JP6472283B2 - High temperature gas valve sealing device - Google Patents

Description

  The present invention relates to a sealing device for sealing a gap between a housing and a shaft in a hot gas valve.

  In an internal combustion engine, a butterfly valve, a poppet valve, or the like is used as a high-temperature gas valve for sucking or exhausting high-temperature gas. This high-temperature gas valve includes a valve body, a shaft that drives the valve body, and a housing that houses the valve body. The housing includes a main body housing for accommodating the valve body, and an extension housing extended from a partial opening of the main body housing, and one end side of the shaft is inserted into the main body housing from the extension housing through the partial opening. The other end side is connected to the shaft drive mechanism.

  The sealing device is mounted in a gap between the extension housing and the shaft, and seals the gap so that hot gas in the main body housing does not leak from the gap to the shaft drive mechanism side through the partial opening.

  In addition, a few examples of patent documents related to such a sealing device are listed below.

Japanese Patent No. 5345708 Japanese Patent No. 5335167 Japanese Patent No. 4307213

  Since the high-temperature gas valve used for the internal combustion engine described above has a gas temperature of 650 ° C. to 800 ° C. or higher, it is expected that the periphery of the gap where the seal device is mounted is in a high-temperature environment of 500 ° C. or higher. Therefore, the sealing device is required to have heat resistance. In addition, since the shaft rotates and reciprocates in the housing, the seal device also needs to have wear resistance and strength that do not wear early due to sliding contact between the housing and the shaft.

  Furthermore, as a sealing device for high-temperature gas valves, in addition to the required heat resistance, wear resistance, and strength performances, the clearance is accurately determined according to the size of the clearance between the housing and the shaft. It is desirable to have a sealing device that can be sealed.

  The present invention has been made in view of the above, and in addition to the basic performance of heat resistance, wear resistance, and high strength, the gap can be accurately sealed according to the size of the gap between the housing and the shaft. An object of the present invention is to provide a sealing device that can stably exhibit desired sealing performance for a long period of time even when used in a severe high temperature environment for a high temperature gas valve.

  In order to solve the above problems, the present invention provides the following means.

A sealing device according to the present invention is a sealing device that is incorporated in a gap between a housing and a shaft that rotates or reciprocates in the housing and seals the gap in the axial direction.
An annular seal member braided with inorganic fibers and wider in the radial direction than in the axial direction ;
A pair of pressing plate members that are sandwiched from both sides of the seal member and maintain the sandwiched state, and are wider in the radial direction than the axial direction ;
With
A radially inner end of the seal member protrudes radially inward from a radially inner end of the pressing plate member,
A radially outer end of the seal member protrudes radially outward from a radially outer end of the pressing plate member,
When the sealing member is compressed in the axial direction by the clamping force of the pressing plate member, the radial inner end of the sealing member further protrudes radially inward, and the radial outer end of the sealing member has a radius It is possible to protrude further outward in the direction ,
The seal member is formed of a plurality of intermediate bodies that are braided with the inorganic fibers and have different radii.
The intermediate bodies are juxtaposed in the radial direction and sandwiched between the pressing plate materials,
It is characterized by that.

  According to the present invention, since the seal member is made of braided inorganic fibers, the seal member has high heat resistance, high wear resistance, and high strength, and the seal member is axially formed from both sides by a pair of pressing plate materials. Since it is pressed and compressed, the inorganic fibers are densely compressed, thereby having a high-density sealing performance. In addition, the protruding amount of the radially inner end and the radially outer end of the seal member can be appropriately controlled by adjusting the pressure compression by the pressing plate material, so the seal member can be used for the outer peripheral surface of the shaft or the inner periphery of the housing. A sufficient sealing effect is obtained by contacting these surfaces with an appropriate surface pressure without damaging the surfaces, thereby sealing a target gap highly stably over a long period of time, thereby preventing leakage of hot gas. It can be effectively prevented.

Preferably, the seal member is formed of a plurality of intermediate bodies that are braided with the inorganic fibers and have different radii.
The intermediate bodies are juxtaposed in the radial direction and sandwiched between the pressing plate members.

Preferably, the seal member is composed of a plurality of intermediate bodies each having a rounded sheet body in which the inorganic fibers are braided and having different radii.
The intermediate bodies are juxtaposed in the radial direction and sandwiched between the pressing plate members.

