TW202219404A - Gasket control method, system, and program - Google Patents

Abstract

Tightening of a gasket held between flanges is controlled on the basis of a step in which a load due to tightening is applied, a step in which a change in the shape of the gasket generated by the load is observed, and the change in shape. The change in shape includes a change in the gasket in at least the direction of the interval between the flanges, or a change in a direction orthogonal to the interval direction, or both of said changes. Thus, if a change in the shape of the gasket receiving the load is observed, tightening of the gasket can be controlled.

Description

Gasket management method, system and program-recorded medium

The present disclosure relates to a management technique for gaskets used for, for example, fastening of piping systems.

In the locking of the gasket, the locking torque or the bolt axial force value applied to the flange by the bolt is conventionally used. The tightening torque or bolt axial force value is information about the tightening of the bolt between the locking flanges.

There is a known system for locking this gasket, and in order to grasp the locking torque, the locking surface pressure corresponding to the type of the gasket or the internal fluid, a plurality of locking forces, and bolts are used. information, etc. (for example, Patent Document 1). Regarding the tightening of the bolts, there is known a method of documenting the strain generated in the bolts to visually recognize the tightening state of the bolts (for example, Patent Document 2). In addition, there is known a technique for measuring the force applied to a part of the gasket by tightening with a sheet-like pressure sensor embedded in the gasket (for example, Patent Document 3). prior art literature Patent Literature

Patent Document 1: Japanese Patent Application Laid-Open No. 2014-225219 Patent Document 2: Japanese Patent Laid-Open No. 2015-141345 Patent Document 3: Japanese Patent No. 4699935

The problem to be solved by the invention

However, the reason why the bolt tightening torque or the axial force value is used for the tightening management of the gasket is that the bolt is a component between the locking flanges, and it is possible to easily grasp the force applied to the gasket from the bolt by measuring the strain of the bolt. locking force, etc.

However, as a result of careful study of the relationship between bolts, flanges, and gaskets, the locking force of the bolts acts on the flanges, while the gaskets only act indirectly through the flanges. That is, the flange will bear the load caused by the locking of the bolt, and this load is only applied to the gasket through the flange. The torque value or the axial force value acting on the bolt is the load acting on a part of the flange, and does not represent the load acting on the surface pressure of the gasket.

Therefore, there are the following problems in the locking management of the gasket.

a) The torque value or axial force value obtained from the bolt is the information about the bolt, and cannot be called the measurement of the surface pressure of the gasket.

b) Judging from the surface pressure of the gasket from the flange, the torque value or axial force value of the bolt is only indirect information, and it is only a reference for the surface pressure.

c) The torque value or the axial force value of the bolt is affected by the locking state of the bolt or flange, and this tendency cannot be ignored.

When estimating the surface pressure of the gasket by the torque value or axial force value measured by the torque wrench or the bolt axial force meter, when it is affected by the locking state of the bolt or flange, the value given to the gasket is given. The relationship between the surface pressure (= estimated surface pressure) and the actual surface pressure (= actual surface pressure) received by the gasket becomes: Estimated surface pressure ≠ actual surface pressure. Even if the measurement accuracy of the torque value or axial force value is improved, the estimated surface pressure and the actual surface pressure of the gasket still do not match. Unable to grasp the surface pressure on the gasket.

In view of such a subject, the inventors have obtained the knowledge that the shape change of the gasket depends on the load received from between the flanges, and observing the shape change is useful in the locking management of the gasket. Patent Documents 1 to 3 do not disclose or suggest such a subject. In addition, the configurations disclosed in Patent Documents 1 to 3 cannot solve such a problem.

Then, the objective of this disclosure is to observe the shape change of the gasket which receives a load between flanges based on the said subject and the said knowledge knowledge, and to use this observation result in the management of the lock|rock of a gasket. means of solving problems

In order to achieve the above-mentioned object, one aspect of the management method of the gasket according to the present disclosure includes the following steps: a step of applying a load to the gasket constrained between the flanges; The step of changing the shape, and managing the locking of the gasket according to the shape change.

In this management method, the shape change includes any one or both of a change in the spacing direction between at least the flanges of the gasket, or a change in a direction intersecting with the spacing direction.

In order to achieve the above-mentioned object, according to one aspect of the management system of the present disclosure, it includes: a measuring unit for measuring the shape change of the gasket bound between the flanges and receiving a load; and a management server for generating and managing the flange according to the shape change and the information prompting department, which prompts the aforementioned management information.

In order to achieve the above-mentioned object, according to one aspect of the program-recorded medium of the present disclosure, a program for realizing the following function in a computer is recorded: a function of acquiring shape information indicating a shape change caused by the gasket being bound to the flange A load is received from between the flanges from time to time, and the shape of the gasket is changed due to the load; and the function of generating management information for managing the locking of the gasket according to the shape change. Invention effect

According to the present invention, any of the following effects can be obtained.

(1) The change in the shape of the gasket between the flanges indicates the load received by the gasket between the flanges and the locking state of the gasket, and the locking of the gasket can be managed by observing the shape change of the gasket.

