CN204165066U - Exhaust smoke processing device - Google Patents
Exhaust smoke processing device Download PDFInfo
- Publication number
- CN204165066U CN204165066U CN201420570367.2U CN201420570367U CN204165066U CN 204165066 U CN204165066 U CN 204165066U CN 201420570367 U CN201420570367 U CN 201420570367U CN 204165066 U CN204165066 U CN 204165066U
- Authority
- CN
- China
- Prior art keywords
- heating agent
- bypass line
- heat regenerator
- exhaust
- temperature
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn - After Issue
Links
Landscapes
- Control Of Steam Boilers And Waste-Gas Boilers (AREA)
Abstract
The utility model provides exhaust smoke processing device.Can prevent from becoming corrosive environment in the exhaust flow path in the downstream of heat regenerator, and can by the temperature stabilization of the heating agent flowed in heat regenerator maintain higher state under.When the startup of boiler, after just having lighted a fire, the whole amount of heating agent is circulated to the 2nd heating agent bypass line, when the entrance delivery temperature of heat regenerator uprises, heating agent is made to flow into heating agent pipeloop gradually, after the heating agent amount flowed in entrance water supply piping reaches more than the flow of regulation, when the temperature of the heating agent flowed in entrance water supply piping is lower than set point of temperature, the heating agent flowed in outlet water supply piping is circulated via the entrance side of the 1st heating agent bypass line to heat regenerator, and make the temperature of the heating agent flowed in entrance water supply piping increase, when the outlet exhaust temperatures of heat regenerator is higher than set point of temperature, control, to make heating agent not via the 1st heating agent bypass line.
Description
Technical field
The utility model relates to the exhaust smoke processing device for purifying exhaust gas, and this exhaust is that the combustion apparatus such as the boiler utilized from the thermal power generation system comprising heat power station are discharged.
Background technology
As an example of conventional art, in Fig. 9, represent the system diagram of the wet-exhaust gas treating apparatus in the steam power plant of No. 4725985th, Japan Patent disclosed in publication.In addition, in each figure shown below, identical Reference numeral is marked to identical device.
In fig .9, the exhaust ejected from the boiler etc. be arranged on heat power station, factory etc. is directed to denitrification apparatus 2, after being removed the nitrogen oxide in exhaust, in air preheater 3, carries out heat exchange with the combustion air leading to boiler 1.Then, exhaust is directed to electric cleaner 4, and after being removed the major part of the flue dust in exhaust, utilize Induced fan 5 boost and be directed to desulfurizer 6, the oxysulfide (SOx) in exhaust is removed.Afterwards, exhaust utilize desulfurization blower fan 7 to boost, utilize chimney 8 to be discharged.
In addition, in the configuration shown in fig. 9, the exhaust flow path of the entrance side of electric cleaner 4 is provided with heat regenerator 9, and the water supply line 106 be provided with for supplying water to boiler 1, this water supply line 106 is provided with feed-water heater 100, be provided with the heating agent circulation pipe arrangement 101 connecting heat regenerator 9 and feed-water heater 100, this heating agent circulation pipe arrangement 101 is provided with for making the heating agent bypass heat regenerator 9 of heat regenerator entrance side and makes the heating agent bypass pipe arrangement 102 that heating agent circulates to feed-water heater 100, this heating agent bypass pipe arrangement 102 is provided with flow rate of heat medium control valve 103.
Operated as follows by the exhaust smoke processing device of described Structure composing.
Such method of operation: when the startup of boiler 1, boiler 1 just lighted a fire after, when the ratio deduster 4 of boiler exhaust stream is by dew point lower than the corrosion composition in exhaust of the delivery temperature of upstream side, open flow rate of heat medium control valve 103, make heating agent bypass, make the heat exchange amount that heating agent does not flow into heat regenerator 9 or reduces heating agent influx and reduce in heat regenerator 9, afterwards, even if also reach the stage of more than setting value at the outlet exhaust temperatures carrying out this heat regenerator 9 of recuperation of heat in heat regenerator 9, close the flow rate of heat medium control valve 103 of heating agent bypass pipe arrangement 102, heating agent carry out recuperation of heat by exhaust in heat regenerator 9 after is directed to feed-water heater 100 by heating agent circulation pipe arrangement 101, after having carried out heating to boiler water supply, transfer to the common operating condition being again directed to heat regenerator 9 by this heating agent circulation pipe arrangement 101.
In addition, be known to such structure: on boiler exhaust stream, be provided with heat regenerator, and be provided with the heating agent circulation pipe arrangement (patent document 2, patent document 3) etc. utilizing heating agent (water) thermal cycle of being reclaimed by this heat regenerator to be supplied to boiler blow-down water heater.
Prior art document
Patent document
Patent document 1: Japan Patent No. 4725985 publication
Patent document 2: Japan Patent No. 4959156 publication
Patent document 3: Japanese Unexamined Patent Publication 2011-94962 publication
Utility model content
The problem that utility model will solve
In the exhaust smoke processing device of described prior art, utilize heat regenerator 9 recovery boiler to be vented hot time, be supplied in the process that delivery temperature when boiler startup rises successively heating agent (water supply) temperature of heat regenerator 9 not high, the delivery temperature flowing out heat regenerator 9 is low temperature, and this temperature is also unstable.
Thermal power generation system startup, stop time, the condition of the exhaust ejected from boiler, the heating agent condition using the generating of turbine to utilize do not reach achieve an equilibrium ikn planning mostly.Particularly when starting, heating agent (water) is mostly below plan temperature.On the other hand, though after just starting at thermal power generation system also combustion fuel in the boiler basis on, exhaust also needs to be cooled to plan condition (90 DEG C etc.).In this case, as long as make heating agent bypass and reduce the quantity delivered that heating agent supplies to heat regenerator 9, the outlet exhaust temperatures of heat regenerator 9 just can be controlled in heat calculating, but in fact owing to flowing to that heating agent amount in heat regenerator 9 is less, heating agent amount that is that flow into each heat pipe of heat recovery section 9 produces deviation, cannot carry out heat exchange equably in heat regenerator 9.
Problem of the present utility model is to avoid such situation: the startup of described thermal power generation system, be subject to the impact from the variation of the capacity of thermal power generation system side, delivery temperature and capacity, delivery temperature when stopping and heating agent quantity delivered, heat medium temperature become unstable, thus causing heat regenerator Outlet Gas Temperature to become unstable, wall and the equipment be arranged in this exhaust flow path of the exhaust flow path in heat regenerator and its downstream become corrosive environment.
