JP5979722B2 - Temperature control system for heating equipment and temperature control method thereof - Google Patents

Description

  The present invention relates to a temperature control system for a heating facility and a temperature control method therefor, and in particular, a heating furnace in which hot air having a predetermined temperature is supplied, and the hot air discharged from the heating furnace are heated and returned to the heating furnace. Heating means, control means for controlling the output of the heating means to heat the hot air returning to the heating furnace to a predetermined temperature, and gas combustion processing for collecting and burning the gas generated in the heating furnace The present invention relates to a temperature control system for a heating facility including a furnace, and a temperature control method for the heating facility.

  For example, as a work heated in a heating furnace, in a painting drying process for baking and drying a body of an automobile that has finished painting, the inside of the heating furnace to which hot air controlled to a predetermined temperature is supplied is provided. The work such as body is moved. In general, in order to efficiently supply hot air having a predetermined temperature to the inside of the heating furnace, the hot air discharged from the heating furnace is heated to a predetermined temperature by heating means and is refluxed to the heating furnace. The heating means has, for example, an indirect heating furnace and an indirect heating furnace heat exchanger, or has a direct fire heating furnace. The output of these heating means is controlled in order to accurately control the temperature of hot air supplied to the heating furnace in accordance with the heat demand of the heating furnace, which fluctuates relatively greatly.

  By the way, in the said coating drying process, a volatile component generate | occur | produces from the coating material coated on the workpiece | work. Therefore, collecting volatile components and combusting them in a gas combustion processing furnace has also been conventionally performed. In this case, in order to control the temperature of the hot air that recovers exhaust heat discharged from the gas combustion treatment furnace and circulates and supplies it to the heating furnace, for example, a heat storage body as disclosed in Patent Document 1 is used. It is known to use.

Patent Document 1 relates to a deodorization system that removes odor generated in a heat facility that performs a predetermined treatment using a relatively low temperature air flow such as a drying furnace or a foaming furnace as a heat source (0001).
In Patent Document 1, as a conventional technique, a hot air furnace 102 that supplies hot air of medium to low temperature to a heat facility 101 that is operated with medium to low temperature heat such as a drying furnace or a foaming furnace, A deodorization furnace comprising a deodorizing furnace 103 that takes out the odor gas generated in the thermal equipment 101 that performs predetermined drying and foaming operations on the workpiece W using the supplied hot air, and deodorizes it by combustion or thermal decomposition. A system has been described (0002).

  And in patent document 1, in the deodorizing system which removes the odor which generate | occur | produces the odor generated from the heat equipment which uses medium-low temperature airflow as a heat source, the exhaust from the said heat equipment containing an odor gas is mixed in a flame and burned alternately. A deodorizing furnace having at least a pair of burners, and including at least the thermal equipment and a circulation fan, the combustion exhaust gas in the deodorizing furnace is taken out of the furnace in the vicinity of the burner or through the burner, and is passed through the thermal equipment before the deodorization. The circulation fan is provided with a recirculation system in the vicinity of the other burner or recirculated through the burner into the furnace, and a regenerator in each of the recirculation paths near the pair of circulation ports of the deodorizing furnace. Of the combustion gas from the deodorizing furnace via the heat accumulator and the deodorizing furnace by reversing the direction of the air flow between the deodorizing furnace and the pair of circulation ports of the deodorizing furnace And a flow path switching device that periodically switches the circulation port for refluxing, and alternately burning the burners and switching the flow path switching device in synchronization with the burner, thereby changing the flow direction of the air flow to the deodorization furnace Exhaust gas containing odor generated in the heat facility while supplying combustion exhaust gas taken out from the deodorization furnace to the medium-low temperature heat facility while alternately switching the heat accumulator that is periodically reversed and passed through the heat storage body The deodorizing system is characterized in that it is refluxed into the deodorizing furnace and burned.

  In Patent Document 1, according to the deodorization system of the present invention, the combustion exhaust gas in the deodorization furnace used for incineration or thermal decomposition of odor components passes through the regenerator on the outside circulation path intake side. A part of the sensible heat is collected in the heat storage body and supplied to the heat facility as a medium-low temperature air stream used in the heat facility, and after completing the prescribed work in the heat facility, the discharge side of the outside circulation system In the heat storage unit, the heat recovered is used to return to the deodorization furnace after the temperature is raised again, so that heat generated from the heat generated in the deodorization furnace cannot be fully recovered by the heat accumulator and is discarded in the heat facility. It is described that the facility can be made compact and low-cost without requiring a separate hot stove for the heat facility.

  In addition, as a conventional technique different from that provided with a heat storage body, there is also provided a heat exchanger for heating circulating hot air that recovers exhaust heat from a gas combustion treatment furnace by transferring it to hot air supplied to a heating furnace. . In general, the exhaust heat temperature of the gas combustion treatment furnace has a constant air volume and a constant temperature, and is higher than the temperature of the hot air supplied to the heating furnace. As an example of this temperature, the exhaust heat temperature of the gas combustion treatment furnace is 800 to 1000 ° C., whereas the temperature of the hot air supplied to the heating furnace is 80 to 100 ° C.

JP-A-9-178151

  However, among the above conventional techniques, in Patent Document 1, a dust collector is provided on the upstream side of the heat equipment in the out-of-furnace circulation system, and combustion in a deodorizing furnace used for incineration or thermal decomposition of odor components is performed. Since the exhaust gas is supplied to the heat facility via the dust collector, if the dust contained in the circulating airflow introduced to the heat facility cannot be completely removed, the dust will be transferred to the heat facility. There was a problem that it may adhere to the workpiece inside.

  Moreover, in what recovers the sensible heat of the combustion exhaust gas in a deodorizing furnace like the said patent document 1 with a thermal storage body, the capacity | capacitance which collect | recovers the sensible heat of this thermal storage body is proportional to the volume of a thermal storage body. Therefore, in order to efficiently recover the sensible heat of the combustion exhaust gas in the deodorization furnace (in the present invention, the gas combustion treatment furnace), it is necessary to enlarge the heat storage body. Therefore, when using a heat storage body, there existed problems, such as the installation space of a heat storage body becoming large and the installation cost starting.

  Further, in the case of adjusting the temperature of the airflow supplied to the heat equipment (the heating furnace in the present invention) by the heat storage body as in Patent Document 1, the responsiveness of the temperature control of the hot air supplied to the heating furnace is slow. For this reason, there has been a problem that the temperature of the hot air cannot be accurately controlled according to the heat demand of the heating furnace.

  On the other hand, among the above-mentioned conventional technologies, in the case of recovering the exhaust heat of the gas combustion treatment furnace by transferring it to the hot air supplied to the heating furnace using a heat exchanger, the heating load of the heating furnace varies relatively greatly. In this situation, if the exhaust heat from the gas combustion treatment furnace is actively recovered by the heat exchanger, the recovery of the exhaust heat becomes a great disturbance to the temperature control by the heating means, and as a result, the temperature of the hot air supplied to the heating furnace. There was a problem when the control became unstable. And from this problem, the recovery of exhaust heat from the gas combustion treatment furnace must be set to a value smaller than the minimum output of the heating means, and the exhaust heat of the gas combustion treatment furnace is efficiently recovered and used. There was a problem that there was a restriction to do.

  The present invention has been made in order to solve the above-described problems in an advantageous manner. With a simple configuration, the exhaust heat of the gas combustion processing furnace is efficiently recovered and used, and the temperature of the heating furnace is accurately controlled. An object of the present invention is to provide a temperature control system for a heating facility and a temperature control method thereof that can save energy of the heating means.

In order to achieve the above object, the invention relating to a temperature control system for a heating facility according to claim 1 is configured so that hot air having a predetermined temperature is supplied therein, and hot air discharged from the heating furnace is set to a set temperature. A heating equipment temperature control system comprising: heating means for heating at a predetermined output and recirculating to the heating furnace; and a gas combustion processing furnace for collecting and burning the gas generated in the heating furnace. A heat exchanger for heating the circulating hot air that transfers the heat of the exhaust discharged from the gas combustion processing furnace to the hot air sent from the heating furnace to the heating means, and the exhaust of the exhaust discharged from the gas combustion processing furnace. Exhaust gas supply control damper for controlling supply to the circulating hot air heating heat exchanger, and exhaust gas provided in a flow path for sending the exhaust gas discharged from the gas combustion treatment furnace to the circulating hot air heating heat exchanger Balance damper and front Damper control means for controlling the opening and closing of the exhaust supply control damper based on the output of the heating means, and for controlling the opening and closing of the exhaust balance damper so as to adjust the air volume of the exhaust discharged from the gas combustion treatment furnace; It is characterized by having.
According to a thirteenth aspect of the present invention related to the temperature control method for a heating facility, in order to achieve the above object, a heating furnace in which hot air of a predetermined temperature is supplied inside, and hot air discharged from the heating furnace as a set temperature. A temperature control method for a heating facility comprising heating means for heating at a predetermined output and recirculating to the heating furnace, and a gas combustion processing furnace for collecting and burning the gas generated in the heating furnace. A heat exchanger for heating the circulating hot air for transferring the heat of the exhaust discharged from the gas combustion treatment furnace to the hot air sent from the heating furnace to the heating means, and the exhaust discharged from the gas combustion treatment furnace An exhaust supply control damper for controlling the supply to the circulating hot air heating heat exchanger, and a flow path for sending the exhaust discharged from the gas combustion processing furnace to the circulating hot air heating heat exchanger. , Heat exchange for circulating hot air heating An exhaust balancing damper for adjusting the flow rate of the exhaust gas sent to, advance the provided, characterized in that controlling the opening and closing of the exhaust supply control damper and the exhaust balanced damper based on the output of the heating means.

In the invention relating to the temperature control system of the heating facility according to the first aspect, the output of the heating means is controlled by the temperature of the hot air heated by the heating means with respect to the set temperature of the heating furnace and returned to the heating furnace. The damper control means controls the opening / closing of the exhaust supply control damper based on the output of the heating means, and opens / closes the exhaust balance damper so as to adjust the air volume of the exhaust discharged from the gas combustion processing furnace. To control. At this time, if the exhaust gas supply control damper is controlled to open, the air volume of the exhaust gas discharged from the gas combustion processing furnace varies so as to decrease, and if the exhaust gas supply control damper is controlled to close, the gas combustion processing furnace A tendency to fluctuate so that the air volume of the exhaust gas discharged increases. However, in any case, these fluctuation trends are avoided by controlling the opening and closing of the exhaust balance damper so that the exhaust balance damper performs correction adjustment, and the exhaust balance damper is discharged from the gas combustion processing furnace and supplied to the circulating hot air heating heat exchanger. The air volume of the exhaust air is kept stable without significant fluctuations.
According to the invention relating to the temperature control system of the heating facility according to claim 1, while controlling the output of the heating means according to the temperature of the hot air heated by the heating means with respect to the set temperature and returned to the heating furnace, In order to control the opening and closing of the exhaust supply control damper according to this output, and to control the opening and closing of the exhaust balance damper so that the air flow of the gas combustion processing furnace is adjusted and kept stable, the gas combustion processing furnace has a simple configuration. The heat of the exhaust exhausted from the heat can be efficiently recovered and utilized, so the output of the heating means can be minimized, and the temperature of the heating furnace can be controlled with high responsiveness and high accuracy. can do. And the big space and equipment cost which were required due to providing a thermal storage body like the prior art can be reduced.
In the invention relating to the temperature control method for a heating facility according to claim 13, a heat exchanger for circulating hot air heating, an exhaust supply control damper and an exhaust balance damper are provided, and the heating means is heated with respect to the set temperature. The output of the heating means is controlled according to the temperature of the hot air returned to the heating furnace. Then, opening / closing of the exhaust supply control damper and the exhaust balance damper is controlled based on the output of the heating means. At this time, if the exhaust gas supply control damper is controlled to open, the air flow of the exhaust gas discharged from the gas combustion processing furnace fluctuates to decrease, and if the exhaust gas supply control damper is controlled to close, the exhaust gas discharged from the gas combustion processing furnace There is a tendency to fluctuate as the air volume of the air increases. However, these variations tend to be avoided in any case by controlling the opening and closing of the exhaust balance damper so as to correct and adjust the exhaust balance damper, and are discharged from the gas combustion processing furnace and supplied to the circulating hot air heating heat exchanger. The air volume of the exhaust is not greatly fluctuated and the air volume is kept stable.
According to the invention relating to the temperature control method for a heating facility of claim 13, the output of the heating means is controlled according to the temperature of the hot air heated by the heating means with respect to the set temperature and returned to the heating furnace, In order to control the opening and closing of the exhaust supply control damper according to this output, and to control the opening and closing of the exhaust balance damper so as to keep the air flow of the gas combustion processing furnace stable, the exhaust gas is discharged from the gas combustion processing furnace with a simple configuration. Therefore, it is possible to efficiently recover and utilize the heat of the exhaust gas. Therefore, the output of the heating means can be minimized, and the temperature of the heating furnace can be controlled with high responsiveness and high accuracy. it can. And the big space and equipment cost which were required due to providing a thermal storage body like the prior art can be reduced.