(2) The change in the shape of the gasket between the flanges indicates the locking state of the gasket between the flanges or the tightness between the flanges. If the shape change is directly observed from the gasket itself, it is easy to Evaluate the locking state or tightness between flanges.

(3) Compared with the conventional management of the torque value or axial force value of the bolt, the locking management accuracy of the gasket can be improved without depending on the skill of the practitioner.

In addition, other objects, features, and advantages of the present invention should become more apparent by referring to the attached drawings and the respective embodiments.

Form for carrying out the invention

[1st Embodiment] FIG. 1 shows the flange fastening portion 2 of the first embodiment. The configuration shown in FIG. 1 is merely an example, and the present disclosure is not limited to such a configuration. In FIG. 1 , as an example, the X axis, the Y axis, and the Z axis are described with the center of the flange fastening portion 2 . In this flange fastening part 2, the piping 4-1 and the piping 4-2 are arrange|positioned in the Z-axis direction. A flange 6-1 is formed on the pipe 4-1 as a fastening assembly with the pipe 4-2. A flange 6-2 is formed on the pipe 4-2 as a fastening assembly with the pipe 4-1.

A gasket 8 is arranged between the flanges 6-1 and 6-2. The flanges 6 - 1 and 6 - 2 are inserted through a plurality of bolts 10 at predetermined angular intervals (for example, 45 degrees), and are fastened by the bolts 10 and the nuts 12 . The gasket 8 is a sealing member between the flanges 6-1 and 6-2, and is, for example, a sheet gasket mixed with PTFE (Polytetrafluoroethylene, polytetrafluoroethylene) and a filler. The gasket 8 may be a gasket using resin or rubber other than PTFE. In addition, the spacer 8 may be a spacer made of a metal material, or a spacer formed by combining a metal material and ceramics, a heat-resistant fiber material, or other materials. Further, the gasket 8 includes a spiral gasket 80 ( FIG. 5 ), a gasket in which a sheet of PTFE or graphite or the like is adhered to the surface of a flat gasket, a gasket formed with grooves or The outer edge portion is provided with a comb-tooth washer and the like of the guard portion.

In this gasket 8, a restraint portion 8-1 is set on the inner peripheral side, and a non-restraining portion 8-2 is set on the outer peripheral side. The restraint portion 8-1 is sandwiched between the flanges 6-1, 6-2 and restrained, and is a contact portion with the flanges 6-1, 6-2, and extends from the flanges 6-1, 6-2. 2 Areas subject to load F. The load F is the locking load caused by the bolts 10 and the nuts 12 .

The non-restricting portion 8 - 2 is integrated with the restricting portion 8 - 1 and is not restricted by the flanges 6 - 1 and 6 - 2 , but is an area on the peripheral side of the gasket 8 . That is, the non-restricting portion 8-2 is in non-contact with the flanges 6-1, 6-2, and is not restricted by the flanges 6-1, 6-2, but not from the flanges 6-1, 6-2. 2 Areas subject to load F.

In addition, a plurality of shape observation parts 14-1, 14-2, 14-3, and 14-4 are set in the unconstrained part 8-2. Each of the shape observation parts 14-1, 14-2, 14-3, and 14-4 is an area for observing the shape change that occurs in the non-restricting part 8-2 when the restricting part 8-1 receives the load F shape changes. In this first embodiment, the observation plane formed by the X axis and the Y axis is assumed, and shape observation parts 14-1, 14-2, 14-3, 14-4.

<Cut end face on line II-II in Fig. 1> FIG. 2 is a cut end surface showing a line portion II-II in FIG. 1 . The restraint portion 8-1 is sandwiched between the spacer seats 16 of the flanges 6-1 and 6-2 and restrained. On the other hand, the unconstrained portion 8-2 protrudes from the gap 18 between the flanges 6-1 and 6-2. The end of the gasket 8 is a free end and constitutes a cantilever beam. When the free end receives a load F on the restraint portion 8-1, the strain relative to the load will appear as a shape change in the unrestrained portion 8-2.

<Observation of the shape change appearing in the non-restrained portion 8-2> After the bolt 10 and the nut 12 are locked in order to fasten the flanges 6-1 and 6-2, the restraining portion 8-1 of the washer 8 is received between the flanges 6-1 and 6-2. load F.

In the spacer 8 subjected to the load F, strain occurs in the restraint portion 8-1, and this strain causes the shape change of the non-restraint portion 8-2. This shape change is the amount of change in response to the load F.

This shape change is based on the magnitude or direction of action of the load F. This shape change includes changes in the spacing direction (Z-axis direction) of the flanges 6-1 and 6-2 and the direction (X-axis direction, Y-axis direction) intersecting with the spacing direction. Changes in the shape of the spacer 8 according to the first embodiment include changes in the thickness direction, the radial direction, or the circumferential direction of the spacer 8 .

<Management procedure of gasket 8> The management procedure of the gasket 8 is an example of the management method of this disclosure. This management step includes the generation step S1 of the restraining part 8-1 and the non-restraining part 8-2, the applying step S2 of the load F, the obtaining step S3 of shape information, and the presenting step S4 of the shape information and the like. S1 to S4 attached to each step are the order of each step, and the terms quoted are used only for convenience.

