JP2013061071A - Suppressing method for piston inclination in gas holder - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress the inclination of a piston by properly controlling the force of pressing a side plate when the piston is to be held horizontally by pressing the side plate of a gas holder with a guide roller installed at the periphery of the piston.SOLUTION: The piston 6 of the gas holder includes a plurality of guide roller units arranged at predetermined intervals in the circumferential direction. Measurement is made for the load of the guide roller unit pressing the side plate 2 of the gas holder when the piston 6 rises and falls within the gas holder, and the amount of travel required to make proper the load on the side plate 2 by the guide roller unit is determined on the basis of the measured load and the coefficient of elasticity of the gas holder side plate 2, and the load to press outward the inner surface of the side plate 2 is adjusted by shifting the position of the applicable guide roller unit in a plan view in the diametric direction of the gas holder on the basis of the required amount of travel.

Description

  In the present invention, when holding the piston horizontally by pressing the side plate of the gas holder by the guide roller disposed on the outer peripheral portion of the piston, the tilt suppression is achieved by appropriately controlling the force pressing the side plate to suppress the tilt of the piston. It is about the method.

  For example, in an ironworks, in order to effectively use a combustible by-product gas generated from a blast furnace or a converter as an energy source, a piston elevating gas holder that temporarily stores the by-product gas is installed. The gas holder includes a cylindrical holder body composed of a plurality of side plates whose outer surfaces are supported by a base pillar and a corridor, and a piston that freely moves up and down in accordance with the increase and decrease of the gas amount inside the holder body. In order to prevent the internal gas from leaking from the sliding portion when the piston moves up and down, a sealing device using sealing oil as disclosed in Patent Document 1, for example, is provided at the outer peripheral edge of the piston. ing.

  In such a sealing device, when the piston tilts when the piston moves up and down, the seal oil in the sealing device moves, and the distance between the seal of the sliding portion and the side plate increases, The seal may not be maintained. Further, when the inclination angle of the piston becomes large, not only the seal cannot be maintained, but also the amount of expansion and contraction that is possible in the structure of the sealing device is exceeded, and the sealing device may be damaged. Therefore, conventionally, as shown in FIG. 11, for example, a plurality of upper and lower guide rollers 102 that are positioned above the sealing device and press the side plate 101 of the gas holder 100 outward are installed at predetermined intervals in the circumferential direction of the gas holder. (Patent Document 2).

  In this pair of upper and lower guide rollers, for example, as shown by a broken line in FIG. 11, when the piston 103 is inclined with respect to the vertical axis, the load that the guide roller 102 presses the side plate 101 is large due to the inclination of the piston 103. Become. At that time, the guide roller 102 at the place where the load for pressing the side plate 101 is increased is pushed back by the reaction force from the side plate 101 of the gas holder 100. As a result, a restoring moment acts on the piston 103, so that the piston 103 is automatically held horizontally, so-called automatic alignment is performed, and the level of the sealing device is appropriately maintained.

  The effect of the automatic alignment by the pair of upper and lower guide rollers 102 described above increases as the reaction force from the side plate 101, that is, the force pressing the side plate 101 by the guide roller 102 increases, while the side plate 101 is pressed. There is a trade-off relationship in which there is a possibility that the side plate 101 may cause fatigue failure if the force to be increased is increased. Therefore, normally, when the gas holder 100 is installed, an adjustment shim liner is inserted between the support member 104 that supports the guide roller 102 and the guide roller 102 so that the force with which the guide roller 102 presses the side plate 101 is appropriate. Adjustments are made so that the values are correct.

JP 2001-219991 A Japanese Patent Laid-Open No. 11-201398

  However, the inner peripheral surface of the gas holder, that is, the vertical cross-sectional shape of the side plate, has irregularities unique to the gas holder due to installation errors during installation, thermal strain due to welding, and the like. Further, when the by-product gas is introduced into the gas holder and the internal pressure of the gas holder rises, the side plate expands, while the side plate corresponding to the corridor provided outside the gas holder side plate is suppressed from expanding by the corridor. . Therefore, when the internal pressure of the gas holder rises, the longitudinal cross-sectional shape of the side plate protrudes convexly on the inner surface of the gas holder at a position corresponding to the corridor in the gas holder height direction, and is recessed concavely between the corridor and the corridor.

