JP6303473B2 - Steam pipe loss measurement system and steam pipe loss measurement method - Google Patents

Description

  The present invention relates to a steam pipe loss measurement system and a steam pipe loss measurement method.

  In factories in the industrial field, steam is used for a wide range of applications from heating in production processes to heating and humidification of air conditioning. Steam can cover a wide temperature range from a low temperature range of about 45 ° C. to a high temperature range of about 170 ° C., so to speak, it is an easy-to-use heat medium. For this reason, steam pipes are generally laid in many places in the factory, and steam is generally sent to each production process from a centrally installed boiler.

  FIG. 5 shows a general conceptual diagram of a steam system laid in a factory. Steam produced by a steam production device such as a boiler is sent to a steam header and used for heating in a production process or heating / humidification of an air conditioner. Steam used for various purposes is collected as drain, collected in a return water tank, etc., and then supplied again to the boiler. Further, a plurality of steam traps for discharging drains generated by condensation of steam accompanying heat radiation from the piping are arranged in the middle of the piping.

  In the steam system shown in FIG. 5, the following four losses can be considered with respect to the input fuel energy. (1) Loss of boiler: Loss that becomes apparent by calculating the amount of heat produced by the boiler with respect to the boiler fuel flow (so-called loss associated with boiler efficiency), (2) Loss during air supply (piping): Loss discharged from the steam trap on the pipe due to heat radiation from the pipe, or loss due to leaked steam from the damaged part of the valve or pipe, (3) Trap loss after the load equipment: From the steam trap to collect the drain (4) Loss of recovery: loss from piping to return drain. Temperature drops due to water replenished to prevent pump cavitation when the return water tank is open to the atmosphere, for example. Loss by doing. The energy obtained by subtracting the losses (1) to (4) from the fuel supplied to the boiler is the energy that is effectively used in the production process and air conditioning equipment.

  Loss at the time of air supply (piping) (hereinafter referred to as “piping loss”) includes the following three types of loss. (1) The drain loss is a loss in which the steam in the pipe is condensed and drained along with heat radiation from the pipe and is discharged from the steam trap. (2) The trap leak is a loss in which steam in the pipe leaks simultaneously when the drain trapped by the steam trap is discharged. (3) Leakage such as piping is a loss in which steam leaks due to a gap or physical damage in a piping system including steam piping, valves, flanges, and the like.

  The pipe loss measurement method is as follows. That is, a steam flow meter is installed on each of the pipe inlet side (immediately after the boiler outlet) and the pipe outlet side (immediately before various load facilities), and the loss is calculated based on the comparison of the measurement results. However, in this method, since it becomes possible to measure by directly installing the steam flow meter on the pipe, if the pipe outlet side has a complicated configuration, it is necessary to install a plurality of flow meters. Moreover, it is necessary to cut the existing steam pipes for new installation. In addition, the wetness may not be fully evaluated because not all the moisture (drain) is removed from the steam trap.

As another method for measuring the pipe loss, there is a method using a special device such as a thermography. However, this method is expensive, requires specialized technology for analysis and evaluation of measurement results, and tends to be insufficient in pipe surface temperature measurement accuracy. Evaluation of thermal conductivity of steam pipes or insulation materials. Has problems such as being relatively difficult.
On the other hand, there is provided a method of measuring a steam pipe loss by measuring the amount of evaporation in the steam pipe in this state in an unloaded state in which the internal space of the steam pipe is substantially closed space (for example, Patent Document 1).

Japanese Patent No. 4924762

  In the conventional measuring method, steam is supplied in order to keep the pressure in the steam pipe constant. However, when performing control to make the pressure constant, there is a problem that the measurement accuracy decreases because the pressure fluctuates more than expected.

  An object of the present invention is to provide a measurement system and a steam pipe measurement method capable of measuring a loss of a steam pipe, in particular, a pipe loss with high accuracy in no-load measurement.

