WO2022009864A1 - Procédé, système et programme de réglage de joint d'étanchéité - Google Patents

Procédé, système et programme de réglage de joint d'étanchéité Download PDF

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Publication number
WO2022009864A1
WO2022009864A1 PCT/JP2021/025406 JP2021025406W WO2022009864A1 WO 2022009864 A1 WO2022009864 A1 WO 2022009864A1 JP 2021025406 W JP2021025406 W JP 2021025406W WO 2022009864 A1 WO2022009864 A1 WO 2022009864A1
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WO
WIPO (PCT)
Prior art keywords
gasket
load
shape
flanges
shape change
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Application number
PCT/JP2021/025406
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English (en)
Japanese (ja)
Inventor
淑子 赤松
清華 戸田
聡美 高橋
正 寺崎
義太朗 坂田
和也 菊永
正浩 江頭
Original Assignee
株式会社バルカー
国立研究開発法人産業技術総合研究所
Priority date (The priority date 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 date listed.)
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Application filed by 株式会社バルカー, 国立研究開発法人産業技術総合研究所 filed Critical 株式会社バルカー
Priority to JP2022535332A priority Critical patent/JPWO2022009864A1/ja
Priority to CN202180048296.2A priority patent/CN115812132A/zh
Priority to KR1020227043627A priority patent/KR20230037495A/ko
Publication of WO2022009864A1 publication Critical patent/WO2022009864A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/02—Sealings between relatively-stationary surfaces
    • F16J15/06—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces
    • F16J15/10—Sealings between relatively-stationary surfaces with solid packing compressed between sealing surfaces with non-metallic packing
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L5/00—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes

Definitions

  • the present disclosure relates to a gasket management technique used for, for example, fastening a piping system.
  • Tightening torque and bolt axial force value applied to the flange by bolts are used to tighten the gasket.
  • Tightening torque and bolt axial force value are information on tightening bolts that tighten between flanges.
  • the reason why the bolt tightening torque and axial force value are used for gasket tightening management is that the bolt is a means of tightening between flanges, and if the bolt strain is measured, the tightening force applied to the gasket from the bolt can be easily grasped. ,and so on.
  • the tightening force of the bolt acts on the flange, and only indirectly acts on the gasket through the flange. That is, the flange receives a load due to the tightening of the bolt, and this load merely acts on the gasket through the flange.
  • the torque value and the axial force value applied to the bolt are the loads acting on a part of the flange, and do not represent the surface pressure acting on the gasket.
  • the torque value and axial force value obtained from the bolt are information about the bolt, and it cannot be said that the surface pressure received by the gasket is measured.
  • the torque value and axial force value of the bolt are only indirect information and are only a guideline for the surface pressure.
  • Patent Documents 1 to 3 do not disclose or suggest such a problem. Further, such a problem cannot be solved by the configurations disclosed in Patent Documents 1 to 3.
  • an object of the present disclosure is to observe a change in the shape of a gasket that receives a load between flanges based on the above problems and the above findings, and to use the observation result for management of gasket tightening.
  • the gasket management method of the present disclosure there is a step of applying a load to the gasket restrained between the flanges and a step of observing a shape change caused in the gasket due to the load.
  • the tightening of the gasket is controlled based on the shape change.
  • the shape change includes at least a change in the spacing direction between the flanges of the gasket, or a change in the spacing direction and the crossing direction, or both.
  • a measuring means for measuring a shape change of a gasket which is restrained between flanges and receives a load, and tightening between the flanges based on the shape change. It includes a management server that generates management information to be managed, and an information presentation unit that presents the management information.
  • a program to be realized by a computer in which a gasket is restrained between flanges and a load is received from between the flanges, and the load causes the gasket.
  • the computer realizes a function of acquiring shape information representing the shape change caused in the above and a function of generating management information for managing the tightening of the gasket based on the shape change.
  • the change in the shape of the gasket that occurs between the flanges represents the load that the gasket receives from between the flanges and the tightening state of the gasket, and the tightening of the gasket can be controlled by observing the change in the shape of the gasket.