  Therefore, even if the guide roller is adjusted at the time of installation, if the internal pressure of the gas holder increases, the load assumed at the time of adjustment cannot be maintained, and automatic alignment is not performed properly. Further, in the adjustment of the guide roller performed in a state where the internal pressure of the gas holder is increased after the installation is completed, it is necessary to adjust so that the load on the side plate becomes an appropriate value at a portion protruding convexly on the inner surface. This is because, when the load is adjusted so as to have an appropriate value at the recessed portion, an excessive load is applied to the side plate at the protruding portion, which may cause fatigue failure. However, in that case, there is a problem in that an appropriate pressing force cannot be obtained at a recessed portion and automatic alignment is not performed.

  The present invention has been made in view of such a point, and in a gas holder that holds the piston horizontally by pressing the side plate of the gas holder by a guide roller disposed on the outer peripheral portion of the piston, the force for pressing the side plate is appropriately set. The purpose is to suppress the inclination of the piston by controlling.

  In order to achieve the above object, the present invention provides a plurality of sets of pistons provided with a plurality of sets spaced apart at a predetermined interval in the circumferential direction of the gas holder and pressing the inner surface of the side plate of the gas holder outward. Inclination suppression method of the piston that suppresses the inclination to the piston, when the piston moves up and down, measuring the load that the plurality of guide rollers press the side plate of the gas holder, the measured load, Based on the elastic coefficient of the gas holder side plate, the required movement amount in the diameter direction of the gas holder to obtain an appropriate value for the load on the side plate by the guide roller is obtained, and when the piston moves up and down By moving the position of the guide roller in plan view along the diameter direction of the gas holder based on the required movement amount, the inner surface of the side plate is moved outward. It is characterized by adjusting the pressure load.

  According to the present invention, by moving the guide roller based on the required movement amount, the load that the guide roller presses the inner surface of the side plate is adjusted. Can be maintained at an appropriate value. Thereby, when the automatic alignment function by a guide roller operates | operates appropriately and a piston raises / lowers, generation | occurrence | production of an inclination can be suppressed over the whole stroke height of a piston.

  The difference between the measured load and the appropriate load when the side surface of the side plate is pressed outward by the guide roller is calculated, and the difference between the calculated appropriate load and the elastic coefficient of the gas holder side plate are calculated. The required movement amount may be obtained based on the above.

  A fixed guide roller is used for the guide roller disposed on one semicircular side across the diagonal line of the gas holder, and a spring-type guide is used for the guide roller disposed on the other semicircular side. A roller may be used.

  The guide roller is supported by the piston by a support member having a gradient of a predetermined angle in which opposing surfaces are symmetrical in a side view, and the position adjustment in the diameter direction of the guide roller is performed by moving the support member up and down. You may go.

  According to the present invention, in the gas holder that holds the piston horizontally by pressing the side plate of the gas holder by the guide roller disposed on the outer peripheral portion of the piston, the force of pressing the side plate is appropriately controlled to suppress the inclination of the piston. can do.

It is a longitudinal cross-sectional view which shows the outline of a structure of the gas holder which has a piston inclination suppression apparatus concerning this Embodiment. It is a cross-sectional view which shows the outline of a structure of the gas holder which has a piston inclination suppression apparatus concerning this Embodiment. It is explanatory drawing which shows the outline of a structure of the guide roller unit vicinity. It is a table | surface which shows the correlation with the height of a piston, and the load by a guide roller unit. It is a table | surface which shows the correlation of the difference of the height of a piston, and the appropriate load of a guide roller unit. It is a table | surface which shows the correlation with the height of a piston, and the required moving amount | distance of a guide roller unit. It is explanatory drawing which shows the state which the fall moment acted on the piston. It is explanatory drawing which shows the structure of the guide roller unit vicinity concerning other embodiment. It is explanatory drawing about the inclination amount of a piston. It is explanatory drawing about the inclination amount of a piston. It is the schematic of the conventional gas holder.