(Aspect of the Invention)
The invention relating to the temperature control system for a heating facility according to claim 2 is the invention according to claim 1, wherein the damper control means preliminarily determines the output of the heating means and the opening / closing of the exhaust supply control damper. The opening and closing of the exhaust supply control damper is controlled by comparing the set upper limit value and lower limit value of the heating means, and the air volume of the exhaust discharged from the gas combustion treatment furnace is adjusted. It is characterized by controlling the opening and closing of the exhaust balance damper.
In the invention of claim 2, in order to determine whether the exhaust supply control damper is opened or closed, the upper limit value and the lower limit value of the output of the heating means are set in advance and input to the damper control means. The damper control means outputs the output of the heating means controlled based on the temperature of the hot air discharged from the heating furnace and the hot air heated by the heating means and recirculated to the heating furnace with respect to the set temperature. Compare with the value. When the output of the heating means is lower than the set lower limit value, the damper control means controls the exhaust supply control damper to be closed, to the heat exchanger for heating the circulating hot air of the exhaust discharged from the gas combustion processing furnace Reduce the amount of supply. When the output of the heating means is higher than the set upper limit value, the damper control means controls to open the exhaust supply control damper to the heat exchanger for heating the circulating hot air of the exhaust discharged from the gas combustion processing furnace. Increase the supply amount. Further, when the output of the heating means is in the range between the set lower limit value and the upper limit value, the damper control means controls to prohibit the operation of the exhaust supply control damper. Control of opening and closing the exhaust supply control damper easily and reliably with high responsiveness and high accuracy can be realized. In any of the above cases, the change in the air volume of the exhaust discharged from the gas combustion processing furnace caused by the operation of the exhaust supply control damper is determined in advance by the correction operation of the exhaust balance damper by the damper control means. It converges to the fluctuation range determined by the determined upper limit value and lower limit value. Therefore, the gas flow rate of the gas combustion treatment furnace is kept stable without greatly fluctuating.

An invention relating to a temperature control system for a heating facility according to claim 3 is the invention according to claim 1 or 2, wherein the damper control means is configured such that an air volume of exhaust discharged from the gas combustion processing furnace is a constant value. Alternatively, the opening and closing of the exhaust balance damper is adjusted so as to be within a predetermined range.
In the invention of claim 3, the air volume of the exhaust gas discharged from the gas combustion processing furnace of a constant value or a predetermined range is set and inputted to the damper control means. When this air volume is set within a predetermined range, an upper limit value and a lower limit value of the air volume are set. When the air volume of the exhaust discharged from the gas combustion processing furnace is lower than the set lower limit value, the damper control means controls the exhaust balance damper to close, and the circulating hot air of the exhaust discharged from the gas combustion processing furnace Increase the supply to the heat exchanger for heating. If the air volume is higher than the set upper limit, the damper control means controls the exhaust balance damper to open, and the amount of exhaust discharged from the gas combustion processing furnace to the circulating hot air heating heat exchanger is controlled. Decrease. Further, when the air volume is in the range from the set lower limit value to the upper limit value, the damper control means controls to prohibit the operation of the exhaust balance damper. As a result, it is possible to correct the change in the air volume of the exhaust gas discharged from the gas combustion processing furnace caused by the operation of the exhaust gas supply control damper, to converge the air volume to a predetermined fluctuation range, and to keep it stable. Can be embodied.

The invention related to the temperature control system for a heating facility according to claim 4 is the invention according to any one of claims 1 to 3, wherein the heat of the exhaust discharged from the gas combustion treatment furnace is captured from the heating furnace. It further comprises a gas heating heat exchanger that collects and transfers heat to the gas that is burnt and processed in the gas combustion processing furnace.
In the invention of claim 4, the heat of the exhaust gas discharged from the gas combustion processing furnace is collected from the heating furnace and transferred to the gas to be burned in the gas combustion processing furnace by the heat exchanger for gas heating. Since the gas collected from the heating furnace is heated in advance, the gas can be reliably combusted in the gas combustion processing furnace, and energy required for the gas combustion processing furnace can be reduced.

The invention related to the temperature control system of the heating facility according to claim 5 is the hot air sent from the heating furnace to the heat exchanger for heating the circulating hot air in the invention according to any one of claims 1 to 4. Air addition means for controllably adding air in the atmosphere, and exhaust gas transferred from the gas combustion treatment furnace to the hot air sent from the heating furnace to the heating means by the heat exchanger for heating the circulating hot air. And a heat exchanger for heating added air for transferring heat to the air added by the air adding means.
In the invention of claim 5, when the fresh air in the atmosphere is added to the hot air discharged from the heating furnace by the air addition means and sent to the circulating hot air heating heat exchanger, the additional air heating heat exchanger Since the heat of the exhaust exhausted from the combustion treatment furnace and transferred to the hot air sent from the heating furnace to the heating means by the heat exchanger for heating the circulating hot air is further transferred to the air added by the air addition means, The heat of the exhaust gas discharged from the gas combustion treatment furnace can be recovered and used more efficiently. Therefore, the output of the heating means can be minimized, and the temperature of the heating furnace can be accurately controlled. can do.

The invention related to the temperature control system for a heating facility according to claim 6 is the invention according to any one of claims 1 to 5, wherein the heating furnace is divided into a plurality of zones each supplied with hot air of a predetermined temperature. The heating means, the circulating hot air heating heat exchanger, and the exhaust supply control damper are provided for each zone.
In the invention of claim 6, the heating furnace is set with a plurality of zones divided by the heat demand, and supplies hot air having a temperature set according to the heat demand for each zone. Therefore, the heating means, the circulating hot air heating heat exchanger, and the exhaust supply control damper are provided for each zone. When the heating means of each zone is higher than the set value, control is performed to open the exhaust gas supply control damper corresponding to that zone, and the exhaust gas discharged from the gas combustion processing furnace is heated by circulating hot air corresponding to that zone. The heat of the exhaust discharged from the gas combustion treatment furnace is transferred to the hot air sent from the zone to the heating means. On the other hand, when the output of the heating means of each zone is substantially equal to the set value, the opening degree of the exhaust supply control damper is maintained and the heat of the exhaust discharged from the gas combustion processing furnace is circulated for hot air heating. The amount of heat transferred from the zone to the hot air sent to the corresponding heating means is maintained. Further, when the output of the heating means in each zone is lower than the set value, the exhaust opening control damper corresponding to that zone is closed to reduce the opening, and the exhaust discharged from the gas combustion processing furnace The amount of heat transferred by the circulating hot air heating heat exchanger to the hot air sent from the zone to the corresponding heating means is reduced. In any of the above cases, in each zone, by controlling the opening and closing of the exhaust balance damper so as to correct and adjust, the air volume does not fluctuate greatly with the opening and closing of the exhaust supply control damper, and a stable air volume is maintained. .
According to claim 6, by controlling the opening and closing of the exhaust supply control damper according to the temperature of the hot air heated by the heating means of each zone divided according to the magnitude of heat demand and returned to the heating furnace The exhaust gas discharged from the gas combustion processing furnace can be supplied to the circulating hot air heating heat exchanger and transferred to the hot air sent from each zone to the corresponding heating means. Therefore, it is possible to efficiently recover and use the heat of the exhaust gas discharged from the gas combustion processing furnace according to the heat demand of a plurality of zones in which the heating furnace is divided and set with a simple configuration. The output of the heating means can be minimized, and the temperature of each zone can be controlled with high responsiveness and high accuracy.

The invention related to the temperature control system for a heating facility according to claim 7 is the invention according to claim 6, wherein the heat of the exhaust discharged from the gas combustion treatment furnace is converted into a zone having a large heat demand among the plurality of zones. The heat is supplied to the heat exchanger for heating the circulating hot air in order from each zone, and heat is transferred from each zone to the hot air sent to the heating means.
In the invention of claim 7, when the heat demand is different depending on a plurality of zones of the heating furnace, the gas combustion processing furnace in order from the heat exchanger for heating the circulating hot air corresponding to the zone having the highest heat demand among the zones. It is possible to supply exhaust gas exhausted from the heat source and transfer the heat to the hot air sent from each zone to the heating means in order as needed, and therefore according to the heat demand that varies depending on the zone in the heating furnace, The temperature of the hot air can be adjusted by efficiently recovering and using the heat of the exhaust discharged from the gas combustion processing furnace, and supplied to each zone.

The invention related to the temperature control system for a heating facility according to claim 8 is the heat exchange for heating the circulating hot air in the plurality of zones in the invention according to claim 6, wherein the heat of the exhaust discharged from the gas combustion treatment furnace is used. It is characterized by being distributed and supplied to the vessel in parallel and transferring heat to the hot air sent from each zone to the heating means.
In the invention of claim 8, when the heat demands of the plurality of divided zones of the heating furnace are the same, the heat of the exhaust discharged from the gas combustion treatment furnace is used as the heat exchanger for heating the circulating hot air of the plurality of zones. The exhaust gas discharged from the gas combustion treatment furnace is uniformly supplied to the circulating hot air heating heat exchanger in each zone, and the heat is sent from each zone to the heating means as necessary. Therefore, the heat of the exhaust discharged from the gas combustion treatment furnace can be efficiently recovered and used to adjust the temperature of the hot air and supply it to each zone.

The invention relating to the temperature control system for a heating facility according to claim 9 is the invention according to any one of claims 1 to 8, wherein the discharge temperature measuring means for measuring the temperature of hot air discharged from the heating furnace, At least one of reflux temperature measuring means for measuring the temperature of hot air to be refluxed to the heating furnace, and the heating means is based on a measurement result of at least one of the discharge temperature measuring means and the reflux temperature measuring means The output is adjusted.
In the invention of claim 9, the output of the heating means is at least one of a discharge temperature measuring means for measuring the temperature of the hot air discharged from the heating furnace, and a reflux temperature measuring means for measuring the temperature of the hot air returned to the heating furnace. Adjust based on either measurement result. Therefore, it is possible to accurately adjust the output of the heating means and accurately control the temperature of the hot air to be returned to the heating furnace.

The invention related to the temperature control system for a heating facility according to claim 10 is the invention according to any one of claims 1 to 9, wherein the exhaust gas between the gas combustion treatment furnace and the exhaust balance damper is passed through the circulating hot air. The flow path for sending to the heat exchanger for heating further has an air volume measuring means for measuring the air volume of the exhaust, and the damper control means is configured to control the exhaust supply control damper based on the output of the heating means. The opening and closing of the exhaust balance damper is controlled based on the measurement result of the air volume measuring means.
In the invention of claim 10, the air volume of the exhaust gas sent to the circulating hot air heating heat exchanger is measured by a path between the gas combustion processing furnace and the exhaust balance damper by the air volume measuring means. The damper control means controls the opening and closing of the exhaust supply control damper based on the output of the heating means, and controls the opening and closing of the exhaust balance damper based on the measurement result of the air volume measuring means. Thereby, it is embodied that the exhaust gas discharged from the gas combustion processing furnace is sent with a stable air volume.

An invention relating to a temperature control system for a heating facility according to an eleventh aspect is the invention according to the tenth aspect, wherein the damper control means includes a measurement result of the flow rate of the exhaust gas measured by the flow rate measurement means, and the exhaust balance damper. The opening and closing of the exhaust balance damper is controlled by comparing the upper limit value and the lower limit value of the exhaust gas flow rate between the gas combustion processing furnace and the exhaust balance damper, which are set in advance to determine the opening and closing of the exhaust gas. It is characterized by being.
In the invention of claim 11, in order to determine whether the exhaust balance damper is opened or closed, an upper limit value and a lower limit value of the exhaust gas flow rate between the gas combustion treatment furnace and the exhaust balance damper are set in advance, and the damper control means Enter it. The measurement result of the air volume of the exhaust gas sent by the path between the gas combustion processing furnace and the exhaust balance damper measured by the air volume measuring means is compared with the upper limit value and the lower limit value of the previously input air volume. When the measurement result of the air volume is lower than the set lower limit value, the exhaust balance damper is controlled to be closed by the damper control means, and the heat exchanger for heating the circulating hot air and the exhaust supply control damper are discharged from the gas combustion processing furnace. Increase the air volume of the exhaust sent to When the measurement result of the air volume is higher than the set upper limit value, the damper control means controls to open the exhaust balance damper, and the heat exchanger for heating the circulating hot air and the exhaust supply control damper are discharged from the gas combustion processing furnace. Reduces the amount of air sent to the exhaust. In addition, when the measurement result of the air volume is in the range between the set lower limit value and the upper limit value, the exhaust balance damper is controlled by the damper control means to be discharged from the gas combustion treatment furnace and the heat for circulating hot air heating. The air volume of the exhaust gas sent to the exchanger and the exhaust gas supply control damper is increased. Control is performed by the damper control means to prohibit the operation of the exhaust balance damper. Control the opening and closing of the exhaust balance damper easily and reliably with high responsiveness and high accuracy, and send the exhaust air with a stable air volume in the range between the upper limit value and the lower limit value regardless of the operation of the exhaust supply control damper Can be realized.

The invention related to a temperature control system for a heating facility according to a twelfth aspect is the invention according to any one of the first to eleventh aspects, wherein the damper control means is configured to reverse the exhaust balance of the exhaust supply control damper. It is characterized by controlling the opening and closing of the damper.
According to a twelfth aspect of the present invention, the damper control means utilizes the fact that the change in the exhaust air volume due to the opening and closing of the exhaust supply control damper is inversely proportional to the change in the exhaust air volume due to the opening and closing of the exhaust balance damper. Control is performed so that the opening / closing operation of the exhaust supply control damper and the opening / closing operation of the exhaust balance damper are reversed. Therefore, the control for opening and closing the exhaust supply control damper and the exhaust balance damper is simplified and facilitated.