  • FIG. 1 A is a diagram showing a gasket according to the first embodiment, and B is a diagram showing an example of a shape observing unit for the gasket. It is a figure which shows the shape change with respect to the load in the gasket which concerns on Example 1.
  • FIG. 1 A is a diagram showing a gasket according to the first embodiment, and B is a diagram showing an example of a shape observing unit for the gasket. It is a figure which shows the shape change with respect to the load in the gasket which concerns on Example 1.
  • A is a diagram showing a gasket according to the second embodiment
  • B is a perspective view showing an outer cut of the gasket
  • C is a diagram showing a shape change appearing in the outer cut. It is a figure which shows the shape change with respect to the load in the outer cut which concerns on Example 2.
  • FIG. A is a diagram showing the gasket according to the third embodiment
  • B is a perspective view for explaining the inner cut
  • C is a diagram showing a shape change appearing in the inner cut. It is a figure which shows the shape change with respect to the load in the gasket which concerns on Example 3.
  • FIG. It is a figure which shows an example of the shape observation of the gasket which concerns on Example 4.
  • A is a diagram showing shape changes on the outer diameter side and the inner diameter side
  • B is a diagram showing shape changes in the circumferential direction and the radial direction.
  • A is a diagram showing the shape of the gasket according to the fifth embodiment
  • B is a diagram showing an example of a state before a load is applied
  • C is a diagram showing an example of a state when a load of a predetermined value is applied. It is a figure which shows the shape observation example which concerns on Example 5.
  • FIG. 1 shows a flange fastening portion 2 according to the first embodiment.
  • the configuration shown in FIG. 1 is an example, and the present disclosure is not limited to such a configuration.
  • the X-axis, the Y-axis, and the Z-axis are shown at the center of the flange fastening portion 2 as an example.
  • the flange fastening portion 2 has a pipeline 4-1 and a pipeline 4-2 arranged in the Z-axis direction.
  • a flange 6-1 is formed in the pipeline 4-1 as a means for fastening to the pipeline 4-2.
  • a flange 6-2 is formed in the pipeline 4-2 as a means for fastening to the pipeline 4-1.
  • a gasket 8 is arranged between the flanges 6-1 and 6-2.
  • the flanges 6-1 and 6-2 penetrate a plurality of bolts 10 at predetermined angular intervals (for example, 45 degrees) and are fastened to each bolt 10 with a nut 12.
  • the gasket 8 is a sealing member between the flanges 6-1 and 6-2, and is, for example, a sheet gasket in which PTFE (Polytetrafluoroethylene) and a filler are blended.
  • the gasket 8 may be a gasket using a resin or rubber other than PTFE.
  • the gasket 8 may be made of a metal material, or may be a combination of a metal material and a ceramic, a heat-resistant fiber material, or another material.
  • the gasket 8 includes a spiral gasket 80 (FIG. 5), a flat plate gasket having a sheet such as PTFE or graphite attached to the surface, a groove formed on the gasket surface, or a flange portion on the outer edge portion. Includes can profile gaskets and the like.
  • the gasket 8 has a restraining portion 8-1 on the inner peripheral side and a non-constraining portion 8-2 on the outer peripheral side.
  • the restraint portion 8-1 is sandwiched between the flanges 6-1 and 6-2 and restrained, and is a contact portion with the flanges 6-1 and 6-2, and is loaded from the flanges 6-1 and 6-2. This is the area that receives F.
  • This load F is a tightening load by each bolt 10 and nut 12.
  • the non-constrained portion 8-2 is integrated with the restrained portion 8-1, and is not constrained by the flanges 6-1 and 6-2, and is a region on the peripheral edge side of the gasket 8. That is, the unconstrained portion 8-2 is not in contact with the flanges 6-1 and 6-2, is not constrained by the flanges 6-1 and 6-2, and receives the load F from the flanges 6-1 and 6-2. It is an area that is not received.