  Embodiments of the present invention will be described below. FIG. 1 is a longitudinal sectional view showing an outline of a configuration of a gas holder 1 to which a piston inclination suppressing method according to the present embodiment is applied. FIG. 2 is a cross-sectional view schematically showing the configuration of the gas holder 1 having an inclination suppressing device for executing the piston inclination suppressing method according to the present embodiment.

  The gas holder 1 includes a plurality of side plates 2 assembled in a substantially cylindrical shape, a plurality of base pillars C that support the outside of the side plates 2 and are vertically spaced apart by a predetermined distance in the circumferential direction of the gas holder, and the side plates 2. A holder body 5 having a substantially cylindrical shape constituted by a corridor P provided along the outer periphery of the holder, a piston 6 provided in the holder body 5, and a roof 7 for closing an upper end opening of the holder body 5. An inclination suppression device 8 that suppresses inclination when the piston 6 moves up and down is provided. The piston 6 moves up and down in accordance with the gas volume inside the holder body 5, and the internal space of the holder body 5 is partitioned by the piston 6 into a region below the piston 6 and a region above the piston 6. ing. For convenience of illustration, FIG. 1 illustrates three corridors P1 to P3, and FIG. 2 illustrates 12 base pillars C1 to C12.

  In the holder main body 5, a region below the piston 6 is a gas reservoir. A gas flow path (not shown) is connected to the lower part of the holder body 5, and the gas introduced through the flow path is stored in a region below the piston 6 inside the holder body 5. It has become so.

  The piston 6 has a sealing mechanism 10 for sealing a region below the piston 6 and a region above the piston 6 at an outer peripheral portion thereof, and the base pillars C1 to C12 of the side plate 2 above the sealing mechanism 10. A guide roller unit 11 is provided in contact with the corresponding position. The guide roller unit 11 includes an upper roller 12 and a lower roller 13 that are a pair of guide rollers that are spaced apart from each other by a predetermined distance in the vertical direction. The upper roller 12 and the lower roller 13 are provided to press the inner surface of the side plate 2 outward, and are supported by the piston 6 via a support member 14 disposed on the upper surface of the outer periphery of the piston 6. The portion where the side plate 2 contacts the guide roller unit 11 is bent outward by the load of the guide roller unit 11, and the load at that time is supported by the base column C and the corridor P.

  When the by-product gas is introduced into the holder main body 5 through the flow path and the piston 6 moves up and down according to the volume of the by-product gas, the guide roller unit 11 is rotated by the upper roller 12 and the lower roller 13 rotating. The piston 6 moves up and down smoothly in the holder body 5. Further, the guide roller unit 11 has a so-called self-aligning function for automatically holding the piston 6 horizontally when the piston 6 is inclined with respect to the vertical axis of the gas holder 1, for example. Specifically, for example, when the piston 6 is inclined, a portion where the amount of deflection of the side plate 2 increases due to the inclination of the piston 6 occurs. Since the side plate 2 is formed of a steel material having an elastic coefficient K, a reaction force that pushes back the upper roller 12 or the lower roller 13 is generated in proportion to the elastic coefficient K and the bending amount at a portion where the bending amount increases. . Therefore, the restoring force acts on the piston 6 by this reaction force, and the piston 6 is automatically aligned.

  For example, as shown in FIG. 3, the support member 14 is connected to the support column 20 installed perpendicularly to the upper surface of the piston 6 and the support column 20 and supports the upper roller 12 and the lower roller 13 on the upper surface. 21. A load adjusting mechanism 33 described later is placed on the upper surface of the support beam 21 and between the upper roller 12 and the lower roller 13 and the support column 20.