For the scheme of dealing with problems
Following solution is utilized to solve described problem.
Utility model described in technical scheme 1 is a kind of exhaust smoke processing device, it is characterized in that, deduster (4) and desulfurizer (6) is configured with in order from the upstream side of exhaust flow path, this deduster (4) and desulfurizer (6) are for the treatment of comprising flue dust contained in the exhaust of the burner of boiler (1), oxysulfide, the exhaust flow path of the entrance side of described deduster (4) is provided with heat regenerator (9), be provided with heating agent in relative to described exhaust flow path independently region and utilize equipment (10), be provided with the heating agent pipeloop (11) for utilizing circulation supply heating agent between equipment (10) to heat regenerator (9) and heating agent, and the delivery temperature control valve (CV1) be provided with on this heating agent pipeloop (11) for regulating the delivery temperature in exhaust flow path, heating agent pipeloop (11) is provided with bypass heating agent utilize equipment (10) and make the 1st heating agent bypass line (13) that the heating agent of the outlet side of heat regenerator (9) circulates to the entrance side of heat regenerator (9), 1st heating agent bypass line (13) is provided with the 1st flow rate of heat medium control valve (CV2) and is supplied to the auxiliary pump (17) of entrance side of heat regenerator (9) for the heating agent of the outlet side by heat regenerator (9), and on heating agent pipeloop (11), be provided with bypass heat regenerator (9) and the 1st heating agent bypass line (13) and make heating agent utilize the heating agent of the outlet side of equipment (10) to turn back to the 2nd heating agent bypass line (15) that heating agent utilizes the entrance side of equipment (10), 2nd heating agent bypass line (15) is provided with the 2nd flow rate of heat medium control valve (CV3), be provided with between the connecting portion be connected with the 2nd heating agent bypass line (15) of heating agent pipeloop (11) for the circulating pump (18) supplying heating agent that circulates towards heat regenerator (9), be provided with the 1st exhaust temperature gage (TE1) for measuring delivery temperature in the exhaust flow path of the entrance being arranged on heat regenerator (9), be arranged on the 2nd exhaust temperature gage (TE2) for measuring delivery temperature in the exhaust flow path of the outlet of heat regenerator (9), and for the heat medium temperature meter (TE3) of the heat medium temperature in the heating agent pipeloop (11) of the entrance side of measuring heat regenerator (9).
Utility model described in technical scheme 2 is a kind of exhaust smoke processing device, on the basis of technical scheme 1, it is characterized in that, heating agent pipeloop (11) is provided with bypass heat regenerator (9), 1st heating agent bypass line (13) and the 2nd heating agent bypass line (15) and make heating agent utilize the heating agent of the outlet side of equipment (10) to turn back to the 3rd heating agent bypass line (19) that heating agent utilizes the entrance side of equipment (10), 3rd heating agent bypass line (19) is provided with the 1st open and close valve (21), upstream side heating agent pipeloop (11) respectively with the 2nd heating agent bypass line (15), the 2nd open and close valve (22) is provided with between the coupling part that 3rd heating agent bypass line (19) connects, heating agent pipeloop (11) in downstream respectively with the 2nd heating agent bypass line (15), the 3rd open and close valve (23) is provided with between the coupling part that 3rd heating agent bypass line (19) connects.
The effect of utility model
Adopt the utility model described in technical scheme 1, be provided with when the burner comprising boiler (1) starts, burner utilizes circulation between equipment (10) to supply the heating agent pipeloop (11) of heating agent to heat regenerator (9) and heating agent after just having lighted a fire, and utilize the aperture of the 1st flow rate of heat medium control valve (CV2) and the 2nd flow rate of heat medium control valve (CV3) be arranged at respectively on the 1st heating agent bypass line (13) and the 2nd heating agent bypass line (15), can adjust and flow to two heating agent bypass lines (13, 15) heating agent amount, 1st heating agent bypass line (13) is located at heating agent pipeloop (11) and bypass heating agent utilizes equipment (10) and the heating agent of the outlet side of heat regenerator (9) is circulated to the entrance side of heat regenerator (9).
Like this, adopt the utility model described in technical scheme 1, particularly utilize heat regenerator (9) to retrieve when the exhaust of the burners such as boiler (1) hot when thermal power generation system starts, when heat medium temperature is lower, can while preventing the thermal conductive surface of heat regenerator (9) from corroding because of condensation, the outlet exhaust temperatures of stably maintaining heat recover (9) under the state of plan.
In other words, adopt the utility model, connection heat regenerator (9) and heating agent is utilized to utilize the auxiliary pump (17) between equipment (10) and be provided with the 1st heating agent bypass line (13) of the 1st flow rate of heat medium control valve (CV2), be provided with the 2nd heating agent bypass line (15) of the 2nd flow rate of heat medium control valve (CV3), the running of auxiliary pump (17) and flow rate of heat medium control valve (CV2, CV3), can the plan heating agent internal circulating load of maintaining heat recover (9), simultaneously can relative to the heating agent amount from thermal power generation system brought by the circulating pump (18) be arranged on heating agent pipeloop (11), the change of heat medium temperature realizes the outlet exhaust temperatures of stable heat regenerator (9) and the entrance heat medium temperature of heat regenerator (9) independently, stable startup is realized while can being absorbed in corrosive environment at the wall and the equipment be arranged in this exhaust flow path avoiding the exhaust flow path of heat regenerator (9) and its downstream.
Adopt the utility model described in technical scheme 2, the heat regenerator (9) being used for the heat of the exhaust retrieved from burners such as boilers (1) is set individually, do not adopt the heating medium for heating mechanism that steam drops into, the recovery heat of heat regenerator (9) is applied to boiler water supply, in such system architecture, delivery temperature that the 1st exhaust temperature gage (TE1) in the entrance side of heat regenerator (9) or the exhaust flow path of outlet side or the 2nd exhaust temperature gage (TE2) measure is arranged on lower than the pre-set temperature (dew point of the corrosion composition in exhaust in utilization, such as 90 DEG C) time, the heating agent cyclic system between equipment (10) is utilized to start by making heat regenerator (9) and heating agent under the state making heat regenerator (9) and heating agent utilize the heating agent circulatory system between equipment (10) to be separated, lower in delivery temperature, by the heating agent free convection in the system of heat regenerator (9) after the heating of the heat of the exhaust in exhaust flow path in the start-up course of boiler (1) etc., the inner heating agent of heat regenerator (9) can be suppressed to be locally heated and the danger of flash distillation (gasification), and avoid heat regenerator (9) to become time of corrosive environment elongated situation.