  • a plurality of shape observation units 14-1, 14-2, 14-3, and 14-4 are set in the non-restraint unit 8-2.
  • Each shape observation unit 14-1, 14-2, 14-3, 14-4 is a region for observing a shape change appearing in the non-constrained portion 8-2 due to the load F received by the restrained portion 8-1.
  • shape observation units 14-1, 14-2, 14-3, 14 of arbitrary width are set at angle positions set at 90-degree intervals. -4 is arranged.
  • FIG. 2 shows the cut end face of the line II-II portion of FIG.
  • the restraint portion 8-1 is sandwiched and restrained between the gasket seats 16 of the flanges 6-1 and 6-2.
  • the non-restraint portion 8-2 protrudes into the gap 18 between the flanges 6-1 and 6-2.
  • the end portion of the gasket 8 is a free end in which when the restraining portion 8-1 receives the load F, strain with respect to this load appears as a shape change in the non-constraining portion 8-2, and constitutes a cantilever.
  • the gasket 8 that received this load F causes strain in the restraint portion 8-1, and this strain causes a shape change in the non-constrained portion 8-2.
  • This shape change is the amount of change according to the load F.
  • This shape change changes depending on the magnitude of the load F and the direction of action.
  • This shape change includes a change in the spacing direction (Z-axis direction) of the flanges 6-1 and 6-2 and a change in the crossing direction (X-axis direction, Y-axis direction) with respect to the spacing direction.
  • the shape change of the gasket 8 of the first embodiment includes a change in the thickness direction, the radial direction, or the circumferential direction of the gasket 8.
  • the management process of the gasket 8 is an example of the management method of the present disclosure.
  • This control step includes a generation step S1 of the restraint portion 8-1 and the non-constraint portion 8-2, a load F application step S2, a shape information acquisition step S3, and a shape information presentation step S4.
  • S1 to S4 attached to each step are the order of each step, and the terms quoted are only used for convenience.
  • Load F application step S2 In the gasket 8, the load F is applied to the restraint portion 8-1 restrained by the flanges 6-1 and 6-2 by tightening the flanges 6-1 and 6-2. In response to this load F, the strain of the restraint portion 8-1 causes a shape change in the non-constrained portion 8-2.
  • Shape information acquisition process S3 The management server 24 (FIG. 3) acquires shape information including the shape change appearing in the non-constrained portion 8-2.
  • the management server 24 generates presentation information including shape information and presents it by the information presentation unit 26 (FIG. 3).
  • the shape information acquired in the shape information acquisition step S3 may be subjected to Nth derivative (multi-step differentiation) to make the change points of the shape information stand out. If this processing result is reflected in the presentation information in the presentation step S4, the change point of the shape information can be clarified.
  • FIG. 3 shows the gasket management system 20 according to the first embodiment.
  • This gasket management system 20 is a system for executing the above-mentioned management process by information processing.
  • the configuration shown in FIG. 3 is an example, and the present disclosure is not limited to such a configuration.
  • the same parts as those in FIG. 2 are designated by the same reference numerals.
  • the gasket management system 20 includes a strain sensor 22, a management server 24, and an information presentation unit 26.
  • the strain sensor 22 is an example of a measuring means for measuring a shape change from the shape observation unit 14 set in the unconstrained unit 8-2, and outputs a detection signal indicating the amount of change in the shape change generated in the shape observation unit 14. ..
  • a laser displacement meter, a camera, or the like may be used for the strain sensor 22 as a device for detecting a shape change and converting it into an electric signal.
  • the laser displacement meter shines a laser beam on the shape observation unit 14, detects the shape change of the shape observation unit 14 with the reflected light, and observes the amount of change.
  • the camera captures the shape observation unit 14, detects the shape change detected by the strain sensor 22 by the management server 24 by the number of pixels, and acquires the shape change information corresponding to the strain.
  • the management server 24 is composed of a computer having a communication function.
  • the management server 24 includes a processor 28, a storage unit 30, an input / output (I / O) unit 32, and a communication unit 34.