Step S1 of generating the restraining portion 8-1 and the non-restraining portion 8-2: after the gasket 8 is installed between the flanges 6-1 and 6-2, the gasket that contacts the flanges 6-1 and 6-2 The part 8 becomes the restraint part 8-1, and the part of the gasket 8 which is not in contact with the flanges 6-1 and 6-2 becomes the non-restraint part 8-2. That is, the restraint portion 8-1 and the non-restraint portion 8-2 of the gasket 8 are formed by being provided between the flanges 6-1 and 6-2.

Step S2 of applying the load F: the gasket 8 applies the load F to the restraining portion 8-1 restrained by the flanges 6-1 and 6-2 by locking the flanges 6-1 and 6-2. . Corresponding to this load F, a shape change occurs in the non-restraining portion 8-2 due to the strain of the restraining portion 8-1.

Step S3 of obtaining shape information: The management server 24 ( FIG. 3 ) obtains shape information including the shape change that occurs in the non-restricted portion 8 - 2 .

Presentation of shape information, etc. Step S4: The management server 24 generates presentation information including the shape information, and presents it by the information presentation unit 26 (FIG. 3). In addition, it is also possible to perform N-fold differentiation (multi-stage differentiation) on the shape information acquired in the acquisition step S3 of the shape information, so as to perform a process of making the point of change of the shape information obvious. If this processing result is reflected in the presentation information in the presentation step S4, the change point of the shape information can be made clear.

<Gasket management system 20> FIG. 3 shows the gasket management system 20 according to the first embodiment. The shim management system 20 is a system for performing the aforementioned management steps by means of information processing. The configuration shown in FIG. 3 is merely an example, and the present disclosure is not limited to such a configuration. In FIG. 3, the same parts as those in FIG. 2 are given the same symbols. The spacer management system 20 includes a strain sensor 22 , a management server 24 , and an information prompting unit 26 .

The strain sensor 22 is an example of a measuring device that measures the shape change from the shape observation part 14 set in the unconstrained part 8 - 2 , and outputs a detection signal indicating the amount of change in the shape change generated in the shape observation part 14 . In the strain sensor 22, a laser displacement meter, a camera, etc. can also be used as a device for detecting the shape change and converting it into an electrical signal.

The laser displacement meter irradiates the shape observation part 14 with laser light, detects the shape change of the shape observation part 14 by the reflected light, and observes the change amount. The camera captures the shape observation unit 14, and the management server 24 detects the shape change detected by the strain sensor 22 by the number of pixels, and acquires shape change information corresponding to the strain.

The management server 24 is constituted by 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) or a hypervisor in the storage unit 30 to perform information processing for shim management. The storage unit 30 includes a storage medium storing the OS and the hypervisor. A spacer management database (DB) 36 ( FIG. 4 ) is stored in the storage unit 30 . The communication unit 34 is connected to a management terminal (not shown) under the control of the processor 28 to input or present information. The management terminal can also be utilized for acquisition of shape information, writing or reading of the spacer management DB 36 , and the like.

The information presentation unit 26 presents management information including load information or determination information associated with change information indicating a shape change, under the control of the management server 24 .

<Information processing of the management server 24> The information processing of the management server 24 includes: a) Import processing of the detection output of the strain sensor 22 b) Obtaining the shape information of the gasket 8 including the shape change of the non-binding portion 8-2 c) Presentation of information by the information presentation unit 26 and so on.

<Gasket management DB36> FIG. 4 shows an example of the pad management DB 36 . The shim management file 38 is stored in this shim management DB 36 . In this gasket management file 38, as an example of gasket management information, a gasket information section 40, a shape detection information section 41, a time information section 42, a load information section 44, a strain sensor information section 46, The detection information part 48 and the history information part 50 .

In the spacer information section 40 , in addition to the identification information of the spacer 8 , specification information for specifying the spacer 8 is also stored.

The shape detection information unit 41 stores information about the shape observation units 14-1, 14-2, 14-3, and 14-4, such as Example 1 ( FIG. 6 ), Example 2 ( FIG. 8 ), Example 1 3 (FIG. 10) etc., the shape observation part information such as the arrangement position is stored.

The time information unit 42 stores time information such as the observation date and time.

The load information section 44 stores load information such as the load F applied between the flanges 6-1 and 6-2 by the locking of the bolts 10, the load conditions thereof, and the like.

The strain sensor information section 46 stores the type of the sensor that observes the shape change, and the like.

The detection information unit 48 stores 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 of shape change, load, and information presentation.

<Effects of the first embodiment> According to this first embodiment, any of the following effects can be obtained.

(1) 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 shows the locked state of the gasket 8. FIG. Then, by observing the shape change of the gasket 8 by the shape observation part 14, the locking state of the gasket 8 can be grasped and the locking state can be managed.

(2) The change in the shape of the gasket 8 indicates the airtightness between the flanges 6-1 and 6-2 formed by the gasket 8 located between the flanges 6-1 and 6-2. If the gasket itself is directly observed With this change in shape, the tightness between the flanges 6-1 and 6-2 can be easily evaluated.