Accompanying drawing explanation
Fig. 1 is the figure of the system of the exhausted smoke processing system representing embodiment 1 of the present utility model.
Fig. 2 is the figure of the detailed construction of the heating agent flow path system of the heat regenerator of the exhausted smoke processing system representing Fig. 1.
Fig. 3 is the figure of the flow chart of the control of the heating agent flow path system of the heat regenerator representing Fig. 1.
Fig. 4 is the figure of another flow chart controlled of the heating agent flow path system of the heat regenerator representing Fig. 1.
Fig. 5 is the figure of the detailed construction of the heating agent flow path system of the heat regenerator of the exhausted smoke processing system representing embodiment 2 of the present utility model.
Fig. 6 is the figure of the flow chart of the control of the heating agent flow path system of the heat regenerator representing Fig. 5.
Fig. 7 is the figure of the flow chart of the control of the heating agent flow path system of the heat regenerator representing Fig. 5.
Fig. 8 is the figure of the detailed construction of the heating agent flow path system of the heat regenerator of the exhausted smoke processing system of the variation represented as embodiment 2 of the present utility model.
Fig. 9 is the figure of the system of the exhausted smoke processing system representing conventional art.
Description of reference numerals
1, boiler; 2, denitrification apparatus; 3, air preheater; 4, electric cleaner; 5, Induced fan; 6, desulfurizer; 7, desulfurization blower fan; 8, chimney; 9, heat regenerator; 10, heating agent utilizes equipment; 11a, entrance water supply piping; 11b, outlet water supply piping; 13, the 1st heating agent bypass line; 15, the 2nd heating agent bypass line; 17,17 ', auxiliary pump; 18, circulating pump; 19, the 3rd heating agent bypass line; 20, control device; 21, the 1st open and close valve; 22, the 2nd open and close valve; 23, the 3rd open and close valve; CV1, delivery temperature control valve; CV2, the 1st flow rate of heat medium control valve; CV3, the 2nd flow rate of heat medium control valve (heating agent bypass flow regulator); TE1, TE2, gas thermometer; TE3, heat medium temperature meter; FX1, the 1st flow rate of heat medium meter; FX2, the 2nd flow rate of heat medium meter.
Detailed description of the invention
Accompanying drawings embodiment of the present utility model.
Embodiment 1
Fig. 1 is the figure of the system of the exhausted smoke processing system representing the present embodiment, Fig. 2 is represent the heat regenerator (gas cooler) 9 be made up of heat pipe group in the exhausted smoke processing system of Fig. 1 and the figure for making heating agent flow into an embodiment of the heating agent flow path system of this heat regenerator 9.In addition, use heating agent to utilize equipment 10 to carry out heat in the system diagram of the exhausted smoke processing system in the past shown in alternate figures 9, utilization exhaust in FIG and carry out the feed-water heater 100 of work, and only some is different from Fig. 9 to utilize between equipment 10 the heating agent flow path system of flowing at the heat regenerator 9 shown in Fig. 1 and heating agent.
As shown in Figure 1 and Figure 2, utilize circulating pump 18 to supply water to heat regenerator 9 via water supply (heating agent) pipe arrangement from watering, after reducing delivery temperature, the water supply that temperature rises is passed out to other heating agent and utilizes equipment 10.In addition, Fig. 1 illustrates the structure being configured with single heat regenerator 9 on the exhaust flow path that flows of exhaust G, but also can adopt the structure of multiple heat regenerator 9 that to be arranged on exhaust flow path.
Be provided with by the entrance water supply piping 11a for supplying heating agent to heat regenerator 9 with for discharging the heating agent pipeloop 11 that the outlet water supply piping 11b that reclaimed hot heating agent is formed from heat regenerator 9, be in heat regenerator 9 inside heat pipe intake section entrance water supply piping 11a on be provided with by regulating flow rate of heat medium to regulate the delivery temperature control valve CV1 of the Outlet Gas Temperature of the heat regenerator 9 of exhaust flow path, for measuring the heat medium temperature meter TE3 of the heat medium temperature in entrance water supply piping 11a, and for the 1st flow rate of heat medium meter FX1 of the flow of measuring the heating agent in the entrance water supply piping 11a in the connecting portion that is between the 1st heating agent bypass line 13 described later and the 2nd heating agent bypass line 15.
Erection is respectively utilized on the entrance water supply piping 11a between equipment 10 and outlet water supply piping 11b to have the 1st heating agent bypass line 13 and the 2nd heating agent bypass line 15 being in heat regenerator 9 and heating agent.Utilize equipment 10 to utilize the 1st heating agent bypass line 13 to link close to the entrance water supply piping 11a of the side of heat regenerator 9 and outlet water supply piping 11b than heating agent, utilize close to heating agent than heat regenerator 9 the entrance water supply piping 11a of the side of equipment 10 and outlet water supply piping 11b to utilize the 2nd heating agent bypass line 15 to link.
1st heating agent bypass line 13 is provided with auxiliary pump 17 and the 1st flow rate of heat medium control valve CV2 for the heating agent from outlet water supply piping 11b being passed out to entrance water supply piping 11a.
In addition, the 2nd heating agent bypass line 15 is provided with for regulating the 2nd flow rate of heat medium control valve CV3 and the 2nd flow rate of heat medium meter FX2 that flow to the bypass amount of the heating agent of outlet water supply piping 11b from entrance water supply piping 11a.
Further, in the heat regenerator 9 being located at boiler exhaust stream, exhaust inlet temperature meter TE1 and exhaust exit temperature meter TE2 is provided with.
In addition, in the present embodiment, the measurement result of whole thermometer TE1, TE2, TE3 and flow rate of heat medium meter FX1, FX2 is sent to control device 20, and control device 20 sends working signal according to the described measured value sent to control valve CV1, CV2, CV3, auxiliary pump 17, circulating pump 18.
In addition, the auxiliary pump 17 being used for the heating agent sent in the 1st heating agent bypass line 13 to entrance water supply piping 11a from outlet water supply piping 11b is configured in the 1st heating agent bypass line 13.