An invention relating to a temperature control method for a heating facility according to a fourteenth aspect is the invention according to the thirteenth aspect, wherein an upper limit value and a lower limit value of the output of the heating means for determining whether the exhaust supply control damper is opened or closed are set. By setting the output of the heating means in advance and comparing the upper limit value and the lower limit value of the output of the heating means, the exhaust supply control damper is controlled to be opened and closed and discharged from the gas combustion processing furnace. The amount of exhaust gas sent to the circulating hot air heating heat exchanger is controlled, and the opening and closing of an exhaust balance damper is controlled to adjust the amount of exhaust air sent to the circulating hot air heating heat exchanger. .
According to the fourteenth aspect of the present invention, in order to determine whether the exhaust supply control damper is opened or closed, the upper limit value and the lower limit value of the output of the heating means are set in advance. The output of the heating means is controlled based on the temperature of the hot air discharged from the heating furnace with respect to the set temperature and the temperature of the hot air heated by the heating means and returned to the heating furnace, and the output of the heating means and its upper limit Compare the value and the lower limit. When the output of the heating means is lower than the set lower limit value, the exhaust supply control damper is controlled to close, and the supply amount of the exhaust discharged from the gas combustion processing furnace to the circulating hot air heating heat exchanger is controlled. Decrease. When the output of the heating means is higher than the set upper limit value, the exhaust supply control damper is controlled to open, and the amount of exhaust discharged from the gas combustion processing furnace to the circulating hot air heating heat exchanger is controlled. Increase. Further, when the output of the heating means is in the range from the set lower limit value to the upper limit value, control is performed so as to prohibit the operation of the exhaust supply control damper. As a result, it is possible to easily and reliably control the opening and closing of the exhaust supply control damper with high accuracy and high responsiveness. In any of the above cases, the change in the air volume of the exhaust gas discharged from the gas combustion processing furnace caused by the operation of the exhaust gas supply control damper is corrected by the exhaust balance damper so that a predetermined upper limit value is set. And the fluctuation range determined by the lower limit value. Therefore, the gas flow rate of the gas combustion treatment furnace is kept stable without greatly fluctuating.

The invention related to the temperature control method for a heating facility according to claim 15 is the invention according to claim 13 or 14, wherein the amount of exhaust air sent to the circulating hot air heating heat exchanger is a constant value or a predetermined range. Thus, the opening and closing of the exhaust balance damper is controlled.
According to the fifteenth aspect of the present invention, the air volume of the exhaust gas discharged from the gas combustion processing furnace is set in advance at a constant value or within a predetermined range. When this air volume is set within a predetermined range, an upper limit value and a lower limit value of the air volume are set. When the air volume of the exhaust discharged from the gas combustion processing furnace is lower than the set lower limit value, the exhaust balance damper is controlled to be closed, and the heat exchange for heating the circulating hot air of the exhaust discharged from the gas combustion processing furnace is performed. Increase the supply to the vessel. When the air volume is higher than the set upper limit value, the exhaust balance damper is controlled to open, and the supply amount of the exhaust gas discharged from the gas combustion processing furnace to the circulating hot air heating heat exchanger is decreased. Further, when the air volume is in the range from the set lower limit value to the upper limit value, control is performed so as to prohibit the operation of the exhaust balance damper. As a result, it is possible to realize the correction of the change in the air volume of the exhaust gas exhausted from the gas combustion processing furnace caused by the operation of the exhaust gas supply control damper so that the air volume converges to a predetermined fluctuation range and is kept stable. .

The invention related to the temperature control method for a heating facility according to claim 16 is the invention according to any one of claims 13 to 15, wherein the heat of the exhaust discharged from the gas combustion treatment furnace is captured from the heating furnace. Heat is transferred to the gas that is collected and burned in the gas combustion treatment furnace.
In the invention of claim 16, the gas collected from the heating furnace is obtained by transferring the heat of the exhaust discharged from the gas combustion processing furnace to the gas that is collected from the heating furnace and burned in the gas combustion processing furnace. Is preheated and burned. Therefore, the gas collected from the heating furnace can be reliably burned in the gas combustion processing furnace, and the energy required for the gas combustion processing furnace can be reduced.

The invention related to the temperature control method for a heating facility according to claim 17 is the invention according to any one of claims 13 to 16, wherein the hot air is discharged from the heating furnace and sent to the heat exchanger for heating the circulating hot air. The air in the atmosphere is added in a controllable manner, and the heat of the exhaust gas transferred from the gas combustion treatment furnace and transferred to the hot air sent from the heating furnace to the heating means by the heat exchanger for heating the circulating hot air, It is characterized by transferring heat to air.
In the invention of claim 17, when fresh air in the atmosphere is added to the hot air discharged from the heating furnace and sent to the circulating hot air heating heat exchanger, the circulating hot air heating heat exchanger discharged from the gas combustion processing furnace Since the heat of the exhaust gas transferred from the heating furnace to the hot air sent to the heating means is further transferred to the added air, the heat of the exhaust gas discharged from the gas combustion processing furnace can be recovered more efficiently. Therefore, the output of the heating means can be minimized, and the temperature of the heating furnace can be accurately controlled.

The invention related to the temperature control method for a heating facility according to claim 18 is the invention according to any one of claims 13 to 17, wherein the heating furnace is provided in a plurality of zones each supplied with hot air of a predetermined temperature. In each zone, the heating means, the circulating hot air heating heat exchanger, the exhaust supply control damper and the exhaust balance damper are provided, and according to the temperature set for each zone, Controlling the output of the heating means based on the temperature of the hot air in the zone, controlling the opening and closing of the exhaust gas supply control damper based on the output of the heating means, and the exhaust gas discharged from the gas combustion processing furnace The supply amount to the circulating hot air heating heat exchanger is controlled, and the opening and closing of the exhaust balance damper is controlled to adjust the amount of exhaust air sent to the circulating hot air heating heat exchanger.
In invention of Claim 18, the several zone divided according to the heat demand of the heating furnace is set, and the hot air of the temperature set according to the heat demand for each zone is supplied. Therefore, the heating means, the circulating hot air heating heat exchanger, the exhaust supply control damper and the exhaust balance damper are provided. When controlling the temperature of the hot air supplied to the heating furnace, the temperature of the hot air discharged from each zone and the temperature of the hot air heated by each heating means and returned to each zone are detected. When the heating means of each zone is higher than the set value, control is performed to open the exhaust gas supply control damper corresponding to that zone, and the exhaust gas discharged from the gas combustion processing furnace is heated by circulating hot air corresponding to that zone. The heat of the exhaust discharged from the gas combustion treatment furnace is transferred to the hot air sent from the zone to the heating means. On the other hand, when the output of the heating means of each zone is substantially equal to the set value, the opening degree of the exhaust supply control damper is maintained and the heat of the exhaust discharged from the gas combustion processing furnace is circulated for hot air heating. The amount of heat transferred from the zone to the hot air sent to the corresponding heating means is maintained. Further, when the output of the heating means in each zone is lower than the set value, the exhaust opening control damper corresponding to that zone is closed to reduce the opening, and the exhaust discharged from the gas combustion processing furnace The amount of heat transferred by the circulating hot air heating heat exchanger to the hot air sent from the zone to the corresponding heating means is reduced. In any of the above cases, in each zone, by controlling the opening and closing of the exhaust balance damper so as to correct and adjust, the air volume does not fluctuate greatly with the opening and closing of the exhaust supply control damper, and a stable air volume is maintained. .
According to claim 18, for each zone divided according to the magnitude of heat demand, according to the temperature of the hot air discharged from the detected heating furnace and the hot air heated by the heating means and recirculated to the heating furnace, By controlling the opening and closing of the exhaust gas supply control damper, the exhaust gas discharged from the gas combustion treatment furnace is supplied to the circulating hot air heating heat exchanger and transferred to the hot air sent from each zone to the corresponding heating means. it can. Therefore, it is possible to efficiently recover and use the heat of the exhaust gas discharged from the gas combustion processing furnace according to the heat demand of a plurality of zones in which the heating furnace is divided and set with a simple configuration. The output of the heating means can be minimized, and the temperature of each zone can be controlled with high responsiveness and high accuracy.

The invention relating to the temperature control method for a heating facility according to claim 19 is the invention according to claim 18, wherein the heat of the exhaust gas discharged from the gas combustion processing furnace is a zone having a high set temperature among the plurality of zones. The heat is supplied to the heat exchanger for heating the circulating hot air in order from each zone, and heat is transferred from each zone to the hot air sent to the heating means.
In the invention of claim 19, when the heat demand differs depending on a plurality of zones divided by the heating furnace, from the gas combustion processing furnace in order from the heat exchanger for heating the circulating hot air corresponding to the zone having the highest heat demand among such zones. The exhausted exhaust can be supplied and transferred as necessary to the hot air sent from each zone to the heating means in turn, thus gas combustion depending on the different heat demands in the zones in the furnace The heat of the exhaust discharged from the processing furnace can be efficiently recovered and used to adjust the temperature of the hot air and supply it to each zone.

The invention related to the temperature control method for a heating facility according to claim 20 is the invention according to claim 18, wherein heat of the exhaust discharged from the gas combustion treatment furnace is used for heat exchange for heating the circulating hot air in the plurality of zones. It is characterized by being distributed and supplied to the vessel in parallel and transferring heat to the hot air sent from each zone to the heating means.
In the invention of claim 20, when the heat demands of the plurality of zones divided by the heating furnace are the same, the heat of the exhaust discharged from the gas combustion processing furnace is paralleled to the heat exchanger for heating the circulating hot air of the plurality of zones. In this way, the exhaust gas discharged from the gas combustion treatment furnace is uniformly supplied to the circulating hot air heating heat exchanger in each zone, and the heat is evenly distributed to the hot air sent from each zone to the heating means as necessary. Therefore, the heat of the exhaust discharged from the gas combustion treatment furnace can be efficiently recovered and used to adjust the temperature of the hot air and supply it to each zone.

The invention related to the temperature control method for a heating facility according to claim 21 is the invention according to any one of claims 13 to 20, wherein the temperature of the hot air discharged from the heating furnace and the hot air to be recirculated to the heating furnace. It measures at least any one of temperature and adjusts the output of the said heating means based on this measurement result, It is characterized by the above-mentioned.
In the invention of claim 21, at least one of the temperature of the hot air discharged from the heating furnace and the temperature of the hot air returned to the heating furnace is measured, and the output of the heating means is adjusted based on the measurement result By doing so, it is possible to accurately adjust the output of the heating means and accurately control the temperature of the hot air to be returned to the heating furnace.

An invention relating to a temperature control method for a heating facility according to a twenty-second aspect is the invention according to any one of the thirteenth to twenty-first aspects, wherein the air volume of the exhaust gas between the gas combustion treatment furnace and the exhaust balance damper is measured. The opening and closing of the exhaust balance damper is controlled based on the measurement result of the exhaust air volume.
In the invention of claim 22, by measuring the air volume of the exhaust gas between the gas combustion treatment furnace and the exhaust balance damper, and controlling the opening and closing of the exhaust balance damper based on the measurement result of the air volume of the exhaust gas, It is embodied that the exhaust discharged from the gas combustion treatment furnace is sent with a stable air volume.

An invention relating to a temperature control method for a heating facility according to a twenty-third aspect is the invention according to the twenty-second aspect, wherein the exhaust gas between the gas combustion treatment furnace and the exhaust balance damper is determined in order to determine whether the exhaust balance damper is opened or closed. An upper limit value and a lower limit value of the air volume are set in advance, and the exhaust balance damper is opened and closed by comparing the measurement result of the measured exhaust air volume with the upper limit value and the lower limit value of the exhaust air volume. It is characterized by controlling.
In the twenty-third aspect of the present invention, in order to determine whether the exhaust balance damper is opened or closed, an upper limit value and a lower limit value of the exhaust gas flow rate between the gas combustion treatment furnace and the exhaust balance damper are set in advance. Then, the measurement result of the measured air volume between the gas combustion treatment furnace and the exhaust balance damper is compared with the upper limit value and the lower limit value of the previously input air volume. When the measurement result of the air volume is lower than the set lower limit value, the exhaust balance damper is controlled to be closed, and the exhaust gas discharged from the gas combustion processing furnace and sent to the circulating hot air heating heat exchanger and the exhaust supply control damper Increase the airflow. When the measurement result of the air volume is higher than the set upper limit value, the exhaust balance damper is controlled to open, and the exhaust gas discharged from the gas combustion processing furnace and sent to the circulating hot air heating heat exchanger and the exhaust supply control damper Reduce the airflow. In addition, when the measurement result of the air volume is in the range from the set lower limit value to the upper limit value, the exhaust balance damper is controlled to close, and the heat exchanger and exhaust gas for heating the circulating hot air discharged from the gas combustion treatment furnace are controlled. Increase the amount of exhaust air sent to the supply control damper. Control is performed by the damper control means to prohibit the operation of the exhaust balance damper. Control the opening and closing of the exhaust balance damper easily and reliably with high responsiveness and high accuracy, and send the exhaust air with a stable air volume in the range between the upper limit value and the lower limit value regardless of the operation of the exhaust supply control damper Can be realized.

The invention relating to a temperature control system for a heating facility according to a twenty-fourth aspect is the invention according to any one of the thirteenth to twenty-third aspects, wherein the opening and closing of the exhaust balance damper is controlled opposite to the opening and closing of the exhaust supply control damper. It is characterized by that.
According to a twenty-fourth aspect of the invention, the damper control means utilizes the fact that the change in the exhaust air volume due to the opening and closing of the exhaust supply control damper is inversely proportional to the change in the exhaust air volume due to the opening and closing of the exhaust balance damper. Control is performed so that the opening / closing operation of the exhaust supply control damper and the opening / closing operation of the exhaust balance damper are reversed. Therefore, the control for opening and closing the exhaust supply control damper and the exhaust balance damper is simplified and facilitated.