According to an aspect of the present invention, a system for measuring a loss of a steam pipe connected to a steam production apparatus and a load facility, the first apparatus creating a substantially closed space including at least a part of the steam pipe; A second device for controlling the amount of steam supplied from the steam producing device into the steam tube so as to keep the pressure in the steam tube substantially constant, and a value relating to the amount of evaporation in the substantially closed space. A third device that measures the pressure of the steam pipe, a fourth device that measures the pressure in the substantially closed space, and a measurement result of the third device and the fourth device. The fifth device calculates a correction coefficient based on the pipe internal temperature of the steam pipe calculated from the pressure measured by the fourth device, and uses the correction coefficient to determine the third device. Correcting the value related to the evaporation amount measured by It measures the loss of the steam pipe.

According to another aspect of the present invention, there is provided a method for measuring a loss of a steam pipe connected to a steam production apparatus and a load facility, wherein the first method creates a substantially closed space including at least a part of the steam pipe. A second step of controlling the amount of steam supplied from the steam producing device into the steam pipe so as to keep the pressure in the steam pipe substantially constant, and the amount of evaporation in the substantially closed space A third step of measuring a value related to the above, a fourth step of measuring a pressure in the substantially closed space, and a value relating to the evaporation amount and a measurement result of the pressure, and measuring the loss of the steam pipe A correction coefficient is obtained based on the internal temperature of the pipe of the steam pipe calculated from the pressure measured in the fourth process, and the third process is performed using the correction coefficient. Correct the value for the evaporation amount measured in the process It measures the loss of the steam pipe by.

  According to this measurement system and measurement method, it is possible to accurately measure a pipe loss even when pressure fluctuation occurs in no-load measurement.

It is the schematic which shows a loss measurement system. It is a schematic diagram which shows a control unit. It is a figure which shows the comparison with a verification test result and a theoretical calculation result. It is the schematic which shows the modification of a loss measurement system. It is a conceptual diagram which shows a general steam system.

Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a schematic diagram showing a loss measurement system 1.
As shown in FIG. 1, the steam pipe 10 is disposed between a steam production apparatus 20 (such as a boiler) and a load facility 30. Steam from the steam production apparatus 20 flows through the steam pipe 10 and is sent to the load facility 30. In the load facility 30, steam or steam heat is used. The steam discharged from the load facility 30 is collected as a drain, collected in the return water tank 25, and then supplied again to the steam production apparatus 20. The steam pipe 10 is heat-retained by heat retention means (not shown). Various known heat retaining means can be applied. The heat retaining means includes, for example, a heat retaining material that covers the outer surface of the steam pipe 10.

  The steam pipe 10 is provided with a plurality of steam traps (drain traps) ST1, ST2, and ST3 that discharge drains generated by condensation of steam accompanying heat radiation in the piping or the like. In FIG. 1, the number of steam traps STn is three. The number of steam traps STn varies depending on equipment specifications. At least a part of the drain generated by condensation in the steam pipe 10 is captured by the steam traps ST1, ST2, and ST3. Various known steam traps are applicable. Normally, the steam traps ST1, ST2 and ST3 have a structure capable of appropriately discharging the captured drain.

  Between the steam production apparatus 20 and the steam trap ST1 in the steam pipe 10, a flow sensor 42 and a pressure sensor (fourth apparatus) 44 are disposed. At least the measurement result of the pressure sensor 44 is sent to the control unit 40. In the steam supply system including the steam production apparatus 20, the supply of steam can be controlled based on the measurement result of the pressure sensor 44 so that the internal pressure of the steam pipe 10 is constant.

  A valve (first device) 27 is disposed near the inlet of the load facility 30 in the steam pipe 10 (between the final steam trap ST3 and the load facility 30). By opening the valve 27, steam from the steam production apparatus 20 can be input to the load facility 30. By closing the valve 27, the steam input from the steam production apparatus 20 to the load facility 30 is shut off.