(3) Compared with the conventional management by the torque value or the axial force value of the bolt, the locking management accuracy of the gasket 8 can be improved without depending on the skill of the practitioner.

[Second Embodiment] The management method of the spacer 8 of the second embodiment is the management method of the first embodiment, and further includes an estimation step S5 based on inflection point information. In the estimation step S5 using the inflection point information, the shape information includes the inflection point information of the shape change caused by the specific load F, and the management server 24 can calculate the inflection point to be assigned to the spacer from the inflection point. 8 load F.

The inflection point is a state in which the shape change in the circumferential direction of the spacer 8 is greatly changed, for example, and includes a minimum point. The minimum point is the point at which the change direction of the shape change changes, for example, the transition point from the compressed state to the stretched (stretched) state, or from the stretched (stretched) state to the compressed state.

<Effects of the second embodiment> According to the second embodiment, any of the following effects can be obtained.

(1) The inflection point information can be obtained from the shape information as the specific information of the shape change.

(2) This inflection point information is associated with the load F to be added to the gasket 8, whereby the inflection point information is confirmed from the shape information, and the load of the gasket 8 can be optimized.

(3) The load setting or the load adjustment of the spacer 8 can be easily performed.

[third embodiment] FIG. 5 shows the gasket management system 20 according to the third embodiment. The configuration shown in FIG. 5 is merely an example, and the technology of the present disclosure is not limited to such a configuration.

This gasket management system 20 is disposed between the flanges 6-1 and 6-2, and uses a spiral gasket as an observation object for the change in shape due to the load F received from the flanges 6-1 and 6-2. Sheet 80. For example, as shown in FIG. 5 , this gasket 80 is a laminate in which a plurality of members with different diameters are coaxially arranged, and includes an outer ring 801 , a gasket 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 shape with a predetermined thickness or a shape close thereto.

The gasket body 802 is formed by spirally winding a laminated body of a thin plate-shaped member formed of a metal material and a buffer material (filler) such as graphite or fluororesin between the inner wall surface of the outer ring 801 and the outer wall of the inner ring 803. constituted. The layered body constituting the gasket body 802 is formed in, for example, a "V" shape in cross section or a waveform close to it. The end faces of this laminate are fixedly connected to the outer ring 801 and the inner ring 803 by spot welding, for example.

In the gasket 80, for example, in the flange fastening portion 2, only the inner ring 803 or 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). The restraint part 8-1 which receives the load F may be connected. That is, the spacer 80 is a part or the whole of the outer ring 801 as the non-restricting portion 8-2. The gasket 80 deforms the gasket body 802 in response to the load F from the flanges 6-1 and 6-2, and the outer ring 801 is strained by the deformation.

In this spacer management system 20 , for example, the shape observation unit 14 is provided on a part of the outer ring 801 , which is the non-restrained part 8 - 2 , and the shape of the outer ring 801 such as strain is measured by the strain sensor 22 . Variety. Furthermore, the shim management system 20 grasps the load F applied to the shim 80 or the locking state of the shim using the amount of change in the shape change. The management processing of the lock state of the gasket 80 may be performed in the same manner as in the above-described embodiment.

<Effects of the third embodiment> According to the third embodiment, any of the following effects can be obtained.

(1) The same effects as those of the first embodiment and the second embodiment can be obtained.

(2) Even when the spiral spacer 80 is used, the locked state can be grasped by measuring the shape change of the non-restricted portions 8-2 of the flanges 6-1 and 6-2. [Example]

<Example 1> A of FIG. 6 shows the gasket 8 of the first embodiment. In this Example 1, the restraint part 8-1 and the non-restraint part 8-2 are set in the shape of a concentric circle with the same width or almost the same width. The restraining portion 8-1 is on the same plane on the gasket 8, and it can also be an area that is automatically determined to be abutting portion, as long as the non-restraining portion 8-2 is an area deviating from the gasket seat 16, the aforementioned contact The contact portion is the contact portion with the gasket seat 16 of the aforementioned flanges 6-1, 6-2.

FIG. 6B shows the spacer 8 in which the plurality of shape observation parts 14-1, 14-2, 14-3, and 14-4 are arranged. Each shape observation part 14-1, 14-2, 14-3, 14-4 is arrange|positioned in the non-restriction part 8-2 at the angular interval of 90 degrees of center angles. θ is an angular range in which the shape observation parts 14-1, 14-2, 14-3, and 14-4 are displayed and set. The arrangement position of each of the shape observation parts 14-1, 14-2, 14-3, and 14-4 can be set at a position that does not overlap with the arrangement position of the bolt 10, but is not limited to this.

Fig. 7 shows the load [kN] on the horizontal axis, and the strain (shape change) on the vertical axis, and the angle = 0 (deg), 45 (deg), 90 (deg) is used as a parameter, and the strain is displayed. The sensor 22 measures the measurement value of the shape change which occurs in the gasket 8 of the first embodiment.

m1 is the deformation of the spacer 8 showing the 0 (deg) direction (=the circumferential direction of the spacer 8), m2 is the deformation of the spacer 8 showing the 45 (deg) direction, m3 is the deformation of the spacer 8 showing the 90 (deg) direction (=mat deformation of the sheet 8 in the thickness direction).