  • the processor 28 executes an OS (Operating System) and a management program in the storage unit 30, and performs information processing for gasket management.
  • the storage unit 30 includes a storage medium for storing the OS and the management program.
  • the gasket management database (DB) 36 (FIG. 4) is stored in the storage unit 30.
  • the communication unit 34 controls the processor 28 to input and present information in cooperation with a management terminal (not shown).
  • the management terminal is also used for acquiring shape information and writing and reading the gasket management DB 36.
  • the information presenting unit 26 under the control of the management server 24, presents management information including load information and determination information related to the change information representing the shape change.
  • ⁇ Information processing of management server 24> For information processing of the management server 24, a) Processing for capturing the detection output of the strain sensor 22 b) Acquisition of shape information of the gasket 8 including the shape change of the unconstrained portion 8-2 c) Processing such as presentation of information by the information presenting unit 26 is included.
  • FIG. 4 shows an example of the gasket management DB 36.
  • the gasket management file 38 is stored in the gasket management DB 36.
  • a gasket information unit 40 as an example of gasket management information, a gasket information unit 40, a shape detection information unit 41, a time information unit 42, a load information unit 44, a strain sensor information unit 46, a detection information unit 48, and history information
  • the unit 50 is set.
  • the gasket information unit 40 stores specification information for specifying the gasket 8.
  • the shape detection information unit 41 contains information on the shape observation units 14-1, 14-2, 14-3, and 14-4, for example, Example 1 (FIG. 6), Example 2 (FIG. 8), and Example 3 (. Shape observation unit information such as the form and arrangement position as shown in FIG. 10) is stored.
  • Time information such as the observation date and time is stored in the time information unit 42.
  • the load information unit 44 stores load information such as the load F applied between the flanges 6-1 and 6-2 by tightening the bolt 10 and the load conditions thereof.
  • the strain sensor information unit 46 stores the type of sensor that observes the shape change and the like.
  • the detection information unit 48 stores the detection values acquired by the strain sensor 22 from the shape observation units 14-1, 14-2, 14-3, and 14-4.
  • the history information unit 50 stores history information such as observation and information presentation such as shape change and load.
  • the shape change of the gasket 8 is caused by the load received by the gasket 8 from between the flanges 6-1 and 6-2, and represents the tightened state of the gasket 8. Therefore, by observing the shape change of the gasket 8 by the shape observing unit 14, the tightening state of the gasket 8 can be grasped and the tightening state can be managed.
  • the shape change of the gasket 8 represents the sealing between the flanges 6-1 and 6-2 by the gasket 8 between the flanges 6-1 and 6-2, and this shape change is directly observed from the gasket itself. Then, the hermeticity between the flanges 6-1 and 6-2 can be easily evaluated.
  • the management method of the gasket 8 according to the second embodiment further includes the estimation step S5 based on the inflection point information in the management method of the first embodiment.
  • the shape information includes the inflection point information of the shape change due to the specific load F, and the management server 24 can calculate the load F to be applied to the gasket 8 from the inflection point.
  • the inflection point represents, for example, a state in which the shape change in the circumferential direction of the gasket 8 changes significantly, and includes a minimum point.
  • the minimum point is a point where the change direction of the shape change changes, and is, for example, a transition point from a compressed state to an extended (tensile) state or an extended (tension) state to a compressed state.
  • Inflection point information can be acquired as peculiar information of shape change from shape information.
  • FIG. 5 shows the gasket management system 20 according to the third embodiment.
  • the configuration shown in FIG. 5 is an example, and the technique of the present disclosure is not limited to such a configuration.
  • This gasket management system 20 is arranged between the flanges 6-1 and 6-2, and the spiral gasket 80 is used as an observation target of the shape change due to the load F received from the flanges 6-1 and 6-2. Be done.
  • the gasket 80 is a laminated body in which a plurality of members having different diameters are coaxially arranged, and includes an outer ring 801, a gasket main body 802, and an inner ring 803.