A flow rate sensor (third device) 46 that measures the amount of water supplied to the steam producing apparatus 20 is disposed near the return water tank 25. The measurement result of the flow sensor 46 is sent to the control unit 40. The control unit (fifth device) 40 can measure the piping loss in the steam pipe 10 based on the measurement results of the flow sensor 46 and the pressure sensor 44 as described later.
As described above, the loss measurement system 1 according to this embodiment includes the valve 27, the flow sensor 42, the pressure sensor 44, the flow sensor 46, and the control unit 40.

  FIG. 2 is a schematic diagram showing the control unit 40. In FIG. 2, the computing device 50 is, for example, a computer system. The control unit 40 includes an input device 127 and a display device (output device) 128 in addition to the calculation device 50. The computing device 50 includes a converter 123 such as an A / D converter, a CPU (arithmetic processing means) 124, a memory 125, and the like. Measurement data sent from a sensor (such as the pressure sensor 44) of the loss measurement system 1 is converted by the converter 123 or the like as necessary, and is taken into the CPU 124. In addition, initial setting values, temporary data, and the like are taken into the computing device 50 via the input device 127 and the like. The display device 128 can display information regarding input data, information regarding calculation, and the like.

  The CPU 124 can execute a calculation related to the loss of the steam pipe 10 based on the measurement data and information stored in the memory 125. For example, the heat loss (pipe loss) of the steam pipe 10 can be calculated using the measurement result of the pressure sensor 44. Hereinafter, an example of a calculation method related to the loss of the steam pipe 10 will be described.

  This measurement method focuses on the amount of water supplied to the steam production apparatus 20 such as a boiler that produces steam. The steam produced by the steam production apparatus 20 is collected after working at various loads while generating a loss. In this measurement method, steam is prevented from flowing into the load facility 30 such as (1) stopping the load facility 30 or (2) closing the valve 27 immediately before the load facility 30. That is, a substantially closed space mainly including the internal space of the steam pipe 10 is created. Hereinafter, this state is appropriately referred to as “no load”. The steam production apparatus 20 supplies steam so as to keep the pressure in the steam pipe 10 constant. This is to supply steam that has been evaporated from the steam pipe 10 and escaped from the steam pipe 10, that is, steam drainage due to heat radiation. Drain is appropriately discharged from the steam traps ST1, ST2, and ST3. If the steam production apparatus 20 is operated in the same manner as in normal times, the amount of water supplied becomes a loss in the piping.

  In the measurement, the amount of water supplied to the steam production apparatus 20 is measured as a value related to the amount of evaporation in a substantially closed space, and the steam pipe is based on the obtained water supply amount and the produced steam properties and the like based on the formula (1). Calculate the loss.

Q = Fw × (hs−C ₀ T _c ) / S (1)

here,
Q: Steam pipe loss (kW)
F _w : Amount of water supply (measured value) (kg)
h _s : saturated steam enthalpy of production steam (kJ / kg)
T _c : Outside air temperature during measurement (environmental temperature) (° C)
S: Measurement time (s)
C ₀ : Specific heat of water (kJ / kg · ° C)

  The amount of steam supplied from the boiler to keep the steam pipe pressure constant when there is no load (when the steam supply to the load equipment is zero) is the amount of drain condensed due to heat dissipation in the steam pipe, or steam leaked from the pipe / valve. The amount is basically equal. In other words, it is considered that the amount of heat lost in the steam pipe can be grasped by measuring the amount of steam generated by the boiler when there is no load. However, it is assumed that the heat transfer coefficient in the pipe is greatly different between no load and normal operation. The validity of using the result of no load as the result of normal operation as it is will be described below.

  Here, the heat transfer coefficient in the pipe during no load and normal operation is calculated, and the degree of influence on the total heat transfer coefficient is examined from the result.