When the restraint portion 8-1 receives the load F from the flanges 6-1 and 6-2 in this way, a shape change according to the load F occurs in the non-restraint portion 8-2. An inflection point is generated in this shape change, and the optimal 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 this can be used as information for judging the completion of the initial tightening .

<Example 2> A of FIG. 8 shows the gasket 8 of the second embodiment. In this Example 2, similarly to Example 1, the restraint part 8-1 and the non-restraint part 8-2 are set concentrically with the same width or almost the same width.

In the unrestricted portion 8-2, an outer cutout 54 is formed in each of the shape observation portions 14-1, 14-2, 14-3, and 14-4. In addition, the notch 54 is formed in the outermost edge part of the non-restriction part 8-2 of the spacer 8, and is a notch shape which has a non-closed part in a part.

In Example 2, a plurality of outer notches 54 are formed in the spacer 8, and the outer notches 54 are arranged in the non-restricting portion 8-2 at angular intervals of 90 degrees from the center angle.

For example, as shown in B of FIG. That is, the outer cutout 54 has a vertical surface portion 56 on the inner side of the spacer 8, and has parallel surface portions 58 and 60 facing each other with a certain width W1.

When a load F is applied from the flanges 6-1 and 6-2 to the restraint portion 8-1 of the spacer 8 having such an outer cutout 54, as shown in FIG. 8C, in accordance with the load F, the vertical The face portion 56 expands as indicated by the arrow a and is displaced in the peripheral direction. In addition, the parallel surface parts 58 and 60 are developed in the peripheral direction as shown by arrows b and c. At this time, the edge surface of the spacer 8 extends outward as indicated by the arrow d.

Shape changes like this can be easily detected by the strain sensor 22 . In addition, a sensor member such as metal or resin may be provided in the space portion of the outer cutout 54, and the shape change of the outer cutout 54 may be obtained from this sensor member.

9 shows the load [kN] on the horizontal axis, and the opening width (shape change) [mm] of the outer cutout 54 on the vertical axis, and shows the shape change and the load appearing in the gasket 8 of Example 2. relation. Similarly, Table 1 shows the relationship between the opening width W2 of the outer cutout 54 and the load F.

[Table 1] Load F[kN] Opening width W2[mm] 0 1 25 1.1 50 1.3 75 1.5 100 1.7 125 2.5 150 3.2

When the restraint portion 8-1 receives the load F from the flanges 6-1 and 6-2, and the load F of the restraint portion 8-1 is increased, the opening width W2 of the cutout 54 is equal to the change in shape with respect to the load F. will increase. Inflection points are created in this shape change. Therefore, in the case of using the second embodiment, as long as the inflection point of the shape change that occurs in the shape observation parts 14-1, 14-2, 14-3, and 14-4 is set as the target, the shape change and the shape change can be specified. The relationship of the load F.

<Example 3> A of FIG. 10 shows the gasket 8 of the third embodiment. In this Example 3, similarly to Example 1, 2, the restraint part 8-1 and the non-restraint part 8-2 are set to the same width or almost the same width|variety in the shape of a concentric circle.

In the unrestricted portion 8-2, the inner cutout 62 is formed in each of the shape observation portions 14-1, 14-2, 14-3, and 14-4. The inner cut 62 is a through opening formed in the unconstrained portion 8 - 2 of the gasket 8 .

Although each inner cutout 62 is arrange|positioned at the non-restriction part 8-2 at the angular interval of the center angle of 90 degrees, it is not limited to this.

As shown in FIG. 10B , the inner cut 62 is an arc-shaped groove portion concentric with the peripheral edge of the gasket 8 and having a constant width W, and penetrates through the upper and lower surfaces of the gasket 8 . That is, the inner notch 62 has vertical surface parts 64 and 66 on the inner side of the spacer 8, and has concentric circular arc parts 68 and 70 facing each other with a constant length L2 and width W3.

When a load F is applied from the flanges 6-1 and 6-2 to the restraint portion 8-1 of the gasket 8 having such an inner cut 62, as shown in C of FIG. As indicated by arrows e and f, the distance between the arcuate portions 68 and 70 is reduced, and the edge surface of the spacer 8 extends outward as indicated by arrow g. Shape changes like this can be easily detected by the strain sensor 22 .

In addition, a sensor member such as metal or resin may be provided in the space portion of the inner cutout 62, and the shape change of the inner cutout 62 may be obtained from the sensor member.

11 shows the load [kN] on the horizontal axis and the strain (shape change) of the inner cut 62 on the vertical axis, and shows the relationship between the shape change and the load of the gasket 8 occurring in Example 3.