And, the outlet water supply piping 11b of entrance water supply piping 11a with Bi 1 heating agent bypass line 13 downstream of upstream side is not leaned on to carry out the 2nd heating agent bypass line 15 be connected via contrasting the 1st heating agent bypass line 13 when the 1st heating agent bypass line 13 owing to being provided with, therefore, utilize the circulating pump 18 being located at entrance water supply piping 11a that the heating agent in entrance water supply piping 11a is supplied to outlet water supply piping 11b via the 2nd heating agent bypass line 15.
2nd heating agent bypass line 15 is configured with the 2nd flow rate of heat medium control valve CV3,2nd flow rate of heat medium control valve CV3 requires the flow of Signal Regulation heating agent according to the quantity delivered from generation source such as exhaust such as boiler 1 grade, will deduct the heating agent amount used in heat regenerator 9 and the value obtained as the heating agent bypass flow setting value in the 2nd heating agent bypass line 15.The 2nd flow rate of heat medium meter FX2 is utilized to measure while adjust the flow rate of heat medium in the 2nd heating agent bypass line 15.
Namely, when the heating agent bypass flow of pre-set of the flow rate of heat medium flowed the 2nd heating agent bypass line 15 in measured when utilizing the 2nd flow rate of heat medium meter FX2 more than the 2nd heating agent bypass line 15, the 2nd flow rate of heat medium control valve (heating agent bypass flow regulator) CV3 is made to carry out work to closing direction and heating agent bypass flow is reduced, in the 2nd heating agent bypass line 15, the flow rate of heat medium of flowing is less than setting flow, heating agent bypass flow regulator CV3 is made to carry out work to opening direction and heating agent bypass flow is increased, thus the flow rate of heat medium of adjustment flowing in the 2nd heating agent bypass line 15.
In addition, heating agent bypass flow regulator CV3 controls the bypass heating agent amount being fed into entrance water supply piping 11a via the 2nd heating agent bypass line 15, becomes set point of temperature to make the temperature of the heating agent flowed in entrance water supply piping 11a utilizing heat medium temperature TE3 to detect.
In addition, heating agent bypass flow regulator CV3 also has such function: when design temperature higher than heat regenerator 9 of the entrance side of the heat regenerator 9 utilizing thermometer TE1 or TE2 to measure or the delivery temperature (being the mean value of the measured value of each exhaust temperature gage TE1 or TE2 of each heat regenerator 9 when having multiple heat regenerator 9) of outlet side, this heating agent bypass flow regulator CV3 carries out work to closing direction, be adjusted to and the heating agent bypass flow of flowing in the 2nd heating agent bypass line 15 is reduced, when design temperature lower than heat regenerator 9 of the measured value of described thermometer TE1 or TE2, this heating agent bypass flow regulator CV3 carries out work to opening direction, be adjusted to and the heating agent bypass flow of flowing in the 2nd heating agent bypass line 15 is increased.
The described open and close controlling that PI (proportional+integral) controls to carry out heating agent bypass flow regulator CV3 is carried out to the design temperature of the exhaust in heat regenerator 9 and the deviation of actual delivery temperature (measuring tempeature of thermometer TE1 or thermometer TE2).In addition, although not shown, but bypass setting apparatus also can be set and can be good relative to boiler load calibration setup desired temperature.
In addition, utilize the temperature (below sometimes referred to as the inlet temperature of heat regenerator 9) in the exhaust flow path of the intake section of thermometer TE1 measurement heat regenerator 9, or utilize the temperature (below sometimes referred to as the outlet temperature of heat regenerator 9) in the exhaust flow path of the exit portion of thermometer TE2 measurement heat regenerator 9, when this measured value is the following temperature of design temperature (such as 90 DEG C), the heat exchange with heating agent need not be exhausted in heat regenerator 9, therefore, the delivery temperature control valve CV1 being in entrance water supply piping 11a is made to be in closed condition.
In addition, the structure that correspondingly can set arbitrarily the design temperature of the exhaust be configured with in the exhaust flow path of heat regenerator 9 according to boiler load is become.Be adjusted to like this and the mean value of the temperature in the exhaust flow path of the configuration section of heat regenerator 9 is remained on design temperature.
When utilizing heat regenerator 9 to reclaim the boiler exhaust of described structure hot, when delivery temperature when boiler 1 starts is lower, need the exhaust flow path internal cause condensation in the downstream preventing heat regenerator 9 and while corrosion, stably maintain the temperature of the heating agent of flowing in heat regenerator 9.
Therefore, in the process risen when the exhaust of flowing in heat regenerator 9 starts from boiler 1, the delivery temperature of heat regenerator 9 entrance or outlet is below 90 DEG C, even if after the circulating pump 18 of heating agent pipeloop 11 starts, also make delivery temperature control valve CV1 be in closed condition and by the 2nd flow rate of heat medium control valve CV3 standard-sized sheet.
When the entrance delivery temperature of heat regenerator 9 is higher than 90 DEG C, with the aperture pre-set relative to the gasinlet temperature of heat regenerator 9, operation is opened to delivery temperature control valve CV1 by program setting.In addition, although the entrance delivery temperature of heat regenerator 9 raises higher than 90 DEG C, heat regenerator 9 outlet exhaust temperatures lower than 90 DEG C situation (now, the heat medium temperature of the entrance of heat regenerator 9 is lower than design temperature 72 DEG C) under, also delivery temperature control valve CV1 is closed, by the 2nd flow rate of heat medium control valve CV3 standard-sized sheet in the 2nd heating agent bypass line 15, the outlet exhaust temperatures of heat regenerator 9 is made promptly to reach more than 90 DEG C.
And, open the 1st flow rate of heat medium control valve CV2 of the flow for regulating the heating agent in the 1st heating agent bypass line 13, make auxiliary pump 17 carry out work, the heating agent of the outlet of heat regenerator 9 higher for temperature is supplied to the entrance side of heat regenerator 9 via the 1st heating agent bypass line 13 circulation.Like this can promptly improve heat regenerator 9 outlet delivery temperature and prevent the exhaust flow path internal cause condensation in the downstream of heat regenerator 9 and while corrosion, stably to maintain in heat regenerator 9 temperature of the heating agent of flowing.