BRIEF DESCRIPTION OF THE DRAWINGS It is the block diagram shown notionally in order to demonstrate 1st Embodiment of the temperature control system of the heating equipment of this invention. It is the timing chart shown in order to demonstrate the basic composition of the temperature control method of the heating equipment of the present invention. It is the flowchart shown in order to demonstrate one Embodiment of the temperature control method of the heating equipment of this invention. 3 is a timing chart for explaining opening and closing of a damper by the temperature control method shown in FIG. It is a graph which shows an example of the result of having conducted the experiment of temperature control by the temperature control method shown in FIG. It is the block diagram shown notionally in order to demonstrate 2nd Embodiment of the temperature control system of the heating equipment of this invention. It is the block diagram shown notionally in order to demonstrate 3rd Embodiment of the temperature control system of the heating equipment of this invention. It is the block diagram shown notionally in order to demonstrate 4th Embodiment of the temperature control system of the heating equipment of this invention. Instead of the step (S9) of operating the exhaust balance damper opening / closing degree opposite to that of the exhaust supply control damper shown in the flowchart of FIG. 3, the flow rate of exhaust gas between the deodorizing furnace and the exhaust balance damper is measured. By comparing the measurement result with the upper limit value and the lower limit value of the exhaust gas flow rate between the gas combustion treatment furnace and the exhaust balance damper that are set in advance to determine whether the exhaust balance damper is opened or closed, the exhaust balance It is the timing chart shown in order to demonstrate the algorithm in the case of controlling opening and closing of a damper.

First, a first embodiment of a temperature control system for a heating facility according to the present invention will be described with reference to FIG.
The heating equipment temperature control system according to the present invention generally includes a heating furnace 1 in which hot air of a predetermined temperature is supplied inside, and the hot air discharged from the heating furnace 1 is heated by heating at a predetermined output so as to reach a set temperature. Heating means 2 for refluxing to the furnace 1, control means 3 for controlling the output of the heating means 2 to heat the hot air returning to the heating furnace 1 to a predetermined temperature, hot air discharged from the heating furnace 1 and the heating means 2 Gases for collecting and burning the gases generated in the heating furnace 1 as sensors 4 and 5 as exhaust temperature measuring means and reflux temperature measuring means for detecting the temperature of the hot air that is heated and recirculated to the heating furnace 1, respectively. Combustion treatment furnace 6, heat exchanger 7 for heating the circulating hot air that transfers the heat of the exhaust discharged from gas combustion treatment furnace 6 to the hot air sent from heating furnace 1 to heating means 2, and gas combustion treatment furnace 6 Circulating hot air from the exhaust discharged from The exhaust gas supply control damper 8 for controlling the supply to the heat exchanger 7 and the flow path 32 for sending the exhaust gas discharged from the gas combustion treatment furnace 6 to the circulating hot air heating heat exchanger 7 are circulated. An exhaust balance damper 9 for adjusting the flow rate of exhaust gas sent to the heat exchanger 7 for heating hot air, and a damper control means 10 for controlling the opening and closing of the exhaust supply control damper 8 and the exhaust balance damper 9 based on the output of the heating means 2 I have.
The damper control means 10 compares the output of the heating means 2 with the upper limit value and lower limit value of the output of the heating means 2 set in advance to determine whether the exhaust supply control damper 8 is opened or closed. The opening and closing of the supply control damper 8 is controlled to control the amount of exhaust discharged from the gas combustion treatment furnace 6 to the circulating hot air heating heat exchanger 7 and the opening and closing of the exhaust balance damper 9 is controlled to circulate hot air. The flow rate of the exhaust gas sent to the heating heat exchanger 7 is adjusted.
Furthermore, in this embodiment, the heat exchanger for gas heating that transfers the heat of the exhaust discharged from the gas combustion processing furnace 6 to the gas that is collected from the heating furnace 1 and combusted in the gas combustion processing furnace 6. 11 is provided.
Furthermore, in this embodiment, air addition means 12 for controllably adding air in the atmosphere to the hot air discharged from the heating furnace 1 and sent to the circulating hot air heating heat exchanger 7, and the gas combustion processing furnace 6 For heating the added air, the heat of the exhaust gas transferred to the hot air sent from the heating furnace 1 to the heating means 2 by the heat exchanger 7 for circulating hot air heating is transferred to the air added by the air addition means 12. And a heat exchanger 13.

  The heating furnace 1 in this embodiment constitutes a drying furnace for baking and drying a workpiece W such as an automobile body that has been painted. In the following description, the heating furnace is referred to as a drying furnace 1. In the drying furnace 1, volatile component gas is generated when the paint applied to the workpiece W is dried. Therefore, the gas of the volatile component is collected and deodorized by being burned in the gas combustion treatment furnace 6. In the following description, the gas combustion treatment furnace is referred to as a deodorization furnace 6.

  In the drying furnace 1, a conveying device 15 for conveying the workpiece W in the direction of the arrow, a hot air blowing header 16 for blowing out hot air supplied from the heating means 2, and hot air from the drying furnace 1 are sucked and discharged. A hot air suction header 17 to be sent to the heating means 2 is provided. Collection ducts 18 for collecting gas generated in the drying furnace 1 are provided at the inlet 1 a, the intermediate part 1 b and the outlet 1 c of the drying furnace 1, respectively. Each collection duct 18 is provided with a collection damper 19 in the middle thereof, and is connected to the collection duct 20. The collection duct 20 is connected to the deodorizing furnace 6 with a collection fan 21 and a gas heating heat exchanger 11 interposed in an intermediate portion thereof.

  The hot air blowing header 16 and the hot air suction header 17 are connected by a hot air circulation duct 22. The hot air circulation duct 22 includes a circulating hot air heating heat exchanger 7, an indirect heating furnace heat exchanger 23 of the heating means 2, a circulating hot air filter 24, and a hot air circulation fan 25. Sensors 4 and 5 for detecting the temperature of the hot air are provided in the vicinity of the hot air blowing header 16 and the hot air suction header 17 in the hot air circulation duct 22, respectively.

  In this embodiment, the heating means 2 includes an indirect heating furnace 26 having a burner 26a, an indirect heating furnace heat exchanger 23, a circulating hot air filter 24, and a hot air circulating fan 25. An indirect heating furnace circulation duct 27 is provided between the indirect heating furnace 26 and the indirect heating furnace heat exchanger 23. The indirect heating furnace circulation duct 27 includes an indirect heating furnace circulation fan 28 and an indirect heating furnace circulation air damper. 29 is interposed. An indirect heating furnace exhaust duct 30 is formed by branching an indirect heating furnace circulation duct 27 between the indirect heating furnace circulation fan 28 and the indirect heating furnace circulation air damper 29. An indirect heating furnace exhaust damper 31 is provided in the indirect heating furnace exhaust duct 30.

  The deodorizing furnace 6 includes an auxiliary combustion burner 50 provided therein, a pipe 51 for supplying fuel to the auxiliary combustion burner 50, a deodorizing furnace temperature control valve 52, a deodorizing furnace control unit 53, and a deodorizing furnace control output device. 54 and a deodorizing furnace temperature sensor 55. The temperature in the deodorizing furnace 6 detected by the deodorizing furnace temperature sensor 55 is output to the deodorizing furnace control unit 53, and the output of the auxiliary burner 50 is controlled so that the temperature in the deodorizing furnace 6 becomes a predetermined constant temperature. In addition, the temperature of the deodorizing furnace 6 is high compared with the temperature (for example, set to 80-100 degreeC etc.) of the hot air supplied to the drying furnace 1, such as 800-1000 degreeC, for example.

  An exhaust heat supply duct 32 is connected to the deodorizing furnace 6. The exhaust heat supply duct 32 passes through the gas heating heat exchanger 11, the circulating hot air heating heat exchanger 7, and the additional air heating heat exchanger 13, and the gas heating heat exchanger 11 and the circulating hot air heating. An exhaust heat supply manual damper 33 is interposed between the heat exchanger 7 and the exhaust heat supply control damper 8 on the downstream side of the heat exchanger 13 for heating the added air. Furthermore, the exhaust heat supply duct 32 is branched between the gas heat heat exchanger 11 and the exhaust heat supply manual damper 33 to form an exhaust heat exhaust duct 34. An exhaust balance damper 9 is provided in the exhaust heat exhaust duct 34.

  The air addition means 12 includes an additional air introduction duct 35 that passes through the additional air heating heat exchanger 13, an additional air filter 36, and an additional air adjusting damper 37. The additional air introduction duct 35 is connected between the sensor 4 near the hot air suction head 17 of the hot air circulation duct 22 and the heat exchanger 7 for heating the circulating hot air.

  The control means 3 for controlling the output of the heating means 2 is detected by the fuel supply control valve 41 provided in the pipe 40 and the sensors 4 and 5 for supplying the fuel to the burner 26a of the indirect heating furnace 26 in a controllable manner. The indirect heating furnace control unit 42 that determines the output of the burner 26a of the indirect heating furnace 26 when the temperature of the heated air is input, and the fuel supply control valve 41 is controlled according to the output determined by the drying furnace temperature control unit 42. And an indirect heating furnace control execution unit 43.

  The damper control means 10 receives the control signal of the output of the burner 26a of the indirect heating furnace 26 determined by the indirect heating furnace control unit 42, and determines the opening / closing of the exhaust supply control damper 8 and the exhaust balance damper 9 to exhaust heat supply. A control device 44, an exhaust gas supply control damper open / close control execution device 45 and an exhaust gas balance damper that receive control signals output from the exhaust heat supply control device 44 and control the exhaust gas supply control damper 8 and the exhaust balance damper 9 to open and close, respectively. And an opening / closing control execution device 46.

Next, an embodiment of the temperature control method for a heating facility according to the present invention will be described based on FIGS. 1 to 5 together with its operation depending on the case of using the temperature control device for a heating facility configured as described above. .
The heating equipment according to the present invention generally includes a heating furnace 1 in which hot air having a predetermined temperature is supplied inside, and the hot air discharged from the heating furnace 1 is heated to a set temperature so as to reach a set temperature, and then returned to the heating furnace 1. Heating means 2 for collecting the gas generated in the heating furnace 1 and a gas combustion processing furnace 6 for collecting and burning the gas generated in the heating furnace 1, and is discharged from the gas combustion processing furnace 6 in order to control its temperature. The heat exchanger 7 for heating the circulating hot air that transfers the heat of the exhaust gas to the hot air sent from the heating furnace 1 to the heating means 2 and the heat exchanger 7 for heating the circulating hot air of the exhaust discharged from the gas combustion processing furnace 6 An exhaust supply control damper 8 for controlling the supply to the exhaust gas and an exhaust balance damper 9 for adjusting the flow rate of the exhaust gas discharged from the gas combustion processing furnace 6 and sent to the circulating hot air heating heat exchanger 7 are provided in advance. Based on the output of the means 2, the exhaust supply control unit The heat of the exhaust gas discharged from the gas combustion processing furnace 6 is converted into hot air sent from the heating furnace 1 to the heating means 2 by the circulating hot air heating heat exchanger 7 by controlling the opening and closing of the exhaust 8 and the exhaust balance damper 9. It is possible to transfer heat.
Then, an upper limit value and a lower limit value of the output of the heating means 2 for determining opening / closing of the exhaust supply control damper 8 are set in advance, and an output of the heating means 2 and an upper limit value and a lower limit of the output of the heating means 2 are set. The opening / closing of the exhaust supply control damper 8 is controlled by comparing the value.
Further, the heat of the exhaust discharged from the gas combustion processing furnace 6 is transferred to the gas collected from the heating furnace 1 and combusted in the gas combustion processing furnace 6.
Furthermore, when air in the atmosphere is controllably added to the hot air discharged from the heating furnace 1 and sent to the circulating hot air heating heat exchanger 7, the circulating hot air heating heat exchanger discharged from the gas combustion treatment furnace 6 is used. In step 7, the heat of the exhaust gas transferred to the hot air sent from the heating furnace 1 to the heating means 2 is transferred to the air.

  In this embodiment, as described above, the drying furnace 1 is configured as a heating furnace, the deodorizing furnace 6 is configured as a gas combustion processing furnace, and the heating means 2 is an indirect heating furnace 26 and an indirect heating furnace heat exchanger 23. It has. When baking and drying a workpiece W such as an automobile body that has been painted, the workpiece W is moved by the conveying device 15 in the drying furnace 1 as indicated by an arrow. At this time, hot air heated to a predetermined temperature in the indirect heating furnace heat exchanger 23 is supplied to the hot air blowing head 16 by the hot air circulation fan 25 and supplied into the drying furnace 1, and is provided in the drying furnace 1. Then, the air is sucked from the hot air suction head 17, heated to a predetermined temperature by the indirect heating furnace 26 through the indirect heating furnace heat exchanger 23, and refluxed again into the drying furnace 1. At this time, the gas such as a volatile component generated by heating the workpiece W is collected by the collection fan 18, which is provided at the inlet 1 a, the intermediate portion 1 b and the outlet 1 c of the drying furnace 1. And is collected into the collection duct 20 via the collection damper 19 and sent to the deodorizing furnace 6, where it is burned by the auxiliary burner 50.

  The temperature of the hot air sucked from the hot air suction head 17 of the drying furnace 1 and the temperature of the hot air supplied to the hot air blowing head 16 are detected by the sensors 4 and 5, respectively. Is sent to the indirect heating furnace temperature control unit 42 of the heating control means 3. In the indirect heating furnace temperature control unit 42, the output of the burner 26 a is determined so that the temperature of the hot air supplied to the drying furnace 1 becomes the set temperature, and the control signal is output to the indirect heating furnace control execution unit 43. Thus, the fuel supply control valve 41 is controlled.