  The following formula (2) shows the basic formula for heat dissipation.

here,
q: Amount of heat dissipated per unit pipe length (W / m),
T ₀ : Pipe internal temperature (pipe steam temperature) (° C),
T ₁ : outside air temperature (atmospheric temperature) (° C.)
α ₁ : In-pipe heat transfer coefficient (W / m ² / ° C.),
α ₂ : heat transfer coefficient from the heat insulating material surface to the atmosphere (W / m ² / ° C.),
λ ₁ : thermal conductivity of heat insulation (W / m / ° C.)
r ₀ : Pipe inner diameter (m),
r ₁ : Piping outer diameter (m),
r ₂ : heat insulation outer diameter (outer diameter of heat insulating material) (m).

Usually, since the heat transfer coefficient in the tube is sufficiently large and does not become a heat transfer resistance, 1 / α ₁ r _{0 in} the above equation (2) is set to zero. However, when evaluating in a no-load state (no flow state), it is considered that the heat transfer coefficient 1 / α ₁ r ₀ cannot be zero because the steam heat flow rate is low and the heat transfer resistance 1 / α ₁ r ₀ is not zero.

  The general formula of heat transfer coefficient in the pipe in forced convection is shown in the following formula (3) from the heat transfer engineering data (revised 4th edition, P55 formulas 29 and 30).

Steam flows in the steam pipe by the amount of drain condensed by heat dissipation. Assuming that the amount of steam supplied from the boiler is 0.48 t / h, the Reynolds number is 3.17 × 10 ⁴ and the above formula is used for calculating the heat transfer coefficient because it is in the turbulent region.

  As a result of calculation, it was found that there was a difference of several percent in the amount of heat dissipation between no load and normal time. When the heat radiation amount is about 20% of the supplied heat amount, the degree of influence on the total heat transfer rate is considered to be slight. A correction coefficient can also be used to reduce the influence.

  An empirical test was conducted on the loss calculation method by measuring the evaporation amount under no load. The measurement results were compared with the theoretical calculation using the above equation (2). In the measurement, a trap checker was used to measure the amount of steam discharged from the steam trap at the same time as the drain discharge, that is, the trap leak. In theoretical calculation, only “drain loss” can be calculated. In actual measurement, “drain loss” and “trapley cross” are mixed. These two losses were separated from the measurement results for accurate verification.

  The comparison results are shown in FIG. As shown in FIG. 3, the theoretical value related to the drain loss and the measured value excluding the trapped cross are almost the same. Regarding drain loss, the measured value is slightly larger, but this seems to be due to the aging of the heat insulating material.

  By the way, in this embodiment, at the time of no-load measurement, the steam production apparatus 20 keeps the pressure in the steam pipe 10 constant, that is, supplies steam so as to become a reference pressure. The pressure control in the steam pipe 10 is performed by, for example, on / off control of the steam production apparatus 20, and the minimum load is about 20%. Therefore, when the pipe loss of the steam pipe 10 is smaller than the minimum load of the steam production apparatus 20, the pressure in the steam pipe 10 is higher than the reference pressure when the steam production apparatus 20 is in the on state, and the steam production apparatus 20 When is turned off, the pressure in the steam pipe 10 becomes lower than the reference pressure. That is, when the pressure in the steam pipe 10 is controlled to be constant, the pressure after the control fluctuates up and down with respect to the reference pressure.

In the steam pipe 10, the saturation temperature also changes with pressure fluctuation. Fluctuation of the saturation temperature in the steam pipe 10 means that T ₀ (pipe internal temperature) represented by the above equation (2) fluctuates. That is, the temperature fluctuation in the steam pipe 10 affects the loss in the steam pipe 10 (steam pipe loss amount Q).

Here, the steam pipe loss Q (hereinafter also referred to as pipe loss Q) obtained from the amount of water supplied to the steam production apparatus 20 defined by the above formula (1) is a constant temperature (reference) in the steam pipe 10. This is based on the assumption that the saturation temperature corresponds to the pressure). Therefore, when applied to a pipe loss in which pressure fluctuation occurs in the steam pipe 10 during no-load measurement, it is necessary to correct based on the pipe temperature fluctuation (pipe internal temperature T ₀ fluctuation) accompanying the pressure fluctuation.