And, when the outlet exhaust temperatures of heat regenerator 9 is higher than 90 DEG C, not worrying the interior condensation of the boiler exhaust stream in heat regenerator 9 and its downstream, therefore, closing the 1st flow rate of heat medium control valve CV2 of the flow for regulating the heating agent in the 1st heating agent bypass line 13.
The step of the flow-control from the heating agent reaching more than 90 DEG C during described boiler startup to the outlet exhaust temperatures of heat regenerator 9 is described in the flow chart shown in Fig. 3.
First, circulating pump 18 is started, heating agent bypass flow regulator (the 2nd flow rate of heat medium control valve) CV3 being in the 2nd heating agent bypass line 15 is set to standard-sized sheet, make the water supply flow flow in entrance water supply piping 11a be full dose, heating agent flows in the path of the 2nd heating agent bypass line 15 by walking around heat regenerator 9.Secondly, when the delivery temperature utilizing the thermometer TE2 of the thermometer TE1 being arranged at the exhaust entrance of heat regenerator 9 or the air exit being arranged at heat regenerator 9 to measure is below 90 DEG C, the heat exchange that need not be exhausted in heat regenerator 9, therefore, the delivery temperature control valve CV1 being in entrance water supply piping 11a is made to be in closed condition.
When the exhaust exit temperature (utilizing the delivery temperature that thermometer TE1 or thermometer TE2 measures) of the entrance delivery temperature of heat regenerator 9 or heat regenerator 9 higher than 90 DEG C when, delivery temperature control valve CV1 is opened to the aperture of regulation, and closing motion is carried out to the 2nd flow rate of heat medium control valve CV3, by the 2nd flow rate of heat medium control valve CV3 to the direction adjustment of closing, flow in the 2nd heating agent bypass line 15 to make the remainder of the heating agent amount being fed into heat regenerator 9 for carrying out the quantity delivered of self-circulating pump 18.
Now, start first slightly to open delivery temperature control valve CV1, start to close the 2nd flow rate of heat medium control valve CV3 simultaneously.Along with the rising of delivery temperature, the aperture of delivery temperature control valve CV1 becomes large, for carrying out the quantity delivered of self-circulating pump 18, in the 2nd heating agent bypass line 15, the heating agent quantitative change of flowing is few, then, the aperture of regulation is reached at delivery temperature control valve CV1, and the heating agent quantity delivered carrying out self-circulating pump 18 identical with the heating agent amount being fed into heat regenerator 9 when, the 2nd flow rate of heat medium control valve CV3 is by full cut-off.
But, when the heating agent quantity delivered utilizing circulating pump 18 to flow in heating agent pipeloop 11 is greater than the heating agent amount being fed into heat regenerator 9,2nd flow rate of heat medium control valve CV3 maintains the aperture of regulation, makes heating agent be recycled to heating agent via the 2nd heating agent bypass line 15 and utilizes equipment 10.
Then, at utilize the 1st flow rate of heat medium meter FX1 to confirm flow (such as 250m that the heating agent amount flowed in entrance water supply piping 11a reaches regulation
3/ h) more than stage, automatically make the auxiliary pump 17 being located at the 1st heating agent bypass line 13 start, be set to and the heating agent of the outlet side of heat regenerator 9 can be made to flow to the state of the entrance side of heat regenerator 9 via the 1st heating agent bypass line 13.In addition, the auxiliary pump 17 ' of preparation also can be set at the juxtaposed position of auxiliary pump 17.
In addition, make auxiliary pump 17 not for below minimum aperture, do not become full cut-off to make the 1st flow rate of heat medium control valve CV2 in the course of the work.
The work adjustment flow rate of heat medium of the 1st flow rate of heat medium control valve CV2, becomes set point of temperature (such as 72 DEG C) in the temperature making to utilize the 1st heat medium temperature TE3 being located at entrance water supply piping 11a to detect.Namely, when the temperature detected by the 1st heat medium temperature meter TE3 is lower than 72 DEG C, a part for heating agent after being heated by heat regenerator 9 utilizes auxiliary pump 17 to be added to via the 1st heating agent bypass line 13 and supplies via entrance water supply piping 11a the heating agent of coming, and the temperature of the heating agent flowed in entrance water supply piping 11a rises.
Also the 1st flow rate of heat medium control valve CV2 can be set to the state opened, utilizing makes the heating agent after being heated by heat regenerator 9 turn back to the circulating path of heat regenerator 9 via the 1st heating agent bypass line 13 to improve the temperature of heating agent, maintains higher by the outlet exhaust temperatures of heat regenerator 9.
In addition, if the temperature utilizing exhaust exit temperature meter TE1 or TE2 to measure exceeds set point of temperature (2 DEG C) than 90 DEG C, then close the 1st flow rate of heat medium control valve CV2, make the work of auxiliary pump 17 stop or heating agent is kept out of the way to minimal flow pipeline (not shown) simultaneously, by the heating agent after being heated by heat regenerator 9 when not utilizing equipment 10 via being transported to not shown other heating agent when the 1st heating agent bypass line 13, carry out the movement of heat.
In addition, as shown in Figure 4, for the work of described 1st flow rate of heat medium control valve CV2, also can operating the operation after the operation for adjusting flow rate of heat medium as follows, becoming set point of temperature (such as 72 DEG C) in the heat medium temperature making to utilize the 1st heat medium temperature TE3 being located at entrance water supply piping 11a to detect.
Namely, also can be, when the heat medium temperature utilizing the 1st heat medium temperature meter TE3 to detect is lower than 72 DEG C, a part for heating agent after being heated by heat regenerator 9 utilizes auxiliary pump 17 to be added to via the 1st heating agent bypass line 13 and supplies via entrance water supply piping 11a the heating agent of coming, the temperature of the heating agent flowed in entrance water supply piping 11a is made to increase, make the temperature utilizing the 1st heat medium temperature meter TE3 to detect higher than 72 DEG C, when the temperature utilizing the 1st heat medium temperature meter TE3 to detect is higher than 72 DEG C, start the work of closing the 1st flow rate of heat medium control valve CV2, then auxiliary pump 17 is stopped, close the 1st flow rate of heat medium control valve CV2 afterwards.