  On the other hand, the exhaust gas after burning the collected gas is discharged from the deodorizing furnace 6 through the exhaust heat supply duct 32. In this embodiment, the heat of the exhaust gas discharged from the deodorizing furnace 6 is transferred to the gas supplied to the deodorizing furnace 6 by the collecting duct 20 first by the gas heating heat exchanger 11. Thereby, the gas generated and collected in the drying furnace 1 is supplied to the deodorizing furnace 6 in a state of being heated by the heat exchanger 11 for gas heating before being subjected to the combustion treatment.

  The exhaust balance damper 9 is for supplying the exhaust discharged from the deodorizing furnace 6 to the circulating hot air heating heat exchanger 7 and the like at a stable flow rate (air volume) regardless of the change in the degree of opening / closing of the exhaust supply control damper 8. Is. Therefore, when it is assumed that the exhaust balance damper 9 is maintained at a constant opening without being automatically controlled, when the exhaust supply control damper 8 is opened, the exhaust discharged from the deodorizing furnace 6 is circulated with hot air. The amount passing through the heating heat exchanger 7 and the like decreases. However, at this time, the flow rate of the exhaust discharged from the deodorizing furnace 6 also changes. When the change in the flow rate of the exhaust gas cannot be permitted in the temperature control system of the heating equipment in this way, the open / close degree of the exhaust balance damper 9 is also forcibly changed as the open / close degree of the exhaust supply control damper 8 changes. It is necessary to let Therefore, the opening and closing of the exhaust balance damper 9 is controlled opposite to the opening and closing of the exhaust supply control damper 8, or the downstream of the gas heating heat exchanger 11 in the flow path 32 for sending the exhaust from the deodorizing furnace 6 and the exhaust balance. In order to measure the flow rate of the exhaust gas upstream of the damper 9, a flow rate measuring means 70 composed of a pressure sensor or a wind speed sensor is provided so that the exhaust gas flow rate falls within a preset upper limit value and lower limit value. In addition, the damper control means 10 is configured to control the opening and closing of the exhaust balance damper 9. Exhaust gas discharged from the deodorizing furnace 6 and passing through the gas heating heat exchanger 11 is distributed in two toward the exhaust supply control damper 8 and the exhaust balance damper 9. The exhaust toward one of the exhaust supply control dampers 8 passes through the circulating hot air heating heat exchanger 7, subsequently passes through the additional air heating heat exchanger 13, and is finally released from the exhaust supply control damper 8 to the atmosphere. . The exhaust toward the other exhaust balance damper 9 finally passes through the exhaust balance damper 9 and is released to the atmosphere. As described above, in order to stabilize the flow rate of the exhaust gas discharged from the deodorizing furnace 6, the opening / closing operations of the exhaust supply control damper 8 and the exhaust balance damper 9 are controlled to be contradictory. And compared with the case where it is assumed that the exhaust balance damper 9 is kept at a constant opening degree as described above by controlling the exhaust supply control damper 8 and the exhaust balance damper 9 to the opposite opening and closing operations. Thus, the amount of exhaust from the deodorizing furnace 6 that has flowed out of the gas heating heat exchanger 11 more effectively passes through the circulating hot air heating heat exchanger 7 and the additional air heating heat exchanger 13 (that is, the drying furnace 1). The degree of heating by the circulating hot air heating heat exchanger 7 before the hot air discharged from the heating means 2 is heated and the room temperature air sucked from the added air introduction duct 35 of the air adding means 12 is discharged from the drying furnace 1. The degree of heating by the heat exchanger 13 for heating added air) can be adjusted before adding to the heated air.

  Here, the basic concept of the present invention for adjusting the temperature of the drying furnace 1 by the heating control means 3 and the damper control means 10 that recovers and uses the exhaust heat of the deodorizing furnace 6 is shown in FIGS. Based on

  The exhaust heat supply control device 44 of the damper control means 10 is inputted with the set upper limit value and lower limit value of the output of the burner 26a of the indirect heating furnace 26 determined by the indirect heating furnace temperature control unit 42 of the heating control means 3. Yes. The upper limit value and the lower limit value are for determining whether the exhaust supply control damper 8 is opened or closed, and the heat of the exhaust discharged from the deodorizing furnace 6 corresponding to the opening degree of the exhaust supply control damper 8 is used for heating the circulating hot air. The amount of heat for heating the hot air discharged from the drying furnace 1 by the heat exchanger 7 can be set based on an empirical rule. The exhaust heat supply controller 44 receives the output (A1) of the burner 26a of the indirect heating furnace 26 determined by the indirect heating furnace temperature control unit 42 (S1 in FIG. 3), and the output (A1) is the upper limit value and the lower limit value. (This range is referred to as a “dead zone”) is determined (S2 in FIG. 3). As shown in FIG. 5, the fluctuation of the output (A1) of the burner 26a of the indirect heating furnace 26 for controlling the temperature of the drying furnace 1 is large, and the exhaust supply control damper 8 is opened and closed according to this fluctuation. Output of the control signal (A2) is not only difficult in practice, but also not appropriate for temperature control. Therefore, the exhaust heat supply control device 44 determines the output of the open / close control signal (A2) of the exhaust supply control damper 8 when the output (A1) of the burner 26a is out of the dead zone (YES in S2 of FIG. 3). Has an A1 timer function for delaying. Therefore, when it is determined that the output (A1) of the burner 26a is out of the dead zone (YES in S2 in FIG. 3), the timer has timed up, that is, the state of being out of the dead zone continues. (S3 in FIG. 3) and if the dead zone is re-entered before the time is up (NO in S3 in FIG. 3), the timer is reset and the output (A1) of the burner 26a is again set. The process returns to the determination (S2 in FIG. 3) of whether or not the dead zone is not reached. If the time is up (in the case of YES in S3 in FIG. 3), it is next determined whether the output (A1) of the burner 26a is equal to or lower than the lower limit value of the dead zone (S4 in FIG. 3).

  Here, when the output (A1) of the burner 26a is out of the dead zone (in the case of YES in S2 of FIG. 3), the exhaust heat supply control device 44 is in the middle of FIG. As shown in FIG. 4, pulses for controlling the opening and closing of the exhaust supply control damper 8 are output at regular intervals. When the output (A1) of the burner 26a is out of the dead zone (in the case of YES in S2 in FIG. 3), the output of this pulse is equal to or lower than the lower limit value of the dead zone (in S4 in FIG. 3, YES). In this case, a control signal in a direction to close the exhaust supply control damper 8 is output (for convenience, the control signal in the close direction is set as a negative direction control signal, and the output of the negative direction control signal is referred to as “opening of the exhaust supply control damper 8”. The output pulse is expressed as “subtract.” (Refer to S5 in FIG. 3). If not lower than the lower limit of the dead zone (NO in S4 of FIG. 3, ie, the output (A1) of the burner 26a exceeds the upper limit of the dead zone. In the case where the exhaust gas supply control damper 8 is opened, a control signal in the direction in which the exhaust supply control damper 8 is opened is output (for convenience, the control signal in the closing direction is set as a positive direction control signal, This is expressed as “adding the open output pulse of the exhaust supply control damper 8” (see S6 in FIG. 3). In FIG. 2, a determination delay (time-up by a timer) constitutes between pulses to be output. When the output (A1) of the burner 26a is not out of the dead zone (NO in S2 of FIG. 3), a pulse for controlling the opening / closing of the exhaust supply control damper 8 is provided as shown in FIG. Maintaining or stopping the previous open / closed state without operating the exhaust supply control damper 8 without outputting (for convenience, maintaining the open / closed state is “open output pulse of the exhaust supply control damper 8 = zero”) (See S7 in FIG. 3). By the output of this control signal, as shown in the lower part of FIG. 2, when the output (A1) of the burner 26a exceeds the upper limit value of the dead zone, the exhaust supply control damper 8 is stepped by adding an open output pulse. When the output (A1) of the burner 26a is within the dead zone, the previous state is maintained. When the output (A1) of the burner 26a is equal to or lower than the lower limit of the dead zone, a step is performed by subtracting the open output pulse. Act to close automatically.

  Thereafter, the exhaust heat supply control device 44 updates the opening / closing degree of the exhaust supply control damper 8 (S8 in FIG. 3). In this embodiment, the opening / closing degree of the exhaust balance damper 9 is set to the opening / closing degree of the exhaust supply control damper 8. The reverse operation is performed so as to conflict (S9 in FIG. 3). In this embodiment, since the exhaust supply control damper 8 and the exhaust balance damper 9 are operated independently of each other, the exhaust balance damper 9 is operated contrary to this after the exhaust supply control damper 8 is operated. However, the present invention is not limited to this embodiment, and outputs the control signal of the opposite opening / closing degree to the exhaust balance damper 9 in parallel with the output of the control signal to the exhaust supply control damper 8. Alternatively, the exhaust supply control damper 8 and the exhaust balance damper 9 may be connected to each other so that the degree of opening and closing of the exhaust supply control damper 8 and the exhaust balance damper 9 is reversed. The exhaust balance damper 9 can be also operated in accordance with the operation of 8.

  As described above, when the output (A1) of the burner 26a of the indirect heating furnace 26 exceeds the upper limit value, the exhaust supply control damper 8 is opened and the exhaust balance damper 9 is closed to operate the deodorizing furnace 6 from the deodorizing furnace 6. The amount of exhaust discharged from the exhaust balance damper 9 is reduced and the amount passing through the circulating hot air heating heat exchanger 7 is increased to efficiently recover the exhaust heat of the combustion treatment of the gas generated in the drying furnace 1. Then, heat is transferred to the hot air sent from the drying furnace 1 to the indirect heating furnace heat exchanger 23, and the hot air is appropriately heated before being heated by the indirect heating furnace heat exchanger 23. Therefore, the temperature of the hot air returned to the drying furnace 1 can be accurately controlled and the amount of heating by the burner 26a of the indirect heating furnace 26 can be reduced, so that the fuel cost of the burner 26a is reduced to save energy. be able to. Further, even when fresh air at room temperature is added to the hot air that is provided from the drying furnace 1 and sent to the circulating hot air heating heat exchanger 7 by providing the air addition means 12, the additional air heating heat exchanger 13. However, the heat of the exhaust gas which is discharged from the deodorizing furnace 6 and transferred to the hot air sent from the drying furnace 1 to the heating means 2 by the circulating hot air heating heat exchanger 7 is further added by the air addition means 12 at room temperature. Since the heat is transferred to the air, the heat of the exhaust gas discharged from the deodorizing furnace 6 can be recovered and used more efficiently. Therefore, the temperature of the drying furnace 1 can be controlled with high accuracy and indirectly heated. The output of the burner 26a of the furnace 26 can be minimized.

  On the other hand, when the output (A1) of the burner 26a of the indirect heating furnace 26 is equal to or lower than the lower limit value, the exhaust supply control damper 8 is closed and the exhaust balance damper 9 is opened so that the exhaust from the deodorizing furnace 6 is discharged. By increasing the amount discharged from the exhaust balance damper 9 and decreasing the amount passing through the circulating hot air heating heat exchanger 7, the amount of exhaust heat recovered from the combustion treatment of the gas generated in the drying furnace 1 is reduced. The heat transfer is reduced from the drying furnace 1 to the hot air sent to the indirect heating furnace heat exchanger 23 so as not to be heated. Therefore, the temperature of the hot air returned to the drying furnace 1 can be accurately controlled.