In this measurement method, the pipe loss Q defined by the above equation (1) is corrected using the fluctuation of the pipe internal temperature T ₀ . Specifically, in the present embodiment, the control unit 40 calculates the saturation temperature (pipe internal temperature T ₀ ) in the steam pipe 10 based on the measurement result of the pressure sensor 44, and uses the saturation temperature to set the pipe loss Q. The correction coefficient is obtained. The control unit 40 can obtain the pipe loss Q with high accuracy using the obtained correction coefficient.

  Hereinafter, a method for accurately obtaining the heat loss in the steam pipe 10, that is, the pipe loss, in the no-load measurement by using the pressure measurement value will be described. Specifically, the point of improving the accuracy of the piping loss Q using the correction coefficient will be described.

  In the measurement method of the present embodiment, the pressure sensor 44 measures the pressure in the substantially closed space formed in the steam pipe 10. Moreover, it measures with the flow sensor 46 which measures the amount of water supply to the steam production apparatus 20. The measurement data of the pressure sensor 44 and the flow sensor 46 are sent to the control unit 40. The control unit 40 stores the data transmitted from the pressure sensor 44 and the flow sensor 46 in the memory 125.

  The control unit 40 calculates the saturation temperature in the steam pipe 10 from the information regarding the pressure after a predetermined time has elapsed. Information regarding the saturation temperature is stored in the memory 125.

  As described above, even when the pressure control is performed, the pressure at the time when the predetermined time elapses is different from the reference pressure (high or low). Therefore, the temperature in the steam pipe 10 is different from the saturation temperature corresponding to the reference pressure, and the pipe loss Q calculated only from the measurement data of the flow sensor 46 includes an error.

On the other hand, in this measurement method, the piping loss Q is corrected using the following correction coefficient.
The correction coefficient is defined based on information regarding heat dissipation corresponding to the saturation temperature in the steam pipe 10. Specifically, the correction coefficient includes the theoretical heat release qr obtained by inputting the saturation temperature corresponding to the reference pressure into the above equation (2) and the saturation temperature corresponding to the pressure measured by the pressure sensor 44. It is defined by the ratio (qr / qm) of the actual measurement heat radiation amount qm obtained by inputting into Equation (2).

  In the present embodiment, the ratio (qr / qm) of the theoretical heat radiation amount qr defined by the reference pressure and the heat radiation amount qm defined by the measurement pressure calculated as described above is used as the correction coefficient.

  Subsequently, the piping loss Q obtained using the measurement data of the flow sensor 46 is corrected by multiplying the correction coefficient (qr / qm).

  As described above, according to the present embodiment, the accuracy is improved by correcting the piping loss obtained by the no-load measurement based on the pressure fluctuation. Therefore, highly practical measurement values can be obtained with high accuracy. Further, there is no need to adjust the flow rate of steam generated by the supply of steam or adjustment due to pressure / velocity fluctuation, and the process is simple, so that there is an advantage that no modification of equipment is required.

In the above embodiment, the case where the correction coefficient considering the variation of the temperature in the steam pipe 10 (pipe internal temperature T ₀ ) is used as an example, but the present invention is not limited to this. For example, it may be used a correction factor that takes into account the variation of the ambient temperature T ₁ of the above formula (2). The correction coefficient in this case is obtained by, for example, calculating the theoretical heat release amount qr ′ obtained by inputting the reference outside air temperature into the above equation (2) and the outside air temperature measured by a temperature sensor not shown in the above equation (2). It is defined by the ratio (qr ′ / qm ′) of the actual measurement heat radiation qm ′ obtained by inputting to 2).

  In the above embodiment, the case of correcting the pipe loss Q over time has been described as an example, but the present invention is not limited to this. For example, the pipe loss Q that has occurred in a certain period of time may be corrected. In this case, the correction coefficient is defined as follows.

  First, the heat dissipation amount q defined by the above formula (2) is obtained every unit time (for example, every second), and as shown in the following formula (4), the total heat dissipation amount Q is obtained by adding these. Can be sought.