When the restraint portion 8-1 receives the load F from the flanges 6-1 and 6-2, and the load F on the restraint portion 8-1 increases, the shape of the cutout 62 changes within the change of the load F. In this shape change, a minimum point included in the inflection point is generated. In the third embodiment, the relationship between the shape change and the load F can be specified by using such a minimum point as a target. This minimum point is, as mentioned earlier, the point at which the change direction of the change in the shape change occurring in the unconstrained portion 8-2 of the gasket 8 changes, that is, the inner cut 62 goes from a compressed state to an elongated (stretched) state, or is the transition point from an elongated (stretched) state to a compressed state.

Therefore, according to Example 3, in the relationship between the load F and the shape change, although the minimum point appears conspicuously due to the shape change in the circumferential direction, there may be a case where the minimum point=inflection point. In addition, there may be cases in which the shape change in the circumferential direction does not generate a minimum point, that is, an inflection point where the shape change in the circumferential direction greatly changes.

<Detection of Inflection Point of Shape Information and Clamping Criteria> As shown in Example 1, Example 2, and Example 3, inflection points can be generated in the shape information corresponding to a specific load F. In this way, when the flanges 6-1 and 6-2 are locked, the specific load F can be estimated from the inflection point of the shape information, and this can be used as a criterion for determining the completion of the locking.

<Comparison of Examples 1, 2, and 3>

[Table 2] Example 1 Example 2 Example 3 No external incision and internal incision 3-1 3-2 3-3 shape width[mm] ― 1 1 2 1 length [mm] ― 3 30 30 50 Opening width W2 [mm] of the outer cutout 54 under a load of 125 kN ― 2.5 ― ― ― Inflection point load of circumferential strain [kN] 140 125 135 115 120 Minimum point load of circumferential strain [kN] none none 135 115 120

Table 2 shows the shapes, their shape changes, and inflection points for Example 1 (=outer incision 54 and inner incision 62: none), Example 2 (=outer incision 54), and Example 3 (=inner incision 62). .

In Example 1, the outer cutout 54 and the inner cutout 62 are not processed. In Example 2, the outer cutout 54 having the width W1=1 mm and the length L1=3 mm was formed. In Example 3-1, the width W3 = 1 mm and the length L2 = 30 mm were set for the inner cutout 62 . In Example 3-2, the width W3=2 mm and the length L2=30 mm were set. In Example 3-3, the width W3=1 mm and the length L2=50 mm were set.

In Example 1, the inflection point load=140 kN was obtained from the shape change in the circumferential direction, but the minimum point load was not obtained. In Example 2, the inflection point load=125 kN was obtained from the shape change in the circumferential direction, but the minimum point load was not obtained. In Example 3-1, the inflection point load=135kN can be obtained from the shape change in the circumferential direction, and the minimum point load=135kN can be obtained. In Example 3-2, the inflection point load=115kN can be obtained from the shape change in the circumferential direction, and the minimum point load=115kN can be obtained. In Example 3-3, the inflection point load=120kN can be obtained from the shape change in the circumferential direction, and the minimum point load=120kN can be obtained.

<Effects of Examples 1, 2, and 3> As is clear from Examples 1, 2, and 3 as described above, in the outer cutout 54, the opening width W2 of the cutout shape is measured from the side surface, whereby the appropriate load F can be estimated. When the outer notch 54 is used for shape detection, the opening width W2 of the outer notch 54 can be measured in advance according to the load F applied to the spacer 8 , and the load F can be estimated by comparing the opening width W2 with the measured value. In this estimation, the opening width W2 of the outer cutout 54 is databased for each load F, and the load F can be easily and accurately calculated by comparison with the actual measurement value of the shape change.

In the inner notch 62, the flanges 6-1 and 6-2 receive the load F, and the inner wall surface of the through-hole-shaped inner notch 62 is closed (contacted), thereby obtaining a remarkable change.

In the monitoring and measurement of such shape change, the shape change of the non-restraining portion 8-2 (Example 1) and the shape change of the outer cutout 54 (Example 2) are measured, unlike torque management and measurement of the bolt axial force. ), the shape of the inner cut 62 is changed (Example 3), and the change of 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 bolts 10 or the flanges 6-1 and 6-2.

Regarding the processing shape of the outer cutout 54 or the inner cutout 62 , it has been confirmed that the spacer 8 can also correspond to various diameters and thicknesses.

<Example 4> FIG. 12 shows a configuration example of the gasket 80 of the fourth embodiment. In the fourth embodiment, for example, in the spiral spacer 80, at least the outer ring 801 constitutes the non-restricted portion 8-2. In this Example 4, the shape changes Qa, Qb or the shape changes R, which are measured on the outer edge side or the inner edge side of the outer ring 801 of the gasket 80 in the circumferential direction, are the measurement objects. The shape change that expands and contracts, and the aforementioned shape change R is a shape change that expands and contracts in the radial direction of the spacer 80 .

<Measurement of shape changes Qa and Qb in the circumferential direction> A of FIG. 13 shows the load [kN] on the horizontal axis and the strain (shape change) in the circumferential direction on the vertical axis, and shows the shape change Qa occurring at the outer edge of the outer ring 801 measured by the strain sensor 22 The measured value of Qb with the shape change occurring at the inner edge.