  • the outer ring 801 and the inner ring 803 are made of a metal material such as stainless steel, carbon steel, or titanium, and are formed in a ring having a predetermined thickness or a shape close to the ring.
  • the gasket body 802 has a thin plate-shaped member made of, for example, a metal material, and a laminated body of a cushioning material (filler) such as graphite or fluororesin, which is spirally wound between the inner wall surface of the outer ring 801 and the outer wall surface of the inner ring 803. It is composed by winding around.
  • the laminate constituting the gasket main body 802 is formed, for example, in a cross section having a “V” shape or a waveform close to it. In this laminated body, for example, the end faces are fixed to the outer ring 801 and the inner ring 803 by spot welding.
  • the gasket 80 is restrained in which only the inner ring 803, a part or all of the inner ring 803 and the gasket body 802, and a part of the outer ring 801 come into contact with the gasket seat 16 (FIG. 2) to receive a load F. It may be part 8-1. That is, in the gasket 80, a part or all of the outer ring 801 becomes an unconstrained portion 8-2. In the gasket 80, the gasket main body 802 is deformed according to the load F from the flanges 6-1 and 6-2, and the outer ring 801 is distorted due to this deformation.
  • a shape observation unit 14 is set in a part of the outer ring 801 which is an unconstrained portion 8-2, and a shape change such as a strain generated in the outer ring 801 is measured by a strain sensor 22. Then, the gasket management system 20 grasps the load F applied to the gasket 80 and the tightened state of the gasket by utilizing the amount of change in the shape change. As for the management process of the tightened state of the gasket 80, the same process as that of the above embodiment may be performed.
  • FIG. 6A shows the gasket 8 according to the first embodiment.
  • the restrained portion 8-1 and the non-constrained portion 8-2 are set concentrically with the same width or substantially the same width.
  • the restraining portion 8-1 is a coplanar surface on the gasket 8, and may be a region automatically determined as a contact portion between the flanges 6-1 and 6-2 described above and the gasket seat 16, and the non-constraining portion 8 may be formed.
  • -2 may be a region separated from the gasket seat 16.
  • FIG. 6 shows a gasket 8 in which a plurality of shape observation units 14-1, 14-2, 14-3, and 14-4 are arranged.
  • the shape observation units 14-1, 14-2, 14-3, and 14-4 are arranged in the unconstrained unit 8-2 at an angular interval of 90 degrees at the center angle.
  • ⁇ indicates the angle range in which the shape observation units 14-1, 14-2, 14-3, and 14-4 are set.
  • the arrangement positions of the shape observation units 14-1, 14-2, 14-3, and 14-4 may be set to positions that do not overlap with the arrangement positions of the bolts 10, but the arrangement position is not limited to this.
  • the shape change appearing in is shown by the measured value measured by the strain sensor 22.
  • m2 is the deformation of the gasket 8 in the 45 (deg) direction
  • the restraining portion 8-1 receives the load F from the flanges 6-1 and 6-2 in this way, the shape of the non-constraining portion 8-2 changes according to the load F.
  • An inflection occurs in this shape change, and the optimum load F can be specified from the relationship between the load F applied to the gasket 8 and the inflection point of the shape change, and can be used as information for determining the completion of initial fastening.
  • FIG. 8 shows the gasket 8 according to the second embodiment.
  • the restrained portion 8-1 and the non-constrained portion 8-2 are set to have the same width or substantially the same width and are concentrically set.
  • Outer cut 54 is formed in each shape observation unit 14-1, 14-2, 14-3, 14-4 in the non-restraint portion 8-2.
  • the outer cut 54 is formed in the outermost edge portion of the non-restraint portion 8-2 of the gasket 8, and has a notch shape having a non-closed portion in a part thereof.
  • a plurality of outer cuts 54 are formed on the gasket 8, and each outer cut 54 is arranged on the non-restraint portion 8-2 at an angular interval of 90 degrees at a center angle.