  The correction coefficient corresponds to the theoretical integrated heat release amount Qr obtained by inputting the saturation temperature corresponding to the reference pressure into the above equation (4) every unit time and the pressure per unit time measured by the pressure sensor 44. This is defined by the ratio (Qr / Qm) of the actual heat radiation amount Qm obtained by inputting the saturation temperature to the above equation (4).

  For example, when it takes 100 seconds for pipe loss measurement, for example, the integrated heat radiation amount Qm is obtained by adding the heat radiation amount q obtained from the saturation temperature corresponding to each measurement pressure in 1 to 100 seconds. Since the reference pressure is constant during pipe loss measurement, the integrated heat dissipation amount Qr is obtained by 100 × qr. Moreover, when calculating | requiring integrated heat radiation amount Qm, you may make it use a time average value as a measurement pressure, or may use a time average value as a saturation temperature corresponding to measurement pressure.

  Subsequently, by multiplying the correction coefficient (Qr / Qm), it is possible to correct the pipe loss Q generated in a certain time obtained using the measurement data of the flow sensor 46.

  In the above embodiment, the valve opening / closing control may be automatic or manual. Periodic loss measurement can be performed to verify damage to piping systems and deterioration of heat insulation performance.

  FIG. 4 shows a modification of the loss measurement system. In FIG. 4, a plurality of steam lines 10A, 10B, and 10C corresponding to the plurality of load facilities 30A, 30B, and 30C are provided. The steam line 10A corresponding to the load facility 30A includes a plurality of steam traps STA1, STA2, and STA3, a pressure sensor 44A, a flow rate sensor 42A, and a valve 27A. Similarly, the steam line 10B corresponding to the load facility 30B includes a plurality of steam traps STB1, STB2, STB3, a pressure sensor 44B, a flow rate sensor 42B, and a valve 27B, and the steam line 10C corresponding to the load facility 30C. Includes a plurality of steam traps STC1, STC2, STC3, a pressure sensor 44C, a flow rate sensor 42C, and a valve 27C. The valves 27A, 27B, and 27C are respectively near the entrance of the load facility 30A (30B and 30B) in the steam line 10A (10B and 10C) (the final steam trap STA3 (STB3 and STC3) and the load facility 30A (30B and 30B). Between).

  In FIG. 4, the loss of the entire steam system can be calculated by closing all the valves 27A, 27B, and 27C. In this case, as a value related to the amount of evaporation in a substantially closed space, the amount of water supplied to the steam production apparatus 20 is measured by the flow rate sensor 46, and the loss in the steam pipe is determined from the obtained amount of water and the produced steam properties. Can be calculated. Alternatively, the loss in the steam pipe can be calculated by measuring the amount of fuel used in the steam production apparatus 20 as a value related to the amount of evaporation in a substantially closed space. Moreover, the pressure fluctuations in the substantially closed space are measured by the pressure sensors 44A, 44B, 44C, and the pipe loss in each of the steam lines 10A, 10B, 10C is obtained with high accuracy using the correction coefficient as in the above embodiment. be able to.

  Further, by closing the valve 27A and opening the valves 27B and 27C, the loss of the steam line 10A corresponding to the load facility 30A can be calculated during the operation of the load facilities 30B and 30C. In this case, the loss in the steam line can be calculated by directly measuring the steam flow rate in the target steam line by the flow rate sensor 42A as a value related to the evaporation amount in the substantially closed space. Further, by directly measuring the pressure change in the substantially closed space by the pressure sensor 44A, it is possible to accurately obtain the pipe loss using the correction coefficient corresponding to the steam line 10A.

  Note that the heat dissipation amount q (W / m) per unit pipe length obtained from the measurement results is a value under the pipe diameter and the heat insulation diameter at the measurement point. You may spend it.