  Preferably, each of the seal members includes a plurality of intermediate bodies in which the sheet body in which the inorganic fibers are braided is folded and the radii are sequentially different, and the intermediate bodies are juxtaposed in a radial direction, It is sandwiched between.

  Preferably, a relationship between a radially inward protruding amount C1 of the inner end of the seal member from the pressing plate member and a radial seal width A of the seal member is 0.1 ≦ C1 / A ≦ 0. .4 inequality is satisfied.

  Preferably, the relationship between the amount C2 of the radially outer end of the seal member projecting radially outward from the pressure plate and the seal width A in the radial direction of the seal member is 0.1 ≦ C2 / A ≦ 0. .4 inequality is satisfied.

  Preferably, when C1 = C2 = C, the relationship between the seal width A in the radial direction of the seal member and the protrusion amount C satisfies an inequality of 0.1 ≦ C / A ≦ 0.4. .

  According to the present invention, in addition to the basic performance of heat resistance, wear resistance, and high strength, the gap can be accurately sealed according to the size of the gap between the housing and the shaft. Even when used in an environment, the desired sealing performance can be exhibited stably over a long period of time.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a schematic cross-sectional view of a high-temperature gas valve provided with a sealing device according to Embodiment 1 of the present invention. The top view of FIG. The elements on larger scale of a sealing member. The schematic structure sectional drawing of the high temperature gas valve provided with the sealing device of Embodiment 2 of the present invention. In Embodiment 2, the front view of a sealing device. In Embodiment 2, the perspective view of a sealing member. The schematic structure sectional drawing of the high temperature gas valve provided with the sealing device of Embodiment 3 of the present invention. In Embodiment 3, it is a perspective view of a sheet. In Embodiment 3, the perspective view in the middle of rounding the sheet | seat of FIG. In Embodiment 3, the perspective view of the state which rounded the sheet | seat of FIG. In Embodiment 3, the perspective view which made the seal | sticker of FIG. 9 cyclic | annular. The schematic structure sectional drawing of the high temperature gas valve provided with the sealing device of Embodiment 4 of the present invention. In Embodiment 4, it is a perspective view of a sheet. The perspective view in the middle of folding the sheet | seat of FIG. The perspective view of the state which folded the sheet | seat of FIG. The perspective view which made the sealing member of FIG. 14 annular. The schematic block diagram of the sealing device of other embodiment. Furthermore, the schematic block diagram of the sealing device of other embodiment. Furthermore, the schematic block diagram of the sealing device of other embodiment.

  Hereinafter, a sealing device according to an embodiment of the present invention will be described with reference to the accompanying drawings.

(Embodiment 1)
The first embodiment will be described with reference to FIGS. 1 to 3.

  1 is a schematic side cross-sectional view of a high-temperature gas valve provided with a sealing device according to Embodiment 1 of the present invention, FIG. 2 is a schematic plan view, and FIG. 3 is a partially enlarged view of a main part of the sealing device. It is.

  1 and 2, reference numeral 1 denotes a high-temperature gas valve such as a butterfly valve or a poppet valve disposed in an intake gas or exhaust gas passage in an internal combustion engine.

  The hot gas valve 1 includes a housing 2. The housing 2 has a main body housing 2a and an extension housing 2b, and a partition wall 3 is provided on the extension housing 2b. The main body housing 2a is disposed on the passage side 4 for intake and exhaust of hot gas, and a valve body (not shown) is provided inside. The inside of the extension housing 2b is the shaft drive mechanism side 5 into which the shaft 6 is inserted.

  The shaft 6 is a shaft that rotates and reciprocates in the extension housing 2b to drive the valve body, and one end side 6a thereof is connected to the valve body in the passage side 4 through the opening 3a of the partition wall 3, The other end 6b extends outside the extension housing 2b and is connected to a shaft drive mechanism (not shown).

  The shaft 6 is driven to rotate in the housing 2 when the hot gas valve 1 is a butterfly valve, and is reciprocated along the axial direction in the housing 2 when the hot gas valve 1 is a poppet valve.

  The sealing device 8 is disposed in the extension housing 2b, and hot gas in the main body housing 2a enters the extension housing 2b from the opening 3a of the partition wall 3, and further extends from a gap between the extension housing 2b and the shaft 6. The gap is sealed (closed) inside and outside in the axial direction so as not to leak to the shaft drive mechanism side outside the housing 2b.