In the outer ring 801, the strain on the inner edge side is larger than the strain on the outer edge side. That is, since the shape of the outer ring 801 is greatly changed on the inner edge side, the behavior of the change of the spacer 80 or the spacer body 802 due to the load F can be easily detected.

<Measurement of the shape change Qb in the circumferential direction and the shape change R in the radial direction> 13B shows the load [kN] on the horizontal axis and the strain (shape change) on the vertical axis, and shows the shape change Qb occurring in the circumferential direction of the inner edge of the outer ring 801 measured by the strain sensor 22 The measured value of the shape change R that appears in the radial direction.

From the measurement results, in the shape change Qb in the circumferential direction, since the measured value increases in the positive direction as the gasket surface pressure increases, it can be grasped that the force in the tensile direction is acting. In addition, in the radial shape change R, since the measured value increases in the negative direction as the gasket surface pressure increases, it can be grasped that it is in a compressed state.

<Example 5> A of FIG. 14 shows a configuration example of the gasket 80 of the fifth embodiment. In this Embodiment 5, for example, at least the outer ring 801 constitutes the non-restricting portion 8-2. In this Example 5, the inner notch 82 of a predetermined length is formed in a part of the outer ring 801 of the spacer 80 along the outer periphery. This inner cut 82 is a through opening formed in the unconstrained portion 8 - 2 of the gasket 8 . The inner notch 82 is formed at a predetermined distance t of 5 [mm] from the outer edge of the outer ring 801 , for example. In this Embodiment 5, for example, the shape observation portion 14 is provided on the outer edge portion along the formation position of the inner cutout 82 .

For example, as shown in FIG. 14B , before the load F from the flanges 6-1 and 6-2 is applied to the gasket body 802 in the outer ring 801, the inner cutout 82a is opened with a predetermined width such as 0.1 [mm]. When the load F acts on the gasket body 802, the outer ring 801 deforms a part or the whole of the opening as shown in, for example, C of FIG. In Example 5, the shape change Qc of the outer ring 801 is measured when the surface pressure of the gasket due to the load F and the state of the inner cut 82b are measured.

FIG. 15 shows the load [kN] on the horizontal axis and the strain (shape change) on the vertical axis, and shows the measured value of the shape change Qc measured by the strain sensor 22, the shape change Qc occurring in and outside The shape of the outer edge in the circumferential direction changes according to the formation position of the inner cut 82b of the ring 801 .

In this measurement result, when the load of the gasket increases, for example, the strain does not change greatly from the beginning to a predetermined value, and then when the load exceeds the predetermined value, the strain sensor will A negative value was measured. This is a change in shape that produces, for example, a case of showing compression in which the outer edge portion of the outer ring 801 is compressed in the circumferential direction. In addition, the strain in the circumferential direction is increased in the positive direction after the minimum point appears in the vicinity of, for example, a load of 220 kN.

<Effects of Examples 4 and 5> According to Examples 4 and 5, the following effects can be expected.

(1) By measuring the shape change of the outer ring 801 of the spiral gasket 80 sandwiched between the flanges 6-1 and 6-2, the surface pressure of the gasket 80 due to the load F can be grasped.

(2) In the spiral spacer 80, depending on the shape characteristics of the spacer body 802 formed in the winding shape, the state of strain according to the measured position of the outer ring 801 is different, and the spacer can be grasped in detail. The state of the sheet and the state of the load.

(3) Due to the spiral gasket 80, the gasket body 802 and the outer ring 801 are different components, so compared with the sheet gasket composed of a single component, although the 6-2 and 6-2, the strains generated in the unconstrained portion 8-2 tend to be different, but the load F applied from the flanges 6-1 and 6-2 can be estimated from the change in the shape of the gasket 80.

(4) The inner notch 82 formed in the spiral gasket 80 closes the opening by the load F from the flanges 6-1 and 6-2, whereby the strain generated in the outer ring 801 can be significantly changed .

(5) In the monitoring or measurement of the shape change in the flange fastening portion 2 using the spiral washer 80 , unlike torque management or measurement of the bolt axial force, it is possible to measure the change in the outer ring 801 by measuring The shape changes Qa, Qb, R (Example 4) and the shape of the inner cut 82 (Example 5) are changed, and the change representing the load F is obtained from the spacer 8 . Therefore, the load F applied to the flanges 6-1 and 6-2 can be estimated from the shape change of the washer 80 without being affected by the bolts 10 or the flanges 6-1 and 6-2.

[other embodiments] (1) Regarding the outer cutout 54, although the vertical surface part 56 and the parallel surface parts 58 and 60 are illustrated in the second embodiment, these are only examples. The outer cutout 54 may have a shape that does not have the vertical surface portion 56 , or may have a non-parallel shape such as a V shape in which the parallel surface portions 58 and 60 are non-parallel.

(2) Regarding the inner cutout 62 , although the concentric circular arc portions 68 and 70 are illustrated in Example 3, these are merely examples. The inner cutout 62 may be in the shape of the arc portions 68 and 70 not having a constant width, and may be a parallel surface or a non-parallel surface instead of the arc shape.