  • the outer cut 54 is, for example, a groove having a constant width W1 cut by a constant length L1 from the peripheral surface of the gasket 8 toward the center, and is an upper and lower surface of the gasket 8. It penetrates into. That is, the outer cut 54 has a vertical surface portion 56 and parallel surface portions 58 and 60 facing each other with a constant width W1 inside the gasket 8.
  • Such a shape change can be easily detected by the strain sensor 22.
  • a sensor member such as metal or resin may be installed in the space portion of the outer cut 54, and the shape change of the outer cut 54 may be extracted from the sensor member.
  • FIG. 9 shows the relationship between the shape change and the load appearing in the gasket 8 according to the second embodiment, with the load [kN] on the horizontal axis and the opening width (shape change) [mm] of the outer cut 54 on the vertical axis. .. Similarly, Table 1 shows the relationship between the opening width W2 of the outer cut 54 and the load F.
  • the opening width W2 of the outer cut 54 indicating the shape change with respect to the load F increases. .. An inflection occurs in this shape change. Therefore, when the second embodiment is used, if the inflection point of the shape change appearing in the shape observation units 14-1, 14-2, 14-3, 14-4 is targeted, the relationship between the shape change and the load F is used. Can be identified.
  • FIG. 10 shows the gasket 8 according to the third embodiment.
  • the restrained portion 8-1 and the non-constrained portion 8-2 are set concentrically with the same width or substantially the same width.
  • Inner cuts 62 are formed in the shape observation units 14-1, 14-2, 14-3, and 14-4 in the non-restraint portion 8-2.
  • the inner cut 62 is a through-hole portion formed in the unrestrained portion 8-2 of the gasket 8.
  • Each inner cut 62 is arranged in the non-restraint portion 8-2 at an angular interval of 90 degrees at the center angle, but is not limited to this.
  • the inner cut 62 is an arcuate groove portion concentric with the peripheral edge portion of the gasket 8 and having a constant width W, and penetrates the upper and lower surfaces of the gasket 8. That is, the inner cut 62 has vertical surface portions 64, 66, a constant length L2, and concentric arc portions 68, 70 facing each other with a width W3 inside the gasket 8.
  • a sensor member such as metal or resin may be installed in the space portion of the inner cut 62, and the shape change of the inner cut 62 may be extracted from this sensor member.
  • FIG. 11 shows the relationship between the shape change and the load appearing on the gasket 8 according to the third embodiment, with the load [kN] on the horizontal axis and the strain (shape change) of the inner cut 62 on the vertical axis.
  • the shape of the inner cut 62 representing the change in the load F changes.
  • This shape change has a minimum point included in the inflection point, and in the third embodiment as well, the relationship between the shape change and the load F can be specified by targeting the minimum point.
  • this minimum point is a point where the change direction of the shape change appearing in the unconstrained portion 8-2 of the gasket 8 changes, that is, the inner cut 62 is expanded (tensioned) or extended from the compressed state. This is the transition point from the (tensile) state to the compressed state.
  • the minimum point appears remarkably due to the shape change in the circumferential direction, but the minimum point may be the inflection point.
  • the change in shape in the circumferential direction may cause an inflection point in which the change in shape in the circumferential direction changes significantly, that is, not a minimum point.
  • Example 1 ⁇ Detection of inflection points in shape information and tightening criteria>
  • Example 2 ⁇ Detection of inflection points in shape information and tightening criteria>
  • inflection points can be generated in the shape information corresponding to a specific load F.
  • a specific load F can be estimated from the inflection point of the shape information, and can be used as a criterion for determining the completion of tightening.
  • Example 1 the outer cut 54 and the inner cut 62 are not processed.
  • an appropriate load F can be estimated by measuring the opening width W2 of the cut shape from the side surface.
  • the opening width W2 of the outer cut 54 is measured in advance for each load F applied to the gasket 8, and the load F is estimated by comparing the opening width W2 with the measured value. can.
  • the opening width W2 of the outer cut 54 is stored in a database for each load F, and the load F can be easily and accurately calculated by comparing with the measured value of the shape change.