Further, when the output (A1) of the burner 26a of the indirect heating furnace 26 is in the dead band range between the upper limit value and the lower limit value, the exhaust supply control damper 8 and the exhaust balance damper 9 are operated without operating them. The amount of exhaust from the deodorizing furnace 6 is released from the exhaust balance damper 9 and the amount passing through the circulating hot air heating heat exchanger 7 is maintained, and the combustion of the gas generated in the drying furnace 1 is maintained. By recovering the waste heat of the process and transferring it to the hot air sent from the drying furnace 1 to the indirect heating furnace heat exchanger 23, the heating of the hot air before being heated in the indirect heating furnace heat exchanger 23 can be performed. Maintain state. Therefore, while controlling the temperature of the hot air recirculated to the drying furnace 1 with high precision, the amount of heating by the burner 26a of the indirect heating furnace 26 can be reduced, and therefore the temperature of the drying furnace 1 can be controlled with high precision. In addition, the output of the burner 26a of the indirect heating furnace 26 can be minimized.
Note that S9 in FIG. 3 suppresses the change in the flow rate (air volume) of the exhaust gas from the deodorizing furnace 6 in accordance with the opening / closing operation of the exhaust supply control damper 8 so that the heat system of the entire heating equipment becomes unstable. As long as it can be avoided, the exhaust gas between the deodorizing furnace 6 and the exhaust balance damper 9 is replaced with a reverse operation in which the opening / closing degree of the exhaust balance damper 9 is opposite to the opening / closing degree of the exhaust supply control damper 8 as described above. In order to measure the flow rate of the exhaust gas, a flow rate measuring means 70 comprising a pressure sensor or a wind speed sensor is provided, and the control algorithm shown in FIG. 9 is applied to open and close the exhaust balance damper 9. It can also be controlled. Here, a control algorithm for the opening / closing operation of the exhaust balance damper 9 shown in FIG. 9 will be described in comparison with the exhaust supply control damper 8. Control of the opening / closing operation of the exhaust supply control damper 8 is based on the output of the indirect heating furnace 26 determined by the temperature of the hot air. The change in the temperature of the hot air is relatively slow and is delayed from the opening / closing operation of the exhaust supply control damper 8. And it can be said that there is almost no noise contained in the output signal of the indirect heating furnace 26 determined by the indirect heating furnace control unit 42. In contrast, the measured value of the pressure or the wind speed detected by the flow rate measuring means 70 of the exhaust gas flowing through the flow path 32 changes relatively abruptly according to the opening / closing operation of the exhaust gas supply control damper 8, and the flow of the exhaust gas Due to the disturbance, noise in a relatively wide frequency band is always included. Therefore, in order to appropriately open and close the exhaust balance damper 9, as shown in FIG. 9, the dead zone upper limit value and dead zone lower limit value are determined with respect to the pressure or wind speed measurement value detected by the flow rate measuring means 70. In the dead zone, an upper limit operating gap having a width lower than the dead zone upper limit by a predetermined value and a lower limit operating gap having a width higher than the dead zone lower limit by a predetermined value are set. Then, when the measured value of the pressure or wind speed detected by the flow rate measuring means 70 increases from a value below the upper limit operating gap to exceed the dead band upper limit value, a predetermined time after the dead band upper limit value is exceeded by the timer. When the exhaust balance damper 9 is opened after the elapse of time (open rotation is ON), and when it decreases beyond the upper limit operating gap from a value above the upper limit of the dead band, a predetermined time after the dead band upper limit is exceeded by the timer After the elapse of time, the closing operation of the exhaust balance damper 9 is stopped (open rotation OFF). Furthermore, when the measured value of the pressure or wind speed detected by the flow rate measuring means 70 decreases from a value above the lower limit operating gap beyond the dead band lower limit value, a predetermined time after the dead zone lower limit value is exceeded by the timer. When the exhaust balance damper 9 is closed after the elapse of time (closed rotation is ON), and when it increases from a value lower than the dead band lower limit value beyond the lower limit operating gap, a predetermined time is passed after the dead band lower limit value is exceeded by a timer. After the passage, the closing operation of the exhaust balance damper 9 is stopped (closing rotation OFF). As described above, the control algorithm for the opening / closing operation of the exhaust balance damper 9 shown in FIG. 9 is different from the control algorithm for the opening / closing operation of the exhaust supply control damper 8 shown in FIG. Therefore, by applying the control algorithm shown in FIG. 9, chattering due to fine fluctuations in the vicinity of the upper limit value and the lower limit value from the measured value of the exhaust pressure or wind speed detected by the flow rate measuring means 70 is avoided, and the exhaust It is possible to appropriately control the opening and closing of the exhaust balance damper 9 so that the flow rate of the exhaust gas falls within a preset upper limit value and lower limit value.

  Next, a modification of the embodiment shown in FIG. 2 of the temperature control method of the present invention will be described with reference to FIG. In the embodiment shown in FIG. 4, the indirect heating furnace temperature control unit 42 receives the determined output (A1) of the burner 26a of the indirect heating furnace 26 ((a) of FIG. 4). When the output (A1) exceeds the upper limit of the dead zone, the burner output determination unit of the indirect heating furnace temperature control unit 42 until a predetermined time elapses by the determination delay unit (timer) of the indirect heating furnace temperature control unit 42 When the state in which the upper limit value of the dead zone of the output (A1) is exceeded continues, as is referred to in S6 (open output pulse addition) in FIG. 3, the exhaust supply control damper 8 The determination (a1) is the opening direction. Further, when the output (A1) is within the dead band range, the determination (a1) of the exhaust supply control damper 8 is set to zero as referred to S7 (open output pulse = zero) in FIG. Further, when the output (A1) is equal to or lower than the lower limit value of the dead zone, the burner output determination unit of the indirect heating furnace temperature control unit 42 until a predetermined time elapses by the determination delay unit (timer) of the indirect heating furnace temperature control unit 42. When the state of the output (A1) dead band or lower is continued, the determination of the exhaust supply control damper 8 is made as referred to S5 (open output pulse subtraction) in FIG. Let (a1) be the closing direction ((b) of FIG. 4). If the state in which the output of the burner 26a deviates from the dead zone changes while delaying the predetermined time, the timer of the indirect heating furnace temperature control unit 42 is reset, and the delay of the predetermined time from that time again starts again. Be started.

  Further, in the indirect heating furnace temperature control unit 42, as shown in FIG. 4C, the indirect heating furnace temperature control unit 42 generates a pulse P with an on-duty and a period of a predetermined time width, and the output calculation unit is shown in FIG. By performing an operation of multiplying the determination a1 and the pulse P in (b), an open / close control signal A2 of the exhaust heat supply control damper 8 is output with a predetermined time width as shown in FIG. By the output of the opening / closing control signal A2, the exhaust heat supply control damper 8 is opened / closed stepwise as shown in FIG. 4 (e).

  FIG. 5 is a graph showing the results of temperature control according to the present invention when the set temperature of the drying furnace 1 is changed from 85 ° C. to 91 ° C. In FIG. 5, upstream from the branch point of the exhaust heat exhaust duct 34 having the exhaust heat balance damper 9 branched from the flow path 32 for sending the exhaust discharged from the deodorizing furnace 6 and passing through the gas heating heat exchanger 11. The result of having measured the pressure of the exhaust_gas | exhaustion discharged | emitted from the deodorizing furnace 6 by attaching the pressure sensor 70 as a flow volume measurement means is shown. In this case, the exhaust heat supply controller 44 processes the measurement signal of the pressure sensor 70 in accordance with the control algorithm shown in FIG. 9, and the exhaust pressure is, for example, an upper limit value of 0.480 KPa and a lower limit value of 0.450 KPa. The opening and closing of the exhaust balance damper 9 is controlled so as to be within the control range. The left vertical axis is the control temperature of the drying furnace 1, and the right vertical axis is the ratio (%) of the actual output to the total output of the burner 26a of the indirect heating furnace 26 and the exhaust heat supply control damper 8 is fully closed. The actual opening degree (%) with respect to the case where 0% is 100% and fully open is shown. In the embodiment shown in this graph, the upper limit value of the output of the burner 26a is set to 10%, and the lower limit value is set to 5%.

  Similarly to the above-described embodiment, when the output of the burner 26a continues to exceed the upper limit of 10%, the exhaust heat supply control device 44 opens the exhaust heat supply control damper 8 and exhaust heat balance damper 9 The exhaust heat supply control damper 8 and the exhaust heat balance damper are controlled in a state where the output of the burner 26a is in the dead band range of 10% which is the upper limit value and 5% which is the lower limit value. The state up to that time is maintained without operating 9. When the output of the burner 26a continues below the lower limit of 5%, the exhaust heat supply control device 44 controls the exhaust heat supply control damper 8 to close and the exhaust heat balance damper 9 to open. To do.

  In the embodiment shown in FIG. 5, when the temperature of the drying furnace 1 is initially set to 85 ° C., the temperature in the drying furnace 1 can be stably controlled in the range of 85 to 87 ° C. If the temperature of the drying furnace 1 is changed from 85 ° C to 91 ° C in the middle, the actual temperature will be 91 ° C in 1 minute 53 seconds, and then within the range of 90-93 ° C in the drying furnace 1 The temperature could be controlled stably.

Next, 2nd Embodiment of the temperature control system of the heating equipment of this invention is described based on FIG. Note that portions that are the same as or correspond to those in the above-described embodiment are denoted by the same reference numerals, description thereof is omitted, and only different portions are described. Further, in FIG. 6, a part of the configuration of the above-described embodiment is omitted.
In the heating equipment temperature control system in this embodiment, the inside of the drying furnace 1 is roughly divided into a plurality of zones (in FIG. 6, two zones, a temperature raising zone 1A and a temperature holding zone 1B). 1B includes heating means 2A and 2B, circulating hot air heating heat exchangers 7A and 7B, exhaust supply control dampers 8A and 8B, and exhaust balance dampers 9A and 9B, respectively.

  Inside the drying furnace 1, hot air blowing heads 16A, 16B, hot air suction heads 17A, as shown in FIGS. 7 and 8, according to the divided temperature raising zone 1A and temperature holding zone 1B, 17B are provided. The collecting duct 20 for collecting and sending the gas generated in the drying furnace 1 is connected to the deodorizing furnace 6 through the gas heating heat exchanger 11 in the middle thereof. Further, the exhaust heat supply duct 32 for sending the exhaust discharged from the deodorizing furnace 6 is connected to the branched exhaust heat supply ducts 48A and 48B through the gas heating heat exchanger 11 respectively. The exhaust heat supply ducts 48A and 48B are provided with exhaust heat supply control dampers 8A and 8B in the middle of the exhaust heat supply ducts 48A and 48B, and rejoin the exhaust heat supply duct 32 through the circulating hot air heating heat exchangers 7A and 7B. So connected. Further, exhaust balance dampers 9A and 9B are interposed between the branch point and the junction of the exhaust heat supply ducts 48A and 48B of the exhaust heat supply duct 32, respectively.

  The heating means 2A and 2B are respectively heated by hot air sucked from the hot air suction heads 16A and 16B (see FIGS. 7 and 8) in the temperature raising zone 1A and the temperature holding zone 1B (see FIGS. 7 and 8). The hot air circulation ducts 22A and 22B for circulating and supplying to the hot air circulation ducts 22A and 22B, the direct-fired heating furnaces 26A and 26B, and the heat exchanger 7A for heating the circulating hot air, respectively. 7B and hot air circulation fans 25A and 25B. That is, the heating means 2 in the above-described embodiment is configured to include the indirect heating furnace 26 and the indirect heating furnace heat exchanger 23, whereas the heating means 2A and 2B in this embodiment include Direct fire heating furnaces 26A and 26B are provided.

Next, a second embodiment of the temperature control method for a heating facility according to the present invention will be described together with the operation of the system configured as shown in FIG. Note that portions that are the same as or correspond to those in the above-described embodiment are denoted by the same reference numerals, description thereof is omitted, and only different portions are described. Further, FIG. 6 is shown with a part of the configuration of the embodiment described above omitted.
The heating equipment in the present invention is roughly divided into a plurality of zones 1A, 1B in the drying furnace 1, and for each zone 1A, 1B, heating means 2A, 2B and a circulating hot air heating heat exchanger 7A, 7B and exhaust supply control dampers 8A, 8B are provided, and hot air sent from each zone 1A, 1B to heating means 2A, 2B and heating means 2A, 2B according to the temperature set for each zone 1A, 1B. Output of the heating means 2A, 2B is controlled based on the temperature of the hot air recirculated from each of the zones 1A, 1B to the exhaust air supply control dampers 8A, 8B and the exhaust gas based on the outputs of the heating means 2A, 2B. By controlling the opening and closing of the balance dampers 9A and 9B, the circulating hot air heating heat exchangers 7A and 7B corresponding to the zones 1A and 1B respectively control the exhaust gas discharged from the gas combustion processing furnace 6. A drying furnace 1A, heating unit 2A from 1B, makes it possible to respectively heat transfer to the hot air sent to 2B.

  When baking and drying a workpiece W such as an automobile body that has been painted, the workpiece W is moved by the transfer device 15 in the drying furnace 1 from the temperature raising zone 1A to the temperature holding zone 1B. At this time, the hot air heated to the predetermined temperature set according to each zone 1A, 1B by the direct-fired heating furnaces 26A, 26B is heated by the hot air circulation fans 25A, 25B, and the hot air blowing head 16A of each zone 1A, 1B. , 16B (see FIGS. 7 and 8), and is also sucked from hot air suction heads 17A and 17B (see FIGS. 7 and 8) provided in the zones 1A and 1B, and heat for circulating hot air It returns to each zone 1A, 1B again through the exchangers 7A, 7B. The temperature of the hot air sucked from each zone 1A, 1B and the temperature of the hot air recirculated to each zone 1A, 1B are detected, and the output of the burner 26a of the direct fire heating furnaces 26A, 26B is controlled based on this temperature. This is the same as in the above-described embodiment. At the same time, a gas such as a volatile component generated by heating the workpiece W is sent to the deodorizing furnace 6 through the collection duct 20 and is burned by the auxiliary burner 50. And the gas sent to the deodorizing furnace 6 through the collection duct 20 is heated by the heat exchanger 11 for gas heating, and the heat of the exhaust discharged from the deodorizing furnace 6 is transferred to the auxiliary burner. 50 is combusted.

  As shown in FIG. 3, the heating means 2A and 2B corresponding to the zones 1A and 1B respectively determine whether or not the output of the burner 26a of the direct fire heating furnaces 26A and 26B is out of the dead zone ( (See S2 in FIG. 3). When the dead time is out of the dead zone, it is determined whether or not the delay timer has expired (see S3 in FIG. 3). The dampers 8A and 8B are operated to close (see S5 in FIG. 3). If the upper limit of the dead zone is exceeded, the exhaust supply control dampers 8A and 8B are operated to open (S6 in FIG. 3 is changed). In the case of the range between the upper limit value and the lower limit value of the dead zone, the exhaust gas supply control dampers 8A and 8B are maintained without being operated (see S7 in FIG. 3).