  The inclination suppressing device 8 includes four position measuring means 30 for measuring the position in the height direction in the vicinity of the outer peripheral portion of the piston 6, and reaction force from the side plate 2 acting on the upper roller 12 and the lower roller 13, that is, the upper roller 12. The load measuring means 31 for measuring the load by which the lower roller 13 presses the side plate 2, the control device 32 to which the measurement results by the position measuring means 30 and the load measuring means 31 are input, and the side plate by the upper roller 12 and the lower roller 13 2 and a load adjusting mechanism 33 that adjusts the load to 2. The load adjustment mechanism 33 is configured such that a side surface is supported by the support column 20, and a moving unit 33 a provided on the side surface opposite to the surface supported by the support column 20 is movable in the horizontal direction by a driving device (not shown). Yes. The tip of the moving part 33 a is connected to the upper roller and the lower roller 13. Therefore, the horizontal position of the upper roller 12 and the lower roller 13 can be adjusted by horizontally moving the moving portion 33a of the load adjusting mechanism 33, and the load by which the upper roller 12 and the lower roller 13 press the side plate 2 is adjusted. Can be changed. The horizontal movement of the moving unit 33a is controlled by an electrical signal from the control device 32.

  The position measuring means 30 are arranged at four locations on the upper surface of the outer periphery of the roof 7 at a pitch of 90 degrees. As the position measuring means 30, for example, a wire type or ultrasonic type level meter can be used. The load measuring means 31 is provided on the side surfaces of the upper roller 12 and the lower roller 13. For example, a strain gauge can be used as the load measuring means 31. In the storage unit 34 of the control device 32, the measurement height H of the piston 6 obtained in advance by the control device 32 based on the measurement results of the position measurement means 30 and the load measurement means 31 and a guide at the measurement height H. The correlation with the required movement amount A in the diameter direction in a plan view of the roller 6 is stored. The control device 32 compares the correlation stored in the storage unit 34 with the measurement result of the position measuring unit 30, and applies the upper roller 12 and the lower roller 13 to the side plate 2 in accordance with the up and down movement of the piston 6. The movement amount of the moving part 33a of the load adjusting mechanism 33 is controlled so that the load falls within a predetermined range.

  Next, a method for obtaining a correlation between the measured height H of the piston 6 stored in the storage unit 34 and the required moving amount A in the diameter direction in the plan view of the guide roller 6 at the measured height H. Detailed description.

  In obtaining the above-described correlation, first, the piston 6 is moved up and down while measuring the position of the piston 6 in the height direction by the position measuring means 30, and the load measuring means 31 acts on each upper roller 12 and lower roller 13. Measure the load to be applied. In addition, it is preferable to perform this measurement work, for example after the completion of installation of the gas holder 1, prior to the basic adjustment work for adjusting the position of the guide roller unit 11 with a shim liner or the like. This is because the value measured by the load measuring means 31 can be used as data for the basic adjustment of the guide roller unit 11 by the shim liner.

  The measurement results of the position measuring unit 30 and the load measuring unit 31 are input to the control device 32. For example, FIG. 4 shows the correlation between the load M on the side plate 2 and the measured height H of the holder body 5 of the piston 6 when the load is applied based on the measurement results of the respective measuring means. Calculate as shown in the table. FIG. 4 shows the measurement in the gas holder 1 in which the interval in the height direction of the three corridors P1 to P3 is 10 m and the elevation height of the piston 6 is 35 m, and the measurement height H for each meter and the measurement height H The result which calculated | required the correlation with the load M is represented. In FIG. 4, for the convenience of illustration, the correlation between the measurement height H for each meter and the load M is shown, but the interval between the measurement heights H is arbitrary, for example, the correlation is performed as a continuous curve. You may ask for a relationship.

  Next, an appropriate load when the side plate 2 is pressed by the upper roller 12 is subtracted from the load M at the measurement height H shown in FIG. 4, and the increase or decrease at each height position H is, for example, as shown in FIG. The relationship with the necessary load ΔM is obtained. In the example of FIG. 5, for example, the load ΔM is obtained with an appropriate load of 8 tons. At this time, the shim liner may be corrected so that the value of the load ΔM becomes zero by inserting an adjusting shim liner between the support member 14 and the guide roller unit 11.