According to such Fig. 3, a series of action shown in Fig. 4 and utilize heat regenerator 9 recovery boiler to be vented hot time, when delivery temperature when boiler startup is lower, the heating agent of low temperature can not be supplied to heat regenerator 9, therefore, prevent the exhaust flow path internal cause in the downstream of heat regenerator 9 from condensing and corroding, and, when delivery temperature is the state of more than set point of temperature, even if when the temperature utilizing circulating pump 18 to be fed into the heating agent of heat regenerator 9 from heating agent pipeloop 11 is reduced to below set point of temperature, also can not corrode because of condensation in the exhaust flow path in the downstream of heat regenerator 9, simultaneously can by the temperature stabilization of the heating agent of flowing in heat regenerator 9 maintain higher state under.
Embodiment 2
In the exhaust smoke processing device described in described embodiment 1, when boiler 1 starts, 2nd flow rate of heat medium control valve CV3 of the 2nd heating agent bypass line 15 is set to standard-sized sheet, make heating agent at the 2nd heating agent bypass line 15 Inner eycle, when utilizing the delivery temperature of the 1st exhaust temperature gage TE1 or the 2nd exhaust temperature gage TE2 measurement be arranged in the entrance side of heat regenerator 9 or the exhaust flow path of outlet side lower than pre-set temperature (such as 90 DEG C), the delivery temperature control valve CV1 of heating agent pipeloop 11 is made to be in closed condition, but in this period, the heating agent be closed in heat regenerator (gas cooler) 9 is warmed gradually by self-purging recuperation of heat, if reach a certain steady temperature, then there is heating agent flash distillation (gasification) and the hidden danger causing the heat pipe in heat regenerator 9 to damage by water hammer.
Described water hammer can not be there is in the present embodiment, it is the structure for making heat regenerator (gas cooler) 9 runs steadily when boiler startup, it is characterized in that, as shown in Figure 5, the structure shown in Fig. 2 is also provided with the 3rd heating agent bypass line 19.
3rd heating agent bypass line 19 is to set up with the 1st heating agent bypass line 13 and the 2nd heating agent bypass line 15 state arranged side by side the entrance water supply piping 11a that is configured in heating agent pipeloop 11 and to export on water supply piping 11b, with by gas cooler 9, the 1st heating agent bypass line 13 and the 2nd heating agent bypass line 15 all bypass, and utilized by heating agent the heating agent of equipment 10 outlet side to turn back to heating agent to utilize equipment 10 entrance side.
In addition, 3rd heating agent bypass line 19 is provided with the 1st open and close valve 21, and, between the connecting portion that entrance water supply piping 11a is connected with the 2nd heating agent bypass line 15, the 3rd heating agent bypass line 19 respectively, be provided with the 2nd open and close valve 22, between the connecting portion that outlet water supply piping 11b is connected with the 2nd heating agent bypass line 15, the 3rd heating agent bypass line 19 respectively, be provided with the 3rd open and close valve 23.
In addition, the 2nd heating agent bypass line 13 is provided with in the same manner as the structure shown in Fig. 2 the auxiliary pump 17,17 ' of configuration side by side.Further, be provided with between the connecting portion be connected with the 3rd heating agent bypass line 19 of heating agent pipeloop 11 for heating agent to be circulated the circulating pump 18 supplied towards gas cooler 9.
In addition, same with the structure of embodiment 1, in the exhaust flow path being provided with the entrance side being arranged on gas cooler 9 and for measure delivery temperature the 1st exhaust temperature gage TE1, be arranged on gas cooler 9 outlet side exhaust flow path in and for the 2nd exhaust temperature gage TE2 that measures delivery temperature and the heat medium temperature meter TE3 for the heat medium temperature in the heating agent pipeloop 11 of the entrance side of measurement gas cooler 9.
And, same with the structure shown in Fig. 2, when the structure shown in Fig. 5, also the signal measured by exhaust temperature gage TE1, TE2 and heat medium temperature meter TE3 is input to control device 20, outputs signal to flow control valve CV1, CV2, CV3 and open and close valve 21,22,23 from control device 20 according to these information.
Comprise and carried out as follows by the method for operation of the exhaust smoke processing device of the burner of the boiler 1 of described Structure composing.
Adopt the method for operation of such exhaust smoke processing device: when the burner comprising boiler 1 starts, after this burner just lighted a fire,
A 2nd open and close valve 22 and the 3rd open and close valve 23, by the 1st open and close valve 21 standard-sized sheet, are set to full-shut position by (), the circulating pump 18 being in heating agent pipeloop 11 is started, and heating agent is utilized between equipment 10 at the 3rd heating agent bypass line 19 and heating agent and circulates,
B () is arranged on delivery temperature that the 1st exhaust temperature gage TE1 in the entrance side of heat regenerator (gas cooler) 9 or the exhaust flow path of outlet side or the 2nd exhaust temperature gage TE2 measures lower than the pre-set temperature (dew point of the corrosion composition in exhaust in utilization, such as 90 DEG C) time, at the 1st open and close valve 21 standard-sized sheet by the 3rd heating agent bypass line 19, under the state making the 2nd open and close valve 22 of heating agent pipeloop 11 and the 3rd open and close valve 23 maintain full cut-off, open the delivery temperature control valve CV1 of heating agent pipeloop 11, and open the 1st flow rate of heat medium control valve CV2 and the 2nd flow rate of heat medium control valve CV3, make heating agent at the 1st heating agent bypass line 13, Natural Circulation between 2nd heating agent bypass line 15 and heat regenerator 9,
When () delivery temperature in the entrance of heat regenerator 9 utilizing the 1st exhaust temperature gage TE1 or the 2nd exhaust temperature gage TE2 to measure or the exhaust flow path of outlet side is higher than described pre-set temperature (90 DEG C) c, open the 2nd open and close valve 22 and the 3rd open and close valve 23, close the 1st open and close valve 21, start to close the 1st flow rate of heat medium control valve CV2 of the 1st heating agent bypass line 13 and the 2nd flow rate of heat medium control valve CV3 of the 2nd heating agent bypass line 15 simultaneously, utilize the circulation being started heating agent between equipment 10 by heating agent pipeloop 11 at heat regenerator 9 and heating agent.