  The sealing device 8 includes a sealing member 9, a pair of pressing plate members 10 a and 10 b, and a fastening member 11. The seal member 9 is an annular member formed by braiding inorganic fibers and wide in the radial direction.

  As shown in FIG. 3A, for example, as shown in FIG. 3A, the sealing member 9 is a braided braided braided into a square braided body by reinforcing braids 91 for reinforcing the outer periphery and reinforcing braids 92 for reinforcing the inside. Gland packing. Further, as shown in FIG. 3 (b), the seal member 9 is provided on the knitting yarn passing through one opposing corner and the path 93 passing through the inside, or the other opposing corner and the path 94 passing through the inside. The reinforcing knitting yarn 91 is used.

  A reinforcing knitting yarn 92 is used for the knitting yarn passing through the four side surfaces of the seal member 9 and the path 95 passing through the inside. The reinforcing knitting yarn 91 is provided with a reinforcing material on the outer periphery of the expanded graphite. As such reinforcing knitting yarns 91 and 92, a plurality of strip-shaped expanded graphite sheets having a predetermined thickness and a predetermined width are laminated, and the surface thereof is coated with high-strength fibers by knitting or bag knitting, or metal A material obtained by spirally winding the outer circumference of expanded graphite with a wire or the like is used.

  Specific examples of the high-strength inorganic fiber include carbon fiber, metal fiber, aramid fiber, glass fiber, and ceramic fiber. The metal wire is made of stainless steel, copper alloy, aluminum alloy, monel, inconel, or the like. Inorganic fibers include these composite materials. Moreover, a reinforced inorganic fiber is included. A composite reinforcing material in which glass fiber or metal fiber is reinforced with carbon fiber may be used. A reinforcing material in which silicon carbide fibers are combined with ceramics may be used. When inorganic fibers are classified by crystal, amorphous fibers such as glass fibers and rock wool, polycrystalline fibers such as carbon fibers and alumina fibers, and single crystal fibers such as wollastonite and potassium titanate fibers may be used.

  Returning to FIG. 1 and FIG. 2, the pressing plate members 10 a and 10 b are annular plate members that are wide in the radial direction and sandwich the sealing member 9 from both surfaces. The holding plate members 10a and 10b are mainly made of a metal material having heat resistance against a high temperature of 500 ° C. or higher, for example, stainless steel.

  The fastening member 11 is made of a screw, penetrates the sealing member 9 from the upper pressing plate material 10a, is inserted into the lower pressing plate material 10b, and is tightened to fix the sealing member 9 to the pressing plate materials 10a, 10b is compressed in the axial direction and the compressed state is maintained. The fastening member 11 is also mainly made of a metal material having heat resistance against a high temperature of 500 ° C. or higher, for example, stainless steel.

  When the sealing member 9 is compressed by the pressing plate members 10a and 10b due to the fastening force of the fastening member 11, the gap between the inorganic fibers constituting the sealing member 9 becomes extremely dense (high density), and the sealing performance is improved.

  When the sealing device 8 is mounted in an annular gap between the extension housing 2b and the shaft 6, the radially inner end of the seal member 9 is in contact with the outer peripheral surface of the shaft 6, and the radially outer end is The contact is brought into close contact with the inner peripheral surface of the extension housing 2b. Thereby, the sealing device 8 seals the gap described above.

  The seal member 9 has a predetermined seal width A in the radial direction, and the pressing plate members 10a and 10b have a predetermined pressing width B in the radial direction.

  The inner end in the radial direction of the seal member 9 protrudes radially inward from the inner end in the radial direction of the pressing plate members 10a and 10b with a predetermined protruding amount (radius inner end protruding amount) C1.

  The radially outer end of the seal member 9 protrudes radially outward from the radially outer end of the pressing plate members 10a and 10b with a predetermined protruding amount (radially outer end protruding amount) C2.

  Note that the protrusion amount of the seal member 9 in the radial direction described above is the protrusion amount when the seal device 8 is mounted on the high-temperature gas valve 1. Therefore, it is necessary to set the size of the seal member 9 before mounting in consideration of the material of the seal member 9 and the like so that the protruding amount of the seal member 9 at the time of mounting becomes the above-described value.