  In this embodiment, upstream of the branch point connected to the exhaust heat supply ducts 48 </ b> A and 48 </ b> B of the flow path 32 for sending the exhaust gas discharged from the deodorizing furnace 6 and passing through the heat exchanger 11 for gas heating. A flow rate measuring means 70 comprising a pressure sensor or a wind speed sensor is attached. Further, downstream of each branch point, exhaust heat exhaust ducts 34A and 34B having exhaust heat balance dampers 9A and 9B are branched and connected. Each exhaust heat balance damper 9A, 9B is controlled in its opening / closing operation according to the control algorithm shown in FIG. With this configuration, the flow rate (air volume) of the exhaust gas sent from the deodorizing furnace 6 varies according to the opening / closing operation of the exhaust gas supply control dampers 8A and 8B according to the heat demand of each zone 1A and 1B. Each of these can be controlled so as to be suppressed to a range between the upper limit value and the lower limit value shown in FIG. As a result, the exhaust gas supply control dampers 8A and 8B in the zones 1A and 1B can stabilize the supply of exhaust gas to the heat exchangers 7A and 7B for heating the circulating hot air, thereby improving the temperature control accuracy of the entire heating equipment. it can. In the embodiment shown in FIG. 6 as well, as described in other embodiments described later (see FIGS. 7 and 8), each circulating hot air heating heat exchanger 7A in each zone 1A and 1B is provided. , 7B can also be provided with heat exchangers 13A and 13B for heating additional air, respectively. In this case, the exhaust gas supplied to the heat exchangers 13A and 13B for heating the additional air after passing through the heat exchangers 7A and 7B for heating the circulating hot air can also be stabilized.

Next, a third embodiment of the temperature control system for heating equipment according to the present invention will be described with reference to FIG. Note that portions that are the same as or correspond to those in the above-described embodiment are denoted by the same reference numerals, description thereof is omitted, and only different portions are described.
In the temperature control system of the heating facility in this embodiment, the inside of the drying furnace 1 is divided into a plurality of zones 1A and 1B, as in the embodiment shown in FIG. However, in this embodiment, the names of the zones 1A and 1B are not given names depending on functions and purposes as in the embodiment shown in FIG. 6, but are referred to as the first zone 1A and the second zone 1B for convenience. And The first zone 1A is assumed to have more heat demand than the second zone 1B. In addition, the same code | symbol is attached | subjected about the part similar to the embodiment mentioned above, or the description is abbreviate | omitted, and the same structure in each zone 1A, 1B attaches | subjects A and B after a code | symbol, and distinguishes them. Only the different parts will be described.

  As in the embodiment shown in FIG. 1, the heating means 2A and 2B corresponding to the zones 1A and 1B in this embodiment are connected to the indirect heating furnaces 26A and 26B and the indirect heating furnace heat exchangers 23A and 23B. Each has.

  Further, in this embodiment, the exhaust heat supply duct 32 connected to the deodorizing furnace 6 and passing through the gas heating heat exchanger 11 includes a circulating hot air heating heat exchanger 7A corresponding to the first zone 1A, and additional air. The heating heat exchanger 13A is connected to the exhaust heat supply control damper 8A, the downstream of the gas heating heat exchanger 11 is branched, and is connected to the exhaust heat exhaust duct 34 having the exhaust heat balance damper 9. ing. Further, an exhaust heat exhaust duct 34A is connected to the downstream side of the exhaust heat supply control damper 8A, and the exhaust heat exhaust duct 34A is provided with a surplus exhaust heat damper 68 at the tip and branched in the middle. The exhaust heat supply duct 32B corresponds to the second zone 1B, passes through the circulating hot air heating heat exchanger 7B and the additional air heating heat exchanger 13B corresponding to the second zone 1B, and the exhaust heat supply control damper 8B. It is connected to the. The exhaust heat supply duct 34 </ b> B is connected to the downstream side of the exhaust heat supply control damper 8 </ b> B, and the exhaust heat exhaust duct 34 </ b> B is connected to an excess exhaust heat duct 69 having an excess exhaust heat damper 68. Further, the exhaust heat supply duct 32A and the exhaust heat exhaust duct 34A corresponding to the first zone 1A and the exhaust heat supply duct 32B and the exhaust heat exhaust duct 34B corresponding to the second zone 1B are respectively exhausted. They are connected by pipes 61A and 61B having feed dampers 60A and 60B.

Next, a third embodiment of the temperature control method for a heating facility according to the present invention will be described together with the operation of the heating facility temperature control system configured as shown in FIG. Note that portions that are the same as or correspond to those in the above-described embodiment are denoted by the same reference numerals, description thereof is omitted, and only different portions are described.
As for the heating equipment in the present invention, the inside of the drying furnace 1 is roughly divided into a first zone 1A and a second zone 1B. For each zone 1A, 1B, heating means 2A, 2B, and circulating hot air heating The heat exchangers 7A and 7B are the same as in the embodiment shown in FIG. In this embodiment, since the first zone 1A has a higher heat demand than the second zone 1B, that is, the set temperature is high, the exhaust discharged from the deodorizing furnace 6 corresponds to the first zone 1A. Hot air is supplied to the circulating hot air heating heat exchanger 7A and then supplied to the circulating hot air heating heat exchanger 7B corresponding to the second zone 1B, and sent to the heating means 2A, 2B from each zone 1A, 1B. The exhaust heat of the deodorizing furnace 6 is sequentially transferred to

  When baking and drying a workpiece W such as an automobile body that has been painted, the workpiece W is moved from the first zone 1A to the second zone 1B in the drying furnace 1 by the transport device 15. At this time, the hot air heated to the predetermined temperatures set in the zones 1A and 1B by the indirect heating furnaces 26A and 26B is supplied to the hot air blowing heads 16A and 16B in the zones 1A and 1B by the hot air circulation fans 25A and 25B. In addition to being supplied, the air is sucked from the hot air suction heads 17A and 17B provided in the zones 1A and 1B, and is returned to the zones 1A and 1B again through the circulating hot air heat exchangers 7A and 7B. Sensors 4A, 5A and 4B, 5B detect the temperature of the hot air sucked from each zone 1A, 1B and the hot air returned to each zone 1A, 1B, and based on this temperature, the temperature of indirect heating furnaces 26A, 26B is detected. Controlling the output of each burner 26a is the same as in the above-described embodiment. At the same time, gases such as volatile components generated by heating the workpiece W are supplied to the inlet 1a of the drying furnace 1 and the rear end 1b of the first zone, and to the front end 1b and the outlet 1c of the second zone 1B. They are collected from the respective collecting ducts 18, joined to the collecting duct 20 via the collecting damper 19, sent to the deodorizing furnace 6, and burned by the auxiliary burner 50. And the gas sent to the deodorizing furnace 6 through the collection duct 20 is heated by the heat exchanger 11 for gas heating, and the heat of the exhaust discharged from the deodorizing furnace 6 is transferred to the auxiliary burner. 50 is combusted.

  As shown in FIG. 3, the heating means 2A corresponding to the first zone 1A respectively determines whether or not the output of the burner 26a of the indirect heating furnace 26A is out of the dead zone (see S2 in FIG. 3). ) If it is out of the dead zone, it is determined whether or not the delay timer has expired (see S3 in FIG. 3), and if it is below the lower limit of the dead zone, the exhaust supply control damper 8A is closed. If the upper limit value of the dead zone is exceeded (see S5 in FIG. 3), the exhaust gas supply control damper 8A is operated to open (see S6 in FIG. 3), and between the upper limit value and the lower limit value of the dead zone. In the case of the range, the state up to that point is maintained without operating the exhaust supply control damper 8A (see S7 in FIG. 3).

Thereafter, the heating means 2B corresponding to the second zone 1B determines whether or not the output of the burner 26a of the indirect heating furnace 26A is out of the dead zone as shown in FIG. 3 (S2 in FIG. 3). If it is outside the dead zone, it is determined whether or not the delay timer has expired (see S3 in FIG. 3), and if it is equal to or lower than the lower limit of the dead zone, the exhaust supply control damper 8B is closed. (See S5 in FIG. 3), and when the upper limit value of the dead zone is exceeded, the exhaust gas supply control damper 8B is opened (see S6 in FIG. 3), and the upper and lower limits of the dead zone. In the case of the range, the state up to that point is maintained without operating the exhaust supply control damper 8B (see S7 in FIG. 3).
In this embodiment, the flow path for sending the exhaust discharged from the deodorizing furnace 6 and passing through the gas heating heat exchanger 11 branches to the exhaust heat supply ducts 32A and 32B corresponding to the zones 1A and 1B. A flow rate measuring means 70 comprising a pressure sensor or a wind speed sensor is attached upstream of the branch point 32a. An exhaust heat exhaust duct 34 having an exhaust heat balance damper 9 is branched and connected between the branch point 32a and the flow rate measuring means 70. The exhaust heat balance damper 9 is controlled in its opening / closing operation according to the control algorithm shown in FIG. With this configuration, the flow rate (air volume) of the exhaust gas sent from the deodorizing furnace 6 varies according to the opening / closing operation of the exhaust gas supply control dampers 8A and 8B according to the heat demand of each zone 1A and 1B. Each of these can be controlled so as to be suppressed to a range between the upper limit value and the lower limit value shown in FIG. As a result, the exhaust gas supply control dampers 8A and 8B in the zones 1A and 1B stabilize the supply of exhaust gas to the circulating hot air heating heat exchangers 7A and 7B and the additional air heating heat exchangers 13A and 13B, respectively. The control accuracy of the temperature of the entire equipment can be improved.

  Thus, in this embodiment, the exhaust discharged from the deodorizing furnace 6 is first supplied to the circulating hot air heating heat exchanger 7A corresponding to the first zone 1A having a relatively high heat demand, and then circulated. The exhaust of the deodorizing furnace 6 that has passed through the hot air heating heat exchanger 7A is supplied to the circulating hot air heating heat exchanger 7B corresponding to the second zone 1B where the heat demand is relatively low, that is, the deodorizing furnace 6. The heat of the exhaust gas discharged from the heat from the heat exchanger 7A for circulating hot air heating corresponding to the first zone 1A having a relatively high heat demand is used for heating the circulating hot air corresponding to the second zone 1B having a relatively low heat demand. By supplying the heat to the hot air before being supplied to the exchanger 7B in order and being sent from the zones 1A and 1B of the drying furnace 1 to the heating means 2A and 2B in advance, the first zone 1A and the first zone 2 zone 2A temperature to each setting Flip and can be controlled accurately, also, it is possible to efficiently recover the exhaust heat of the deodorizing furnace 6.

Next, a fourth embodiment of the temperature control system for heating equipment according to the present invention will be described with reference to FIG. Note that portions that are the same as or correspond to those in the above-described embodiment are denoted by the same reference numerals, description thereof is omitted, and only different portions are described.
In the temperature control system for heating equipment in this embodiment, the interior of the drying furnace 1 is divided into a plurality of first zones 1A and second zones 1B, as in the embodiment shown in FIG. However, in the embodiment shown in FIG. 7, the heat demand in the drying furnace 1 is different between the first zone 1A and the second zone 1B, and the heat of the exhaust discharged from the deodorizing furnace 6 is relatively high. The circulating hot air heating heat exchanger 7A corresponding to the first zone 1A having a large demand is configured to be supplied in order to the circulating hot air heating heat exchanger 7B corresponding to the second zone 1B having a relatively small heat demand. On the other hand, in this embodiment, the heat demand in the drying furnace 1 is the same in the first zone 1A and the second zone 1B, and the heat of the exhaust discharged from the deodorizing furnace 6 is changed to the first zone 1A. And a circulating hot air heating heat exchanger 7A corresponding to the second zone 1B and a circulating hot air heating heat exchanger 7B corresponding to the second zone 1B. Heat transfer to hot air sent to 2B And it is configured so as to.

  The heating means 2 corresponding to each zone 1A, 1B in this embodiment includes indirect heating furnaces 26A, 26B and indirect heating furnace heat exchangers 23A, 23B, respectively, as in the embodiment shown in FIG. ing.

  Further, in this embodiment, the exhaust heat supply duct 32 connected to the deodorizing furnace 6 and passing through the gas heating heat exchanger 11 includes a circulating hot air heating heat exchanger 7A corresponding to the first zone 1A, and additional air heating. An exhaust heat supply duct 32A connected to the exhaust heat supply control damper 8A through the heat exchanger 13A, a circulating hot air heating heat exchanger 7B corresponding to the second zone 1B, and an additional air heating heat exchanger 13B. It branches to an exhaust heat supply duct 32B connected to the exhaust heat supply control damper 8B.

Next, a fourth embodiment of the temperature control method for a heating facility according to the present invention will be described together with the operation of the heating facility temperature control system configured as shown in FIG. Note that portions that are the same as or correspond to those in the above-described embodiment are denoted by the same reference numerals, description thereof is omitted, and only different portions are described.
As for the heating equipment in the present invention, the inside of the drying furnace 1 is roughly divided into a first zone 1A and a second zone 1B. For each zone 1A, 1B, heating means 2A, 2B, and circulating hot air heating The heat exchangers 7A and 7B and the exhaust supply control dampers 8A and 8B are provided in the same manner as in the embodiment shown in FIG. In this embodiment, the first zone 1A and the second zone 1B have the same heat demand, and the heat of the exhaust discharged from the deodorizing furnace 6 is heated by circulating hot air corresponding to the first zone 1A. Hot air sent from the zones 1A and 1B to the corresponding heating means 2A and 2B, respectively, distributed and supplied in parallel by the heat exchanger 7A for heating and the circulating hot air heating heat exchanger 7B corresponding to the second zone 1B Heat each.

  When baking and drying a workpiece W such as an automobile body that has been painted, the workpiece W is moved from the first zone 1A to the second zone 1B in the drying furnace 1 by the transport device 15. At this time, the hot air heated to the predetermined temperatures set in the zones 1A and 1B by the indirect heating furnaces 26A and 26B is supplied to the hot air blowing heads 16A and 16B in the zones 1A and 1B by the hot air circulation fans 25A and 25B. While being supplied, the air is sucked from the hot air suction heads 17A and 17B provided in the zones 1A and 1B, and is returned to the zones 1A and 1B again through the circulating hot air heat exchangers 7A and 7B. The temperature of the hot air sucked from each of the zones 1A and 1B and the temperature of the hot air returned to each of the zones 1A and 1B are detected by the sensors 4A, 5A and 4B and 5B, respectively, and the indirect heating furnaces 26A and 26B are detected based on these temperatures. Controlling the output of each burner 26a is the same as in the above-described embodiment.