And, also can substitute described (b) and adopt the method for operation of such exhaust smoke processing device: in the delivery temperature utilizing the 1st exhaust temperature gage TE1 or the 2nd exhaust temperature gage TE2 to measure lower than the pre-set temperature (dew point of the corrosion composition in exhaust, such as 90 DEG C) time, open delivery temperature control valve CV1, and open the 2nd flow rate of heat medium control valve CV3 of the 2nd heating agent bypass line 15, heating agent is circulated between the 2nd heating agent bypass line 15 and heat regenerator (gas cooler) 9, and open the 1st flow rate of heat medium control valve CV2 of the 1st heating agent bypass line 13, circulating pump 17 is started, make heating agent forced circulation between the 1st heating agent bypass line 13 and heat regenerator 9.
When illustrating that in the flow chart shown in Fig. 6 and Fig. 7 the burner comprising boiler 1 starts, burner just lighted a fire after, the step that reaches the flow-control of the heating agent of more than 90 DEG C from the outlet exhaust temperatures to heat regenerator 9 during the boiler startup of the present embodiment 2.
First, the 1st open and close valve 21 being in the 3rd heating agent bypass line 19 is set to standard-sized sheet, 2nd open and close valve 22 of heating agent pipeloop 11 and the 3rd open and close valve 23 are set to full cut-off, circulating pump 18 is started, making the water supply flow in outlet water supply piping 11b utilize the stream of equipment 10 by entrance water supply piping 11a from the 3rd heating agent bypass line 19 via heating agent, heating agent is circulated.
Then, there is the control of the control in accordance with the flow process of Fig. 6 and the flow process in accordance with Fig. 7.
First, the control of the flow process in accordance with Fig. 6 is described.When the delivery temperature utilizing the 1st exhaust temperature gage TE1 that is arranged in the entrance side of gas cooler 9 or the exhaust flow path of outlet side or the 2nd exhaust temperature gage TE2 to measure such as, lower than pre-set temperature the dew point of the corrosion composition in exhaust (, 90 DEG C), open the delivery temperature control valve CV1 of heating agent pipeloop 11, open the 2nd flow rate of heat medium control valve CV3 of the 2nd heating agent bypass line 15, make the heating agent Natural Circulation between gas cooler 9 and the 2nd heating agent bypass line 15 in gas cooler 9.
In addition, when delivery temperature in the entrance side of gas cooler 9 utilizing the 1st exhaust temperature gage TE1 or the 2nd exhaust temperature gage TE2 to measure or the exhaust flow path of outlet side is higher than described pre-set temperature (such as 90 DEG C), 1st open and close valve 21 of the 3rd heating agent bypass line 19 is set to full cut-off, 2nd open and close valve 22 of heating agent pipeloop 11 and the 3rd open and close valve 23 are set to standard-sized sheet, open the delivery temperature control valve CV1 of heating agent pipeloop 11, start to close the 2nd flow rate of heat medium control valve CV3, make at heating agent bypass line 13, in 15, the flow rate of heat medium of flowing tails off gradually.
Like this, when boiler startup, the situation that the delivery temperature time that is lower, that become corrosive environment is elongated can be avoided, and, by the aperture of the delivery temperature control valve CV1 in adjustments of gas chiller system (heat regenerator 9 and heating agent utilize the heating agent circulatory system entirety between equipment 10) and the 2nd flow rate of heat medium control valve CV3, in the start-up course of boiler 1 by the outlet heat extraction of air preheater 3 by the heating agent free convection after heating, the heating agent of gas cooler 9 inside can be suppressed to be locally heated and the danger of flash distillation (gasification).
Then, the control of the flow process in accordance with Fig. 7 is described.
Delivery temperature in the entrance side of gas cooler 9 utilizing the 1st exhaust temperature gage TE1 or the 2nd exhaust temperature gage TE2 to measure or the exhaust flow path of outlet side is lower than the pre-set temperature (dew point of the corrosion composition in exhaust, such as 90 DEG C) time, open the delivery temperature control valve CV1 of heating agent pipeloop 11 and the 2nd flow rate of heat medium control valve CV3 of the 2nd heating agent bypass line 15, and open the 1st flow rate of heat medium control valve CV2 of the 1st heating agent bypass line 13, make water supply (heating agent) at gas cooler 9, circulate between 1st heating agent bypass line 13 and the 2nd heating agent bypass line 15.Now, owing to being provided with circulating pump 17 on the 2nd heating agent bypass line 15, therefore, if make this circulating pump 17 start, then heating agent can be made more swimmingly to utilize between equipment 10 at heat regenerator 9 and heating agent and to circulate.
In addition, when delivery temperature in the entrance side of gas cooler 9 utilizing the 1st exhaust temperature gage TE1 or the 2nd exhaust temperature gage TE2 to measure or the exhaust flow path of outlet side is higher than described pre-set temperature (such as 90 DEG C), 1st open and close valve 21 of the 3rd heating agent bypass line 19 is set to full cut-off, 2nd open and close valve 22 of heating agent pipeloop 11 and the 3rd open and close valve 23 are set to standard-sized sheet, start the opening action of delivery temperature control valve CV1, the circulating pump 17 that work stops, start to close the 1st flow rate of heat medium control valve CV2 and the 2nd flow rate of heat medium control valve CV3 simultaneously, make at heating agent bypass line 13, in 15, the flow rate of heat medium of flowing tails off gradually.
In addition, the auxiliary pump 17 ' of the guest machine of the auxiliary pump 17 as Fig. 5 is substituted by arranging the 2nd flow rate of heat medium control valve CV3 as shown in Figure 8, the 2nd heating agent bypass line 15 can be cancelled, in this case, also can obtain the effect roughly equal with the situation shown in Fig. 5.