  Both protrusion amounts C1 and C2 may be the same protrusion amount or different protrusion amounts. These protrusion amounts C1 and C2 can be adjusted by the force between the holding plate members 10a and 10b. In other words, when the seal member 9 is compressed in the axial direction by the clamping force of the holding plate members 10a and 10b accompanying the fastening of the fastening member 11, its radially inner end protrudes further radially inward than before compression, The radially outer end can protrude further outward in the radial direction than before compression.

As shown in FIG. 1, the seal device 8 includes a seal width A in the radial direction when the seal plate 9 is compressed in the axial direction by the press plate members 10 a and 10 b, and a radial inside and outside from the press plate member of the seal member 9. The preferable relationship between the protruding amounts C1 and C2 is as follows:
0.1 ≦ C1 / A ≦ 0.4 (1)
0.1 ≦ C2 / A ≦ 0.4 (2)
Satisfies the inequality.

Of course, if C1 = C2 = C, a preferable relationship between the seal width A in the radial direction of the seal member 9 and the protrusion amount C is
0.1 ≦ C / A ≦ 0.4 (3)
Satisfies the inequality.

  In these equations, if the values of C2 / A, C1 / A, and C / A are less than 0.1, the pressing plate members 10a and 10b are in contact with the outer peripheral surface of the shaft 6 and the inner week surface of the housing 2. There arises a problem that the shaft 6 and the housing 2 may be damaged, and when it exceeds 0.4, there occurs a problem that the seal member 9 is deformed during use and the sealing performance is deteriorated. On the other hand, if the values of C2 / A, C1 / A, and C / A are 0.1 or more and 0.4 or less, the outer peripheral surface of the shaft 6 and the inner week surface of the housing 2 are damaged. Therefore, the effect of maintaining good sealing performance can be exhibited. More preferably, the values of C2 / A, C1 / A, and C / A are 0.15 or more and 0.35 or less, and most preferably 0.2 or more and 0.3 or less.

  When the seal width A of the seal member 9 and the projections C1 and C2 in the radial direction from the pressing plate members 10a and 10b of the seal member 9 are in the above-described relationship, the seal member 9 constituting the seal device 8 and the presser When the plate members 10a, 10b, etc. are made of a fragile material or a flexible material, the projecting amounts C1, C2 of the seal member 9 are too short, and the surface pressure on the shaft 6 and the housing 1 is insufficient to provide a sufficient seal. If the effect is not obtained, or conversely, the protruding amounts C1 and C2 are too long, and the outer peripheral surface of the shaft 6 and the inner peripheral surface of the housing 1 are scratched at the radially inner end and the radially outer end of the seal member 9. The risk of being reduced.

  The seal thickness D in the axial direction of the seal member 9 is a factor that affects the seal performance. If the seal thickness D is increased, an increase in the sealing effect is expected. On the other hand, if the seal thickness D is too thick, the shaft Therefore, it is preferable to appropriately select the seal thickness D by experiment.

  In the first embodiment, the number of the sealing members 9 is one, but the sealing performance may be improved by using a plurality of sealing members 9 having two or more layers.

  In the first embodiment described above, the sealing member 9 has its radially inner end protruding with a protruding amount C1 radially inward from the radially inner ends of the pressing plate members 10a and 10b before being compressed. The outer end in the radial direction protrudes outward in the radial direction from the outer end in the radial direction of the pressing plate members 10a and 10b by a protruding amount C2.

  And according to the size of the opposing gap between the shaft 6 and the housing 1, the seal member 9 is compressed in the axial direction by the axial compression force from the pressing plate members 10a, 10b accompanying the fastening of the fastening member 11. The radially inner end of the seal member 9 is further protruded radially inward to abut against the outer peripheral surface of the shaft 6 to seal a gap between the seal member 9 and the radially outer end of the seal member 9 also in the radial direction. Further projecting outwardly, it is brought into contact with the inner peripheral surface of the housing 2 to seal the gap with this.

  As a result, the gap between the inside and outside in the radial direction of the seal member 9 is sealed in accordance with the size of the seal member 9, and as a result, the shaft 6 opens and closes the valve body. Gas does not leak from the gap to the shaft drive mechanism side 5, and the gap is stably sealed.