Here, in the table of FIG. 5, the place where the value of the load ΔM is positive is that the distance between the side plates 2, that is, the diameter of the holder body 5 is smaller than the diameter at which an appropriate load can be obtained. The place where the value is negative means the opposite. Therefore, when the piston 6 moves up and down in the holder main body 5, in order to make the load that the upper roller 12 and the lower roller 13 press the side plate 2 over the entire stroke height of the piston 6 have an appropriate value. The position of the upper roller 12 and the lower roller 13 in plan view may be moved along the diameter direction of the holder body 5 in accordance with the diameter of the holder body 5 at the measurement height H, that is, the longitudinal sectional shape of the side plate 2. . Therefore, required to obtain a proper load in the measurement height H, required movement amount A _H in the horizontal direction of the upper roller 12 and lower roller 13, a load .DELTA.M _H at the measurement height H, obtained in advance The control device 32 obtains A _H = ΔM / K from the elastic coefficient K of the side plate 2 that is present. The elastic coefficient K of the side plate 2 is input to the control device 32 in advance.

FIG. 6 shows the correlation between _AH and measurement height _H obtained by the control device 32. The elastic coefficient K is not constant in the height direction of the holder body 5, but is large at the position in the height direction corresponding to the corridor C, and is small between the corridors C adjacent to each other in the vertical direction. This is because the expansion of the side plate 2 is suppressed by the corridor C. In FIG. 6, the elastic coefficient K is 2.0 (ton / mm) at the position corresponding to the corridor C, 1.5 (ton / mm) at a position 1 m above and below the corridor, and 0.00 at other positions. The required movement amount _AH is obtained as 5 (ton / mm).

Then, the required movement amount A _H at each measurement height H, determined for each guide roller unit 11 corresponding to each group pillar C1-12, stored in the storage unit 34. If the value of the elastic coefficient K is large, the value of the load applied to the side plate 2 fluctuates greatly by a slight movement of the roller unit 11, so that the load adjusting mechanism 33 can be controlled in millimeters. In this embodiment, for example, it is a worm gear jack. For example, a hydraulic actuator, an electric actuator, or an air actuator may be used as long as it can be controlled in millimeters.

  The gas holder 1 having the inclination suppressing device 8 according to the present embodiment is configured as described above. Next, the lifting and lowering operation of the piston 6 of the gas holder 1 will be described.

First, by-product gas flows into the gas holder 1 from the flow passage, and the piston 6 is raised accordingly. At that time, the position of the piston 6 in the height direction is measured by the position measuring means 30, and the measurement result is input to the control device 32. The controller 32 based on the correlation between the measurement height H of the piston 6 by the position measuring means 30, the required movement amount A _H of the measurement height H shown in FIG. 6, the load adjusting an upper roller 12 and lower roller 13 move horizontally only required movement amount _{a H} a moving portion 33a of the mechanism 33.

  When the height of the piston 6 changes according to the change in the gas amount in the gas holder 1, the load adjustment mechanism 33 is continuously controlled by the control device 32 according to the measured height H of the piston 6.

According to the above embodiment, the piston 6 when to move up and down, the upper roller 12 on the basis of the correlation between the measured height H and the required movement amount A _H of the piston 6, which is stored in the storage unit 34 and Since the position of the lower roller 13 in the horizontal direction is adjusted, the load applied to the side plate 2 by the upper roller 12 and the lower roller 13 can always be kept at an appropriate value regardless of the unevenness of the inner surface of the side plate 2. For this reason, when the automatic alignment function by the guide roller unit 11 operates appropriately and the piston 6 moves up and down, the inclination of the piston 6 can be suppressed over the entire stroke height of the piston 6.

  Moreover, since the side plate 2 is not pressed by an excessive force, the fatigue failure of the side plate 2 can be prevented. Therefore, the life of the side plate 2 can be extended.