Claims (2)
1. an exhaust smoke processing device, is characterized in that,
Deduster (4) and desulfurizer (6) is configured with in order from the upstream side of exhaust flow path, this deduster (4) and desulfurizer (6) are for the treatment of comprising flue dust, oxysulfide contained in the exhaust of the burner of boiler (1)
The exhaust flow path of the entrance side of described deduster (4) is provided with heat regenerator (9),
Be provided with heating agent in relative to described exhaust flow path independently region and utilize equipment (10),
Be provided with the heating agent pipeloop (11) for utilizing circulation supply heating agent between equipment (10) to heat regenerator (9) and heating agent, and the delivery temperature control valve (CV1) be provided with on this heating agent pipeloop (11) for regulating the delivery temperature in exhaust flow path
Heating agent pipeloop (11) is provided with bypass heating agent utilize equipment (10) and make the 1st heating agent bypass line (13) that the heating agent of the outlet side of heat regenerator (9) circulates to the entrance side of heat regenerator (9)
1st heating agent bypass line (13) is provided with the 1st flow rate of heat medium control valve (CV2) and is supplied to the auxiliary pump (17) of entrance side of heat regenerator (9) for the heating agent of the outlet side by heat regenerator (9)
And on heating agent pipeloop (11), be provided with bypass heat regenerator (9) and the 1st heating agent bypass line (13) and make heating agent utilize the heating agent of the outlet side of equipment (10) to turn back to the 2nd heating agent bypass line (15) that heating agent utilizes the entrance side of equipment (10)
2nd heating agent bypass line (15) is provided with the 2nd flow rate of heat medium control valve (CV3),
Be provided with between the connecting portion be connected with the 2nd heating agent bypass line (15) of heating agent pipeloop (11) for the circulating pump (18) supplying heating agent that circulates towards heat regenerator (9),
Be provided with in the exhaust flow path of the entrance being arranged on heat regenerator (9) for measure delivery temperature the 1st exhaust temperature gage (TE1), be arranged on heat regenerator (9) outlet exhaust flow path in for measuring the 2nd exhaust temperature gage (TE2) of delivery temperature and the heat medium temperature meter (TE3) for the heat medium temperature in the heating agent pipeloop (11) of the entrance side of measuring heat regenerator (9).
2. exhaust smoke processing device according to claim 1, is characterized in that,
Heating agent pipeloop (11) is provided with bypass heat regenerator (9), the 1st heating agent bypass line (13) and the 2nd heating agent bypass line (15) and make heating agent utilize the heating agent of the outlet side of equipment (10) to turn back to the 3rd heating agent bypass line (19) that heating agent utilizes the entrance side of equipment (10)
3rd heating agent bypass line (19) is provided with the 1st open and close valve (21),
Between the coupling part be connected with the 2nd heating agent bypass line (15), the 3rd heating agent bypass line (19) respectively of the heating agent pipeloop (11) of upstream side, be provided with the 2nd open and close valve (22), between the coupling part be connected with the 2nd heating agent bypass line (15), the 3rd heating agent bypass line (19) respectively of the heating agent pipeloop (11) in downstream, be provided with the 3rd open and close valve (23).
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2014-113263 | 2014-05-30 | ||
| JP2014113263 | 2014-05-30 | ||
| JP2014-179803 | 2014-09-04 | ||
| JP2014179803A JP2016005830A (en) | 2014-05-30 | 2014-09-04 | Flue gas treatment apparatus, and operational method of flue gas treatment apparatus |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204165066U true CN204165066U (en) | 2015-02-18 |
Family
ID=52538750
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420570367.2U Withdrawn - After Issue CN204165066U (en) | 2014-05-30 | 2014-09-29 | Exhaust smoke processing device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204165066U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105318343A (en) * | 2014-05-30 | 2016-02-10 | 三菱日立电力系统株式会社 | Flue-gas treatment apparatus and operating method thereof |
| CN113028391A (en) * | 2021-04-22 | 2021-06-25 | 烟台龙源电力技术股份有限公司 | Flue gas recirculation system and boiler |
-
2014
- 2014-09-29 CN CN201420570367.2U patent/CN204165066U/en not_active Withdrawn - After Issue
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105318343A (en) * | 2014-05-30 | 2016-02-10 | 三菱日立电力系统株式会社 | Flue-gas treatment apparatus and operating method thereof |
| CN105318343B (en) * | 2014-05-30 | 2018-11-16 | 三菱日立电力系统株式会社 | The method of operation of exhaust smoke processing device and the exhaust smoke processing device |
| CN113028391A (en) * | 2021-04-22 | 2021-06-25 | 烟台龙源电力技术股份有限公司 | Flue gas recirculation system and boiler |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP5523810B2 (en) | Combined cycle power generation facility and its feed water heating method | |
| EP2642092B1 (en) | Method for operating a combined cycle power plant and plant to carry out such a method | |
| JP2007205187A (en) | Heat recovery system attached to boiler-steam turbine system | |
| US9803853B2 (en) | Heat recovery and utilization system | |
| CN101298933B (en) | Method and system for gas humidification control | |
| CN204165066U (en) | Exhaust smoke processing device | |
| US20130199196A1 (en) | System and method for gas turbine part load efficiency improvement | |
| EP2993398B1 (en) | Flue-gas treatment apparatus and its method of operation | |
| KR20120030427A (en) | Heat recovery module | |
| CN105318343A (en) | Flue-gas treatment apparatus and operating method thereof | |
| CZ299279B6 (en) | Method for controlling the level of water in a fuel gas saturator | |
| JP2012057860A (en) | Exhaust heat recovery device | |
| US6813888B2 (en) | Integration construction between a boiler and a steam turbine and method in preheating of the supply water for a steam turbine and in its control | |
| CN110382842A (en) | The control method of Gas Turbine Combined-cycle equipment and Gas Turbine Combined-cycle equipment | |
| EP3754255B1 (en) | Incineration plant for solid material | |
| CA1129276A (en) | Flue gas reheat system | |
| US6951106B2 (en) | Integration construction between a boiler and a steam turbine and method in preheating of the supply water for a steam turbine and in its control | |
| US5315816A (en) | Method and device for temperature control in a combustion plant | |
| JP3670791B2 (en) | Steam supply method and apparatus for coke dry fire extinguishing equipment | |
| RU2698382C1 (en) | Boiler plant | |
| JP7308719B2 (en) | Exhaust heat recovery system | |
| SU1343040A1 (en) | Method of stopping power unit with cooling turbine | |
| JP2007285220A (en) | Combined cycle power generation facility | |
| JP3820636B2 (en) | Method and apparatus for controlling feed water temperature in exhaust recombustion combined cycle plant | |
| KR102010145B1 (en) | Supercritical CO2 Power generation plant |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| ASS | Succession or assignment of patent right |
Owner name: MITSUBISHI HITACHI POWER SYSTEM LTD. Free format text: FORMER OWNER: BABCOCK HITACHI K. K. Effective date: 20150212 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20150212 Address after: Kanagawa Patentee after: Mitsubishi Hitachi Power System Ltd. Address before: Kanagawa Patentee before: Babcock Hitachi K.K. |
|
| AV01 | Patent right actively abandoned |
Granted publication date: 20150218 Effective date of abandoning: 20181116 |
|
| AV01 | Patent right actively abandoned |