  As described above, in the sealing device 8 according to the first embodiment, the sealing member 9 is made of braided high heat resistance, high wear resistance, and high strength inorganic fibers, and the sealing member 9 is pressed and compressed in the axial direction by the pressing plate 10. In addition to having high-density sealing performance, the protruding amounts C1 and C2 of the inner end and the outer end in the radial direction of the seal member 9 are appropriately adjusted by adjusting the pressing compression amount by the pressing plate material 10. By being controlled, a sufficient sealing effect can be obtained by contacting these surfaces with an appropriate surface pressure without damaging the outer peripheral surface of the shaft 6 and the inner peripheral surface of the housing 1, and highly stable over a long period of time. The gap can be sealed, and leakage of hot gas to the shaft drive mechanism side can be effectively prevented.

(Embodiment 2)
A second embodiment of the present invention will be described with reference to FIGS.

  The difference between the seal device 8a of the second embodiment and the seal device 8 of the first embodiment will be described. In the first embodiment, the seal member 9 is single, but in the second embodiment, the seal member 9 is different. As shown in FIG. 4, it is comprised of a plurality of string-like intermediate bodies 9a to 9f that are sequentially wound around the shaft 6 in an annular shape. These intermediate bodies 9a to 9f are juxtaposed between the pair of pressing plate members 10a and 10b.

  In such juxtaposed state of the intermediate bodies 9a to 9f, before the pressing plate members 10a and 10b are pressed by the fastening member 11, the intermediate bodies 9a to 9f are substantially circular in cross section and have a diameter equal to or larger than a predetermined value. In the whole 9a-9f, the radial seal width is a certain value or more. In this state, when the intermediate bodies 9a to 9f are pressed and compressed by the pressing plate members 10a and 10b, the cross section is deformed into an elliptical shape, thereby increasing the overall seal width A in the radial direction, the seal width A, The relationship between the protrusions C1 and C2 in the radial direction from the pressing plate members 10a and 10b of the seal member 9 can satisfy the relationships of the above-described formulas (1) to (3).

  The form of the string is not particularly limited, but for example, a plurality of yarns obtained by twisting a plurality of the various inorganic fibers described above are braided into a string, or the inorganic fibers are directly knitted, It can be a string. As a concrete form of the string, for example, as described with reference to FIGS. 3 (a) and 3 (b), an outer knitting yarn 91 provided with a reinforcing material on the outer periphery and an inner knitting yarn provided with a reinforcing material inside. 92 is braided into a square braid by lattice knitting to form a string, or the outer knitting yarn 91 and the internal knitting yarn 92 are braided into a square braid by bag knitting so as to cover the core. It may be in the shape of

  The materials of the string-like intermediate bodies 9a to 9f and the pressing plate materials 10a and 10b are the same as those in the first embodiment. In FIG. 4, the fastening member 11 is not shown for simplification of illustration, but the pressing plate members 10 a and 10 b compress the seal member 9 in the axial direction from both sides by the fastening force of the fastening member 11. And the point which can exhibit sealing performance is the same as that of Embodiment 1.

  These intermediate bodies 9a to 9f have the same radial seal width, and the inner and outer diameters in the radial direction are sequentially different. That is, the intermediate body 9a has the largest outer diameter, and its radially outer end abuts against the inner peripheral surface of the housing 2, and the next intermediate body 9b has a radially outer end that is the radially inner end of the intermediate body 9a. The next intermediate body 9c has its radially outer end abutted against the radially inner end of the intermediate body 9b, and so on. And the radially outer end abut. The intermediate body 9f has the smallest inner diameter, and the radially inner end thereof is in contact with the outer peripheral surface of the shaft 6.

  As shown in FIGS. 5 and 6, these intermediate bodies 9 a to 9 f are cut at a predetermined angle (for example, 45 degrees) in a side view with a dedicated cutter on each end face 12 a to 12 f, Both the cut end faces 12a to 12f are abutted.

  Therefore, among these intermediate bodies 9a to 9f, the intermediate body 9a having the largest outer diameter has its cutting end surface 12a not in contact with the inner peripheral surface of the housing 2, and the intermediate body 9f having the smallest inner diameter has its cutting edge. The end surface 12f does not contact the outer peripheral surface of the shaft 6.

  Thereby, in the sealing device 8a of the second embodiment, the seal member 9 is not easily worn by contact with the outer peripheral surface of the shaft 6 or the inner peripheral surface of the housing 2, and has high heat resistance, high wear resistance, high strength, and Each performance of preventing high gas leakage can be stably maintained over a long period of time.

(Embodiment 3)
A third embodiment of the present invention will be described with reference to FIGS.