  • a load F is applied to the flanges 6-1 and 6-2, and the inner wall surface of the through-hole-shaped inner cut 62 is closed (contacted), so that a remarkable change can be obtained.
  • the shape change of the non-restraint portion 8-2 (Example 1)
  • the shape change of the outer cut 54 (Example 2)
  • the inner cut The shape change (Example 3) of 62 can be measured, and the change representing the load F can be obtained from the gasket 8. Therefore, the load F applied to the flanges 6-1 and 6-2 can be estimated from the shape change of the gasket 8 without being affected by the bolt 10 and the flanges 6-1 and 6-2.
  • gasket 8 can also handle various diameters and thicknesses regarding the processed shapes of the outer cut 54 and the inner cut 62.
  • FIG. 12 shows a configuration example of the gasket 80 according to the fourth embodiment.
  • the outer ring 801 of the spiral gasket 80 constitutes the unconstrained portion 8-2.
  • the shape changes Qa and Qb on the outer edge side and the inner edge side of the outer ring 801 of the gasket 80 that expand and contract in the circumferential direction and the shape change R that expands and contracts in the radial direction of the gasket 80 are measured.
  • A has a load [kN] on the horizontal axis and a strain (shape change) in the circumferential direction on the vertical axis, and the shape change Qa appearing on the outer edge of the outer ring 801 and the shape change Qb appearing on the inner edge are measured by the strain sensor 22. The measured value is shown.
  • the strain on the inner edge side of the outer ring 801 is larger than the strain on the outer edge side. That is, since the shape of the outer ring 801 changes significantly on the inner edge side, it is easy to detect the change behavior of the gasket 80 or the gasket body 802 due to the load F.
  • B has a load [kN] on the horizontal axis and a strain (shape change) on the vertical axis, and the strain sensor 22 measures the shape change Qb in the circumferential direction appearing on the inner edge of the outer ring 801 and the shape change R appearing in the radial direction. The measured value is shown.
  • the measured value increases in the positive direction as the gasket surface pressure increases, so it can be understood that a force in the tensile direction is acting. Further, in the shape change R in the radial direction, the measured value increases in the negative direction as the gasket surface pressure increases, so that it can be understood that the compressed state is obtained.
  • FIG. 14A shows a configuration example of the gasket 80 according to the fifth embodiment.
  • the outer ring 801 constitutes the unconstrained portion 8-2.
  • an inner cut 82 having a predetermined length is formed on a part of the outer ring 801 of the gasket 80 along the outer circumference.
  • the inner cut 82 is a through-hole portion formed in the unrestrained portion 8-2 of the gasket 8.
  • the inner cut 82 is formed at a position of 5 [mm], for example, as a predetermined distance t from the outer edge portion of the outer ring 801.
  • the shape observation unit 14 is provided at the outer edge portion along the formation position of the inner cut 82.
  • the outer ring 801 has a predetermined width of, for example, 0.1 [mm] before the load F from the flanges 6-1 and 6-2 is applied to the gasket body 802.
  • the inner cut 82a is open.
  • the outer ring 801 is formed into an inner cut 82b in which a part or all of the opening portion is deformed and closed, as shown in FIG. 14, for example, C.
  • the gasket surface pressure due to the load F and the shape change Qc of the outer ring 801 in the state of the inner cut 82b are measured.
  • a load [kN] is applied on the horizontal axis and a strain (shape change) is applied on the vertical axis, and the shape change Qc in the circumferential direction appearing on the outer edge corresponding to the formation position of the inner cut 82b of the outer ring 801 is measured by the strain sensor 22. The measured value is shown.
  • the state of strain differs depending on the measurement position of the outer ring 801 due to the shape characteristics of the gasket body 802 formed in a spiral shape, and the state of the gasket and the state of load. Can be grasped in detail.
  • the load F from the flanges 6-1 and 6-2 is compared with the sheet gasket composed of a single member.
  • the load F applied from the flanges 6-1 and 6-2 can be estimated from the shape change of the gasket 80.