  At the same time, gases such as volatile components generated by heating the workpiece W are supplied to the inlet 1a of the drying furnace 1, the rear end 1b of the first zone, and the front end 1b and outlet of the second zone 1B. The gas is collected from the collection ducts 18 respectively provided in 1 c, joined to the collection duct 20 through the collection damper 19, sent to the deodorizing furnace 6, and burned by the auxiliary burner 50. And the gas sent to the deodorizing furnace 6 through the collection duct 20 is heated by the heat exchanger 11 for gas heating, and the heat of the exhaust discharged from the deodorizing furnace 6 is transferred to the auxiliary burner. 50 is combusted. The exhaust gas that has been subjected to the combustion treatment and discharged from the deodorizing furnace 6 passes through the exhaust heat supply duct 32 and is divided into branched exhaust heat supply ducts 32A and 32B, and each of the heat exchangers 7A for heating the circulating hot air corresponding to the first zone 1A. Are distributed and supplied in parallel to the second zone 1B and the corresponding circulating hot air heating heat exchanger 7B.

  The heating means 2A, 2B corresponding to each zone 1A, 1B has the output of the burner 26a of the indirect heating furnace 26A determined based on the temperature of the hot air detected by each sensor 4A, 5A and 4B, 5B. The upper limit value and the lower limit value of the dead zone are respectively compared, and based on this comparison, the opening degrees of the exhaust supply control dampers 8A and 8B are determined. On the other hand, the exhaust balance damper 9 is controlled in its opening / closing operation according to the control algorithm shown in FIG. By controlling the opening / closing operation of the exhaust balance damper 9, the flow rate (air volume) of the exhaust sent from the deodorizing furnace 6 can be controlled. As a result, the supply of exhaust gas to the heat exchangers 7A and 7B for heating the circulating hot air and the heat exchangers 13A and 13B for heating the added air by the exhaust gas supply control dampers 8A and 8B in the zones 1A and 1B is stabilized and heated. The control accuracy of the temperature of the entire equipment can be improved. As a result, the exhaust discharged from the deodorizing furnace 6 is distributed and supplied to the circulating hot air heating heat exchangers 7A and 7B through the exhaust heat supply ducts 32A and 32B, respectively, and indirectly from the zones 1A and 1B to the heating means 2A and 2B. It becomes possible to heat the hot air before being sent to the heating furnace heat exchangers 23A and 23B. The exhaust discharged from the deodorization furnace 6 flows through the heat exchangers 7A and 7B for heating the circulating hot air through the exhaust heat supply ducts 32A and 32B, respectively, and then flows into the heat exchangers 13A and 13B for heating the added air. When adding air to the hot air sent from each zone 1A, 1B to the indirect heating furnace heat exchangers 23A, 23B of the heating means 2A, 2B, the air added to the hot air can be preheated, and therefore The temperature of the hot air recirculated to each zone 1A, 1B can be accurately controlled, and the exhaust heat of the deodorizing furnace 6 can be efficiently recovered. Therefore, the indirect heating furnace 26A of the heating means 2A, 2B , 26B can be reduced, and as a result, the amount of fuel sent to the burner 26a can be reduced to save energy.

  The present invention comprises a heating furnace in which hot air of a predetermined temperature is supplied inside as a heating facility, and heating means for heating the hot air discharged from the heating furnace at a predetermined output so as to reach a set temperature and returning it to the heating furnace. As long as it controls the temperature of the heating equipment provided with a gas combustion treatment furnace that collects and burns the gas generated in the heating furnace, it is not limited to the above-described embodiment, For example, the present invention can be applied to a foaming furnace that foams a material by heating.

  1: Drying furnace (heating furnace) 2: Heating means 3: Control means 4, 5: Temperature sensor 6: Deodorizing furnace (gas combustion treatment furnace) 7: Heat exchanger for heating circulating hot air, 8: Exhaust Supply control damper, 9: Exhaust balance damper, 10: Damper control means, 11: Heat exchanger for gas heating, 12: Air addition means, 13: Heat exchanger for heating added air

Claims (24)

A heating furnace in which hot air of a predetermined temperature is supplied;
Heating means for heating the hot air discharged from the heating furnace at a predetermined output so as to be a set temperature, and refluxing the heating air to the heating furnace;
A gas combustion treatment furnace for collecting and burning the gas generated in the heating furnace;
A temperature control system for a heating facility comprising:
A heat exchanger for heating a circulating hot air for transferring the heat of the exhaust discharged from the gas combustion treatment furnace to the hot air sent from the heating furnace to the heating means;
An exhaust supply control damper for controlling supply of the exhaust discharged from the gas combustion treatment furnace to the circulating hot air heating heat exchanger;
An exhaust balance damper provided in a flow path for sending the exhaust discharged from the gas combustion treatment furnace to the circulating hot air heating heat exchanger;
Damper control means for controlling the opening and closing of the exhaust supply control damper based on the output of the heating means, and for controlling the opening and closing of the exhaust balance damper so as to adjust the air volume of the exhaust discharged from the gas combustion processing furnace. And a temperature control system for heating equipment.   The damper control means compares the exhaust supply control by comparing the output of the heating means with an upper limit value and a lower limit value of the output of the heating means set in advance to determine whether the exhaust supply control damper is opened or closed. The heating equipment according to claim 1, wherein opening and closing of the damper is controlled, and opening and closing of the exhaust balance damper is controlled so as to adjust an air volume of exhaust discharged from the gas combustion processing furnace. Temperature control system.   The damper control means adjusts the opening and closing of the exhaust balance damper so that the air volume of the exhaust discharged from the gas combustion treatment furnace is a constant value or a predetermined range. The temperature control system of the heating equipment in any one of 2.   It further comprises a gas heating heat exchanger that collects heat of the exhaust discharged from the gas combustion treatment furnace and transfers the heat to a gas that is collected from the heating furnace and burned in the gas combustion treatment furnace. The temperature control system for a heating facility according to any one of claims 1 to 3. Air addition means for controllably adding air in the atmosphere to hot air discharged from the heating furnace and sent to the circulating hot air heating heat exchanger;
The heat of the exhaust discharged from the gas combustion treatment furnace and transferred to the hot air sent from the heating furnace to the heating means by the circulating hot air heating heat exchanger is transferred to the air added by the air addition means. The temperature control system for a heating facility according to any one of claims 1 to 4, further comprising a heat exchanger for heating added air. The heating furnace is divided into a plurality of zones each supplied with hot air of a predetermined temperature,
The heating equipment according to any one of claims 1 to 5, wherein the heating device, the circulating hot air heating heat exchanger, and the exhaust supply control damper are provided for each zone. Temperature control system.   The heat of the exhaust discharged from the gas combustion treatment furnace is supplied to the circulating hot air heating heat exchanger in order from the zone with the highest heat demand among the plurality of zones, and is sent to the heating means from each zone. The temperature control system for heating equipment according to claim 6, wherein each of the hot air conducts heat.   The heat of the exhaust discharged from the gas combustion processing furnace is distributed and supplied in parallel to the circulating hot air heating heat exchangers of the plurality of zones, and each heat is transferred from each zone to the hot air sent to the heating means. The temperature control system for a heating facility according to claim 6. It comprises at least one of discharge temperature measurement means for measuring the temperature of hot air discharged from the heating furnace and reflux temperature measurement means for measuring the temperature of hot air to be refluxed to the heating furnace,
The output of the heating means is adjusted based on the measurement result of at least one of the discharge temperature measuring means and the reflux temperature measuring means. The temperature control system for a heating facility according to item 1. The flow path for sending the exhaust gas between the gas combustion treatment furnace and the exhaust balance damper to the circulating hot air heating heat exchanger further includes an air volume measuring means for measuring the air volume of the exhaust gas,
The damper control means controls the opening and closing of the exhaust supply control damper based on the output of the heating means, and controls the opening and closing of the exhaust balance damper based on the measurement result of the air volume measuring means. The temperature control system for a heating facility according to any one of claims 1 to 9.   The damper control means includes a measurement result of the exhaust air volume measured by the air volume measuring means, and a gap between the gas combustion treatment furnace and the exhaust balance damper that are set in advance to determine whether the exhaust balance damper is opened or closed. The temperature control system for a heating facility according to claim 10, wherein opening and closing of the exhaust balance damper is controlled by comparing an upper limit value and a lower limit value of an air flow rate of the exhaust gas.   The temperature of the heating equipment according to any one of claims 1 to 11, wherein the damper control means controls the opening and closing of the exhaust balance damper opposite to the opening and closing of the exhaust supply control damper. Control system. A heating furnace in which hot air of a predetermined temperature is supplied;
Heating means for heating the hot air discharged from the heating furnace at a predetermined output so as to be a set temperature, and refluxing the heating air to the heating furnace;
A temperature control method for a heating facility comprising a gas combustion processing furnace for collecting and burning the gas generated in the heating furnace,
A heat exchanger for heating a circulating hot air for transferring the heat of the exhaust discharged from the gas combustion treatment furnace to the hot air sent from the heating furnace to the heating means;
An exhaust supply control damper for controlling supply of the exhaust discharged from the gas combustion treatment furnace to the circulating hot air heating heat exchanger;
An exhaust balance damper that is provided in a flow path for sending the exhaust discharged from the gas combustion treatment furnace to the circulating hot air heating heat exchanger and adjusts the amount of exhaust sent to the circulating hot air heating heat exchanger; ,
Set up
A method for controlling a temperature of a heating facility, wherein opening and closing of the exhaust supply control damper and the exhaust balance damper are controlled based on an output of the heating means. An upper limit value and a lower limit value of the output of the heating means for determining opening / closing of the exhaust supply control damper are set in advance,
By comparing the output of the heating means with the upper limit value and the lower limit value of the output of the heating means, the circulating hot air of the exhaust discharged from the gas combustion processing furnace by controlling the opening and closing of the exhaust supply control damper is controlled. The amount of exhaust gas sent to the heat exchanger for heating the circulating hot air is adjusted by controlling the supply amount to the heating heat exchanger and controlling the opening and closing of the exhaust balance damper. Temperature control method for heating equipment.   The heating equipment according to claim 13 or 14, wherein the opening and closing of the exhaust balance damper is controlled so that the amount of exhaust air sent to the heat exchanger for heating the circulating hot air becomes a constant value or a predetermined range. Temperature control method.   The heat of the exhaust gas discharged from the gas combustion treatment furnace is transferred to the gas collected from the heating furnace and burnt in the gas combustion treatment furnace. The temperature control method of the heating equipment as described in 2. Add controllable air to the hot air discharged from the heating furnace and sent to the circulating hot air heating heat exchanger,
The exhaust heat transferred to the hot air discharged from the gas combustion processing furnace and transferred from the heating furnace to the heating means by the circulating hot air heating heat exchanger is transferred to the air. Item 17. The temperature control method for a heating facility according to any one of Items 13 to 16. The heating furnace is divided into a plurality of zones each supplied with hot air of a predetermined temperature,
For each zone, the heating means, the circulating hot air heating heat exchanger, the exhaust supply control damper and the exhaust balance damper are provided,
According to the temperature set for each zone, the output of the heating means is controlled based on the temperature of the hot air in each zone, and the opening and closing of the exhaust supply control damper is controlled based on the output of the heating means. The amount of exhaust air sent to the circulating hot air heating heat exchanger by controlling the supply amount of the exhaust discharged from the gas combustion treatment furnace to the circulating hot air heating heat exchanger and controlling the opening and closing of the exhaust balance damper The temperature control method for a heating facility according to any one of claims 13 to 17, wherein the temperature is adjusted.   The heat of the exhaust discharged from the gas combustion treatment furnace is supplied to the circulating hot air heating heat exchanger in order from the zone having the highest set temperature among the plurality of zones, and is sent from each zone to the heating means. The temperature control method for heating equipment according to claim 18, wherein heat is transferred to each hot air.   The heat of the exhaust discharged from the gas combustion processing furnace is distributed and supplied in parallel to the circulating hot air heating heat exchangers of the plurality of zones, and each heat is transferred from each zone to the hot air sent to the heating means. The temperature control method for a heating facility according to claim 18. Measure at least one of the temperature of the hot air discharged from the heating furnace and the temperature of the hot air returned to the heating furnace,
The temperature control method for a heating facility according to any one of claims 13 to 20, wherein the output of the heating means is adjusted based on the measurement result. Measuring the air volume of the exhaust gas between the gas combustion treatment furnace and the exhaust balance damper;
The temperature control method for a heating facility according to any one of claims 13 to 21, wherein opening and closing of the exhaust balance damper is controlled based on a measurement result of the air volume of the exhaust. In order to determine the opening and closing of the exhaust balance damper, an upper limit value and a lower limit value of the exhaust air volume between the gas combustion treatment furnace and the exhaust balance damper are set in advance,
23. The heating according to claim 22, wherein opening and closing of the exhaust balance damper is controlled by comparing the measurement result of the measured exhaust air volume with an upper limit value and a lower limit value of the exhaust air volume. Equipment temperature control method.   The temperature control method for a heating facility according to any one of claims 13 to 23, wherein the opening and closing of the exhaust balance damper is controlled in reverse to the opening and closing of the exhaust supply control damper.

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