(3) In the step of presenting shape information and the like ( S4 ) in the management step of the spacer 8 , the management server 24 may also generate a presentation by performing a process such as multi-stage differentiation on the acquired shape information. The information may be presented on the information presentation section 26 (FIG. 3) on a display section that clearly indicates the change point.

As described above, the preferred embodiments and the like of the present disclosure have been described. The present disclosure is not limited to the disclosure described above. Those with ordinary knowledge in the technical field to which the present invention pertains can make various modifications or changes in accordance with the gist of the invention described in the scope of the claims or disclosed in the form for carrying out the invention. Of course, such deformations and changes are also included in the scope of the present disclosure. industrial availability

According to the gasket management method, system, and program-recorded medium of the present disclosure, without measuring the axial force or torque value of the bolts that fasten between the flanges, the damage caused by the load received from the flanges is observed. The shape of the gasket changes, and the load on the gasket can be calculated from the shape information without being affected by the locking state of the bolt or flange, and can be used for management information such as gasket replacement. Revealing is helpful.

2: Flange fastening part 4-1, 4-2: Pipeline 6-1, 6-2: Flange 8,80: Gasket 8-1: Restraint Department 8-2: Unrestrained Section 10: Bolts 12: Nut 14, 14-1, 14-2, 14-3, 14-4: Shape Observation Department 16: Gasket seat 18: Gap 20: Gasket Management System 22: Strain sensor 24: Manage Servers 26: Information Reminder Department 28: Processor 30: Storage Department 32: Input and output (I/O) part 34: Communications Department 36: Gasket Management Database (DB) 38: Gasket Management File 40: Gasket Information Department 41: Shape Detection Information Department 42: Time Information Department 44: Load Information Department 46: Strain Sensor Information Department 48: Inspection and Information Department 50: Resume Information Department 54: External incision 56: Vertical Face 58,60: Parallel face 62, 82, 82a, 82b: Internal incision 64,66: Vertical face 68,70: Arc part 801: Outer ring 802: Gasket body 803: inner ring a,b,c,d,e,f,g: arrows F: load II-II: Line L1, L2: length m1,m2,m3: deformation Qa, Qb, Qc, R: shape change W1,W2,W3: width X: X axis Y: Y axis Z: Z axis

FIG. 1 is a view showing a flange fastening portion of the first embodiment. FIG. 2 is a view showing a cut end face of a portion along the line II-II in FIG. 1 . Fig. 3 is a diagram showing a gasket management system according to the first embodiment. FIG. 4 is a diagram showing a shim management database. Fig. 5 is a diagram showing a gasket management system according to a third embodiment. FIG. 6A is a diagram showing the gasket of Example 1, and B is a diagram showing an example of a shape observation portion with respect to the gasket. FIG. 7 is a diagram showing a change in shape with respect to a load in the gasket of Example 1. FIG. FIG. 8A is a view showing the gasket of Example 2, B is a perspective view showing an outer cutout of the spacer, and C is a view showing a shape change that occurs in the outer cutout. FIG. 9 is a diagram showing the shape change with respect to the load in the incision other than Example 2. FIG. FIG. 10A is a view showing the gasket of Example 3, B is a perspective view for explaining an inner cut, and C is a view showing a shape change that occurs in the inner cut. FIG. 11 is a diagram showing a shape change with respect to a load in the gasket of Example 3. FIG. FIG. 12 is a view showing an example of the shape observation of the gasket of Example 4. FIG. 13 is a shape observation example of Example 4, A is a diagram showing the shape change on the outer diameter side and the inner diameter side, and B is a diagram showing the shape change in the circumferential direction and the radial direction. 14A is a diagram showing the shape of the gasket of Example 5, B is a diagram showing an example of a state before applying a load, and C is a diagram showing an example of a state when a load of a predetermined value is applied. FIG. 15 is a diagram showing an example of shape observation in Example 5. FIG.

4-1, 4-2: Pipeline

6-1, 6-2: Flange

8: Gasket

8-1: Restraint Department

8-2: Unrestrained Section

14-2: Shape Observation Department

16: Gasket seat

18: Gap

F: load

X: X axis

Y: Y axis

Z: Z axis

Claims (4)

A management method is characterized in that: comprise the following steps: the step of applying a load to the gasket restrained between the flanges; and The step of observing the change in shape of the gasket due to the load, The locking of the aforementioned spacer is managed according to the aforementioned shape change. The management method according to claim 1, wherein the shape change includes any one or both of a change in a spacing direction between at least the flanges of the gasket, or a change in a direction intersecting the spacing direction. A management system is characterized by comprising: Measuring components, measuring the shape change of the gasket that is bound between the flanges and bears the load; a management server for generating management information for managing the locking between the flanges according to the shape change; and The information prompting department prompts the aforementioned management information. A medium on which a program is recorded, the aforesaid program is a program used by a computer to realize the following functions: A function of obtaining shape information representing a change in shape, which is a change in shape of the gasket due to the load being received between the flanges when the gasket is restrained between the flanges; and A function of generating management information for managing the locking of the gasket based on the shape change.

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