  The difference between the sealing device 8b of the third embodiment and the sealing device 8 of the first embodiment will be described. In the third embodiment, the sealing member 9 is sequentially wound around the shaft 6 as shown in FIG. It is comprised by the several sheet-like intermediate body 9a-9f by which it was folded, and these are pinched | interposed by holding | suppress board material 10a, 10b. These intermediate bodies 9a to 9f are juxtaposed between the pair of pressing plate members 10a and 10b.

  In this juxtaposed state, before the pressing plate members 10a and 10b are pressed by the fastening member 11, each of the intermediate bodies 9a to 9f is substantially rectangular in cross section and has an individual diameter in the radial direction that is greater than or equal to a predetermined value. The overall seal width in the radial direction of 9f is a certain value or more. And when both surfaces of each intermediate body 9a-9f are pressed and compressed in the axial direction by the pressing plate members 10a, 10b, the intermediate body 9a-9f is deformed to increase in the radial direction, thereby increasing the overall seal width A in the radial direction, The relationship between the seal width A and the protrusion amounts C1 and C2 in the radial direction from the pressing plate members 10a and 10b of the seal member 9 can satisfy the relationships of the above-described formulas (1) to (3).

  The individual sheet-like forms of the intermediate bodies 9a to 9f are not particularly limited. The materials of the intermediate bodies 9a to 9f and the pressing plate materials 10a and 10b are the same as those in the first embodiment. In FIG. 7, the fastening member 11 is not shown for simplification of the drawing, but the pressing plate members 10a and 10b compress the seal member 9 in the axial direction by the fastening force of the fastening member 11, The point which can exhibit sealing performance is the same as that of Embodiment 1.

  These intermediate bodies 9a to 9f have the same radial individual seal widths, but have different radial inner diameters. That is, the intermediate body 9a has the largest outer diameter, and its radially outer end abuts against the inner peripheral surface of the housing 2, and the next intermediate body 9b has a radially outer end that is the radially inner end of the intermediate body 9a. The next intermediate body 9c has its radially outer end abutted against the radially inner end of the intermediate body 9b, and so on. And the radially outer end abut. The intermediate body 9f has the smallest inner diameter, and the inner end in the radial direction is in contact with the outer peripheral surface of the shaft 6.

  As shown in FIG. 8, these intermediate bodies 9 a to 9 f are manufactured by using a plurality of sheets 13 a to 13 f having the same length and sequentially different widths, that is, five sheets in the embodiment. However, in FIG. 8, only one sheet is shown for simplicity of illustration, but these sheets 13a to 13f have the same length L1 and widths W1 to W5 that are sequentially different. The maximum width is W1 and the minimum width is W5. The maximum width sheet 13a corresponds to the intermediate body 9a, and the minimum width sheet 13f corresponds to the intermediate body 9f.

  These sheets 13a to 13f are formed by braiding inorganic fibers, for example, a sheet obtained by braiding a plurality of yarns obtained by twisting a plurality of inorganic fibers, or by directly braiding a plurality of inorganic fibers. The braiding method is not particularly limited.

  And each sheet | seat 13a-13f is rounded from the one end side (inner side) of a length direction, as shown in FIG. 9, and rounded body 14a-14f rounded to the other end side (outer side) as shown in FIG. And In this case, both end surfaces 15a to 15f of the round bodies 14a to 14f are end portions of the inorganic fibers, but the outer peripheral surfaces of the round bodies 14a to 14f are not end portions of the inorganic fibers. Therefore, the end portion of the inorganic fiber does not directly contact the outer peripheral surface (sliding surface and seal surface) of the shaft 6 and the inner peripheral surface (sliding surface and seal surface) of the housing 2.

  Next, each of the round bodies 14a to 14f is individually rounded, and the both end faces 15a to 15f are butted together to form a ring as shown in FIG. 11, whereby intermediate bodies 9a to 9f can be manufactured. As shown in FIG. 7, when these intermediate bodies 9a to 9f are sandwiched between pressing plate members 10a and 10b and compressed in the axial direction by the fastening member 11, the sealing device 8b of Embodiment 3 can be obtained.

  In the sealing device 8b according to the third embodiment, among the intermediate bodies 9a to 9f, the intermediate body 9a having the largest outer diameter has the butted surfaces 15a at both ends of the intermediate body 9a that contact the inner peripheral surface (sliding surface and sealing surface) of the housing 2. The intermediate body 9f having the smallest inner diameter is not in contact with the outer peripheral surface, and the butted surfaces 15f at both ends thereof do not contact the outer peripheral surface (sliding surface and seal surface) of the shaft 6, and the outer peripheral surface is in contact with the intermediate body 9f. Touch.