  • the inner cut 82 formed in the spiral gasket 80 has a remarkable change in the strain generated in the outer ring 801 due to the opening being closed by the load F from the flanges 6-1 and 6-2.
  • the shape changes Qa, Qb, and R (Example 4) that occur in the outer ring 801 are different from the torque management and the measurement of the bolt axial force in the monitoring and measurement of the shape change.
  • the shape change of the inner cut 82 (Example 5) the change representing the load F can be obtained from the gasket 8. Therefore, the load F applied to the flanges 6-1 and 6-2 can be estimated from the shape change of the gasket 80 without being affected by the bolt 10 and the flanges 6-1 and 6-2.
  • the vertical surface portion 56 and the parallel surface portions 58 and 60 are exemplified in the second embodiment, but these are examples.
  • the outer cut 54 may have a shape that does not have the vertical surface portion 56, or may have a V-shaped shape in which the parallel surface portions 58 and 60 are non-parallel, for example.
  • the inner cut 62 may have a shape in which the arcuate portions 68 and 70 do not have a constant width, or may be a parallel surface or a non-parallel surface instead of the arcuate shape.
  • the management server 24 may generate presentation information by processing the acquired shape information by multi-step differentiation or the like, and the information presentation unit may be used.
  • a display unit that clearly indicates the change point may be presented in 26 (FIG. 3).
  • the gasket management method, system and program of the present disclosure it is possible to observe the change in the shape of the gasket due to the load received from the flange without measuring the axial force or torque value of the bolt that fastens between the flanges, and to observe the change in the shape of the gasket due to the load received from the flange. It is useful because the load on the gasket can be calculated from the shape information without being affected by the tightening state of the gasket, and it can be used for management information such as gasket replacement.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Gasket Seals (AREA)

Abstract

Le serrage d'un joint d'étanchéité (8) maintenu entre des flasques (6-1, 6-2) est réglé en se basant sur une étape dans laquelle une charge due au serrage est appliquée, une étape dans laquelle un changement de la forme du joint d'étanchéité généré par la charge est observé, et le changement de forme. Le changement de forme comprend un changement dans le joint d'étanchéité dans au moins la direction de l'intervalle entre les flasques, ou un changement dans une direction orthogonale à la direction d'intervalle, ou les deux changements. Ainsi, si un changement de la forme du joint d'étanchéité recevant la charge est observé, le serrage du joint d'étanchéité peut être réglé.
PCT/JP2021/025406 2020-07-08 2021-07-06 Procédé, système et programme de réglage de joint d'étanchéité WO2022009864A1 (fr)

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JP2022535332A JPWO2022009864A1 (fr) 2020-07-08 2021-07-06
CN202180048296.2A CN115812132A (zh) 2020-07-08 2021-07-06 衬垫的管理方法、系统以及程序
KR1020227043627A KR20230037495A (ko) 2020-07-08 2021-07-06 개스킷의 관리 방법, 시스템 및 프로그램

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013040647A (ja) * 2011-08-15 2013-02-28 Hitachi-Ge Nuclear Energy Ltd フランジのガスケット締代測定方法
WO2018008585A1 (fr) * 2016-07-07 2018-01-11 日本バルカー工業株式会社 Dispositif de formation et procédé de formation pour construire un joint

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4699935B2 (ja) 2006-04-26 2011-06-15 株式会社日立エンジニアリング・アンド・サービス フランジ締結監視装置
JP2014225219A (ja) 2013-11-07 2014-12-04 ニチアス株式会社 ガスケット締付計算システム、ガスケット締付計算システムの制御方法、及び、プログラム
JP2015141345A (ja) 2014-01-29 2015-08-03 日本バルカー工業株式会社 フランジ締付け実習システム

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013040647A (ja) * 2011-08-15 2013-02-28 Hitachi-Ge Nuclear Energy Ltd フランジのガスケット締代測定方法
WO2018008585A1 (fr) * 2016-07-07 2018-01-11 日本バルカー工業株式会社 Dispositif de formation et procédé de formation pour construire un joint

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