 are provided with a first regenerative burner 41 and a second regenerative burner 42, respectively.

When the first regenerative burner 41 is in a combustion state, the second regenerative burner 42 is in a heat storage state, and the combustion exhaust gas 82 flows from right to left in the drawing. Others are the same as the first embodiment.

In the indirect hot air generator according to FIG. 11, first and second combustion chambers 611 and 612 and 621 and 622 are provided on both sides of the plate fin heat exchanger 3. And, the first and second combustion chambers 611, 612,
For each of 621 and 622, first regenerative burners 418 and 419 and second regenerative burners 428 and 429 are provided. And, the first combustion chamber 611, the second combustion chamber 6
The space 22 is defined by the partition wall 15.

When the first regenerative burners 418 and 419 are in the combustion state, the second regenerative burners 42
8, 429 are in a heat storage state, and the combustion exhaust gas is transferred from the first combustion chamber 611 to the second combustion chamber 621 and to the first combustion chamber 612.
To the second combustion chamber 622. Others are the same as the embodiment.

Further, in the indirect hot air generator according to FIG. 12, a first combustion chamber 61 and a second combustion chamber 62 are provided on both sides of the plate fin heat exchanger 3. Each of the combustion chambers 61 and 62 is provided with a regenerative single burner 5. In the regenerative single burner 5, as described in the second embodiment, the combustion state and the heat storage state operate simultaneously, and the combustion exhaust gas 82 generated from one regenerative single burner 5 is transferred to the other regenerative single burner 5. Is introduced. Others are the same as the first embodiment.

[0062]

As described above, according to the present invention, it is possible to provide an indirect hot air generator that is small in size and has high efficiency in recovering thermal energy.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional explanatory view of an indirect hot air generator according to a first embodiment.

FIG. 2 is an explanatory cross-sectional view of the indirect hot air generator according to the first embodiment.

FIG. 3 is a cross-sectional view taken along the line AA in FIG. 1 according to the first embodiment.

FIG. 4 is a cross-sectional view taken along the line BB in FIG. 1 according to the first embodiment.

FIG. 5 is an explanatory view showing the structure of the plate fin heat exchanger according to the first embodiment.

FIG. 6 is an explanatory view showing a structure of first and second regenerative burners according to the first embodiment.

FIG. 7 is an explanatory view showing a structure of an indirect hot air generator having no partition wall according to the first embodiment.

FIG. 8 is an explanatory view showing a structure of an indirect hot air generator using a heat storage type single burner according to a second embodiment.

FIG. 9 is an explanatory view showing the structure of a heat storage type single burner according to the second embodiment.

FIG. 10 is an explanatory view showing a structure of an indirect hot air generator having first and second combustion chambers with a plate fin heat exchanger interposed therebetween according to a third embodiment.

FIG. 11 is an explanatory view showing a structure of an indirect hot air generator having four combustion chambers according to a third embodiment.

FIG. 12 is an explanatory view showing a structure of an indirect hot air generator having first and second combustion chambers with a plate fin heat exchanger interposed therebetween and having a regenerative single burner according to a third embodiment.

FIG. 13 is an explanatory longitudinal sectional view of an indirect hot air generator according to a conventional example.

FIG. 14 is an explanatory cross-sectional view of a portion where a plate fin heat exchanger of an indirect hot air generator according to a conventional example is arranged.

[Explanation of Codes] . . 9. Indirect hot air generator, . . Furnace body, 21, 22,. . . 2. combustion chamber; . . 30. plate fin heat exchanger; . . Heated gas passage, 32. . . Flue gas passage, 40. . . Flame, 41, 42. . . Regenerative burners, 411,421. . . Combustor, 412, 422. . . Thermal storage, 5. . . Storage type single burner, 81. . . Gas to be heated, 810. . . Hot air, 82. . . Flue gas,

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Mamoru Matsuo 2-1-153 Shirite, Tsurumi-ku, Yokohama-shi, Kanagawa Prefecture Inside Japan Furness Industry Co., Ltd. (72) Inventor Kiyofumi Kurita 2-1-1 Shirite, Tsurumi-ku, Yokohama-shi, Kanagawa No. 53 Inside Japan Furnace Industry Co., Ltd.

Claims (5)

[Claims] 1. A regenerative storage system comprising a furnace body, a combustion chamber provided therein, a plate fin heat exchanger provided in the combustion chamber, a combustor for injecting a flame into the combustion chamber, and a regenerator. The plate fin heat exchanger has a heated gas passage through which a gas to be heated is passed and a flue gas passage through which flue gas is passed;
An indirect hot air generator characterized in that both are arranged without conducting each other. 2. The combustion chamber according to claim 1, wherein the combustion chamber is divided into a first combustion chamber and a second combustion chamber by a partition, and the plate fin heat exchanger is disposed in each combustion chamber. An indirect hot air generator, wherein each of the regenerative burners is provided in a combustion chamber. 3. A regenerative burner in a combustion state and a regenerative burner in a heat storage state in a plurality of times each being provided toward the combustion chamber in the same time zone. Indirect hot air generator. 4. The indirect hot air generator according to claim 1, wherein the regenerative burner is one or a plurality of regenerative single burners capable of simultaneously operating a combustion state and a heat storage state. . 5. The method according to claim 1, wherein:
An indirect hot air generator, wherein the combustion chamber is provided on both sides of the plate fin heat exchanger.