  Furthermore, by maintaining the load on the side plate 2 by the guide roller unit 11 at an appropriate value, for example, in a conventional guide roller, a tipping moment that may act on the piston 6 at the uneven portion on the inner surface of the holder body 5 is increased. It can be prevented from occurring. Specifically, for example, as shown in FIG. 7, when the piston 6 passes upward through a portion where the inner surface of the holder main body 5 is narrowed, the piston 6 may be inclined. In this case, for example, as indicated by a broken line in FIG. 7, no load is applied to the upper roller 12 or the lower roller 13 on the side where the reaction force originally received from the side plate 2 due to the inclination of the piston 6 is increased, and the inner surface of the holder body 5 is narrowed. Further load may be applied to the upper roller 12 or the lower roller 13 passing through the spot, and a fall moment may occur. However, as described above, since the horizontal positions of the upper roller 12 and the lower roller 13 are adjusted along the unevenness of the inner surface of the holder main body 5, the above-described overturning moment does not occur.

Incidentally, in the above embodiment, the work of using the relationship between the measurement height H and the required movement amount A _H, which had been done at basic adjustment after installation completion of the gas holder 1, actually sub in gasholder 1 You may perform when raw gas is introduced. In doing so, the actual operating conditions, i.e. pressure, longitudinal sectional shape of the side plate 2 at a temperature of by-product gas can reflect, it is possible to obtain a more accurate required movement amount A _H. Even after the required movement amount _AH is obtained, the value of the load measuring means 31 is confirmed. If the load is not within the predetermined range, the load M and the measurement height H are measured again or repeatedly, and necessary. correction of the movement amount a _H may be performed. Incidentally, gas holder 1 by a change in outside air temperature, since the longitudinal sectional shape of the side plate 2 is changed, the required movement amount A _H, for example, may be created for each season.

  In the above embodiment, the positions of the upper roller 12 and the lower roller 13 are adjusted by moving the moving portion 33a of the load adjusting mechanism 33 in the horizontal direction. For example, as shown in FIG. The roller 12 and the lower roller 13 are supported by a substantially trapezoidal fixed-side support member 40 and a free-side support member 41 having a slope of an angle α where the opposing surfaces are symmetrical, and the free-side support member 41 is moved up and down by a load adjustment mechanism 33. The position may be adjusted by moving it. In this case, the fixed-side support member 40 is fixed to the support column 20, and the free-side support member 41 is fixed to the upper roller 12 and the lower roller 13 side. In such a case, the amount of movement of the upper roller 12 and the lower roller 13 by the moving portion 33a is a value obtained by dividing the amount of movement when the moving portion 33a actually moves up and down by tan α, so that the load adjustment with higher system is achieved. Can be performed.

In the above embodiment, for example, when the correlation between the measured height H and the load M shown in FIG. 4 is obtained, the inclination of the piston 6 is not taken into consideration. An error occurs between the measured value M by the measuring means 31 and the load actually applied to the side plate 2. Therefore, based on the inclination amount of the piston 6 may be corrected in the required movement amount A _H. The correction procedure is shown below.

  First, at the measurement height H, the measurement values of the four position measurement means 30 are averaged, and the value is obtained as the position in the height direction at the center point of the piston 6. When the piston 6 is inclined, two adjacent points among the four measurement points are larger than the above average value, and the other two adjacent points are smaller than the average value. The maximum inclination point S at which the height of the outer peripheral edge of the piston 6 is the highest with respect to the height of the center position of the piston 6 is 2 as shown in FIG. It exists between points U and T. Therefore, the angle formed in plan view between the maximum inclination point S and one of the measurement points of two points U and T larger than the average value is θ, the inclination amount of the maximum inclination point S is Y, and the point U , T can be obtained as tan θ = (Y2 / Y1) and Y = (Y1 / cos θ), where Y1 and Y2 are inclination amounts, respectively.

  Next, for example, assuming that the base column that coincides with the point U in plan view is the base column C1, the base column C1 and the base column C1 are located in the diameter direction of the base column C1 and the base column C1, that is, the diagonal line of the base column C1. The horizontal movement amount of the upper roller 12 and the lower roller 13 corresponding to the base pillar C7 is obtained. In this case, for example, as shown in FIG. 10, the distance between the opposed upper rollers 12, 12, that is, the diameter of the piston 6 is L, the length of the hypotenuse between the pair of upper and lower upper rollers 12 and the lower roller 13 is G, the diameter Assume that the angle formed by L and the hypotenuse G is β, and the piston 6 is inclined by the inclination angle γ in the clockwise direction of FIG. 9 by inclining the amount of inclination Y1, for example, with the lower roller 13 corresponding to the base column C1 as a fulcrum. The movement amount Q of the upper roller 12 corresponding to the base column C1 due to the influence of the inclination angle γ, the movement amount R1 of the upper roller 13 corresponding to the base column C7, and the movement amount R2 of the lower roller corresponding to the base column C7 are respectively Q = G × cos (β−γ) −L, (R1 + R2) = G × cos (β + γ) −L, R1 = Q + R2, and tan γ = (Y1 / L).