The size and heat insulation thickness of the steam pipe in the steam system may vary depending on the steam conditions (amount of steam used, pressure, temperature) of the load equipment. Even in such a case, if the heat radiation amount of a certain steam pipe is known, it is possible to obtain the heat radiation amount by performing correction based on differences in the pipe size, the insulation thickness, the pipe internal temperature, and the outside air temperature. is there. A correction calculation formula (5) for calculating a heat radiation amount corresponding to another pipe size and heat insulation thickness from a known heat radiation amount is shown below. This equation (5) can be derived from the above theoretical equation (2).
In the correction calculation formula (4), q ″: heat radiation amount per unit length (W / m) in another pipe, r1 ′: pipe outer diameter (m) of another pipe, r2 ′: another pipe Thermal insulation outer diameter (outer diameter of heat insulating material) (m), T0 ′: Internal temperature of another pipe (supply steam temperature) (° C.), T1 ′: Outside air temperature (air temperature) of another pipe (° C.) is there.

  As mentioned above, although embodiment of this invention was described, this invention is not limited to this embodiment. The numerical value used in the above description is an example, and the present invention is not limited to this. Additions, omissions, substitutions, and other modifications can be made without departing from the spirit of the present invention.

DESCRIPTION OF SYMBOLS 1 ... Loss measurement system, 10 ... Steam pipe, 20 ... Steam production apparatus, 27 ... Valve (1st apparatus), 30 ... Load equipment, 40 ... Control unit (2nd apparatus, 5th apparatus), 44 ... Pressure sensor ( 4th apparatus), 46 ... Flow sensor (3rd apparatus).

Claims (6)

A system for measuring the loss of steam pipes connected to steam production equipment and load equipment,
A first device for creating a substantially closed space including at least a portion of the steam pipe;
A second device for controlling the amount of steam supplied from the steam producing device into the steam pipe so as to keep the pressure in the steam pipe substantially constant;
A third device for measuring a value relating to the amount of evaporation in the substantially closed space;
A fourth device for measuring the pressure in the substantially closed space;
Using a measurement result of the third device and the fourth device, a fifth device for measuring the loss of the steam pipe ,
The fifth device obtains a correction coefficient based on the pipe internal temperature of the steam pipe calculated from the pressure measured by the fourth device, and relates to the evaporation amount measured by the third device using the correction coefficient. loss measurement system of the steam pipe, characterized that you measure the loss of the steam pipe by correcting the values.   The said first device includes at least one of a means for stopping the load equipment and a means for closing a valve disposed in the steam pipe in the vicinity of an inlet of the load equipment. The described loss measurement system.   The third device comprises: means for measuring the amount of water supplied to the steam producing device; means for measuring the amount of fuel used in the steam producing device; and means for directly measuring the steam flow rate in the substantially closed space. The loss measurement system according to claim 1, comprising at least one. A method for measuring a loss of a steam pipe connected to a steam production apparatus and a load facility,
A first step of creating a substantially closed space including at least a portion of the steam pipe;
A second step of controlling the amount of steam supplied from the steam production apparatus into the steam pipe so as to keep the pressure in the steam pipe substantially constant;
A third step of measuring a value relating to the amount of evaporation in the substantially closed space;
A fourth step of measuring the pressure in the substantially closed space;
Using a value related to the amount of evaporation and a measurement result of the pressure, and a fifth step of measuring the loss of the steam pipe ,
In the fifth step, a correction coefficient is obtained based on the internal temperature of the steam pipe calculated from the pressure measured in the fourth step, and the evaporation amount measured in the third step using the correction coefficient. loss measuring method of the steam pipe, characterized that you measure the loss of the steam pipe by correcting the values.   5. The method according to claim 4, wherein the first step includes at least one of a step of stopping the load facility and a step of closing a valve disposed in the steam pipe in the vicinity of an inlet of the load facility. The loss measuring method of the steam pipe of description.   The third step includes a step of measuring a water supply amount to the steam production device, a step of measuring a fuel usage amount in the steam production device, and a step of directly measuring a steam flow rate in the substantially closed space. The loss measurement method according to claim 4 or 5, wherein at least one is included.

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