Therefore, by multiplying the movement amounts Q, R1, and R2 of each guide roller by the elastic coefficient K, the load generated in each guide roller unit 11 due to the inclination amount Y1 can be obtained. Therefore, the load due to the inclination amount by correcting the load M in the table of FIG. 5, it is possible to obtain a more accurate required movement amount A _H. As a result, the load on the side plate 2 by the guide roller can be adjusted more strictly, and the automatic alignment function by the guide roller unit 11 can be further improved. In addition, the inclination amount in the other base pillar C can be obtained by changing the value of the angle θ described above according to the position of each base pillar. Further, for example, when the position in plan view is shifted from the point U and the base column C1 by a predetermined angle, the angle θ may be corrected according to the angle.

  In the above embodiment, all of the fixed guide rollers are used. However, a fixed guide roller is used for the guide roller unit 11 corresponding to the base pillars C1 to C6 for half a circumference, and the diagonal lines of the base pillars C1 to C6 are used. On the other side of the guide roller unit 11 corresponding to the base pillars C7 to C12, a spring-type guide that moves horizontally following the unevenness in the vertical direction of the side plate 2 of the holder body 5 by a built-in spring. A roller may be used. In such a case, since the guide roller unit 11 at a position corresponding to the pillars C7 to C12 can absorb the irregularities on the inner surface of the holder body 5, the automatic alignment mechanism of the guide roller unit 11 is further improved.

  The present invention is useful when the inclination of the piston of the gas holder is suppressed by the guide roller.

DESCRIPTION OF SYMBOLS 1 Gas holder 2 Side plate 5 Holder main body 6 Piston 7 Roof 8 Tilt control apparatus 10 Seal mechanism 11 Guide roller unit 14 Support member 20 Support pillar 21 Support beam 30 Position measurement means 31 Load measurement means 32 Control apparatus 33 Load adjustment mechanism 33a Moving part 34 Storage part 40 Fixed side support member 41 Free side support member C Base pillar P Corridor

Claims (4)

Piston inclination suppressing method for suppressing a piston provided with a plurality of sets spaced apart from each other at a predetermined interval in the circumferential direction of the gas holder and having a guide roller that presses the inner surface of the side plate of the gas holder outward when the piston is moved up and down Because
When the piston moves up and down, the load that the plurality of guide rollers press the side plate of the gas holder is measured,
Based on the measured load and the elastic coefficient of the gas holder side plate, the required movement amount in the diameter direction of the gas holder for obtaining an appropriate value for the load on the side plate by the guide roller,
When the piston moves up and down, the load for pressing the inner surface of the side plate outward is adjusted by moving the position of the guide roller in plan view along the diameter direction of the gas holder based on the required movement amount. An inclination suppression method characterized by the above. Calculating a difference between the measured load and an appropriate load when the side surface of the side plate is pressed outward by the guide roller;
2. The inclination suppressing method according to claim 1, wherein the required movement amount is obtained based on a difference from the calculated appropriate load and an elastic coefficient of the gas holder side plate. A fixed guide roller is used for the guide roller disposed on one semicircular side across the diagonal line of the gas holder, and a spring-type guide is used for the guide roller disposed on the other semicircular side. The inclination suppressing method according to claim 1, wherein a roller is used. The guide roller is supported by the piston by a support member having a gradient with a predetermined angle in which opposing surfaces are symmetrical in a side view,
4. The inclination suppressing method according to claim 1, wherein the position adjustment of the guide roller in the diameter direction is performed by moving the support member up and down.

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