  Thereby, in the sealing device 8b of the third embodiment, the seal member 9 is not easily worn by contact with the outer peripheral surface of the shaft 6 or the inner peripheral surface of the housing 2, and has high heat resistance, high wear resistance, high strength, and Each performance of preventing high gas leakage can be stably maintained over a long period of time.

(Embodiment 4)
A fourth embodiment of the present invention will be described with reference to FIGS.

  The difference between the sealing device 8c of the fourth embodiment and the sealing device 8 of the first embodiment will be described. In the fourth embodiment, the sealing member 9 is sequentially wound around the shaft 6 as shown in FIG. It is comprised by the intermediate bodies 9a-9f folded by the several sheet shape made. Then, when both surfaces of the intermediate bodies 9a to 9f are pressed and compressed in the axial direction by the pressing plate members 10a and 10b, the intermediate bodies 9a to 9f are individually increased and deformed in the radial direction, thereby increasing the seal width A in the entire radial direction. The relationship between the seal width A and the protrusion amounts C1 and C2 in the radial direction from the pressing plate members 10a and 10b of the seal member 9 can satisfy the relationships of the above-described formulas (1) to (3).

  The materials of the intermediate bodies 9a to 9f and the pressing plate materials 10a and 10b are the same as those in the first embodiment. In FIG. 12, the fastening member 11 is not shown for simplification of the drawing, but the pressing plate members 10a and 10b compress the seal member 9 in the axial direction by the fastening force of the fastening member 11, The point which can exhibit sealing performance is the same as that of Embodiment 1.

  These intermediate bodies 9a to 9f have the same seal width in the radial direction, and the inner and outer diameters in the radial direction are sequentially different. That is, the intermediate body 9a has the largest outer diameter, and its radially outer end abuts against the inner peripheral surface of the housing 2, and the next intermediate body 9b has a radially outer end that is the radially inner end of the intermediate body 9a. The next intermediate body 9c has its radially outer end abutted against the radially inner end of the intermediate body 9b, and so on. And the radially outer end abut. The intermediate body 9f has the smallest inner diameter, and the inner end in the radial direction is in contact with the outer peripheral surface of the shaft 6.

  As shown in FIG. 13, these intermediate bodies 9 a to 9 f are manufactured by using a plurality of sheets 16 a to 16 f having the same length and sequentially different widths, and five sheets in the embodiment. However, in FIG. 13, only one sheet is shown for simplicity of illustration, but these sheets 16a to 16f have the same length L2 and sequentially differ in widths W1 to W5. The maximum width is W1 and the minimum width is W5. The maximum width sheet 16a corresponds to the intermediate body 9a, and the minimum width sheet 16f corresponds to the intermediate body 9f.

  And as shown in FIGS. 14-15, each sheet | seat 16a-16f is folded in the direction of the length L2 from one end side to the other end side, and the folding bodies 17a-17f are obtained. In this case, since the edge part of sheet | seat 16a-16f becomes an edge part of inorganic fiber, both end surface 18a-18f of folding body 17a-17f becomes an edge part of inorganic fiber, but the edge of folding body 17a-17f The surface other than the portion does not become the end portion of the inorganic fiber.

  And as shown in FIG. 16, sheet | seat-shaped intermediate bodies 9a-9f can be manufactured if the folding bodies 17a-17f are rounded circularly and the both end surfaces 18a-18a are faced | matched. When these intermediate bodies 9a to 9f are sandwiched between a pair of upper and lower pressing plate members 10a and 10b and compressed in the axial direction by the fastening member 11, the sealing device 8c of the fourth embodiment can be obtained. Since the end portions of the inorganic fibers do not appear on the outer peripheral surfaces of the intermediate bodies 9a to 9f, the end portions of the inorganic fibers are the outer peripheral surface (sliding surface and seal surface) of the shaft 6 and the inner peripheral surface (sliding surface) of the housing 2. There is no direct contact with the moving surface and the sealing surface.

  In the sealing device 8c of the fourth embodiment, among the intermediate bodies 9a to 9f, the intermediate body 9a having the largest outer diameter has a minimum inner diameter without the butting surfaces 18a at both ends thereof coming into contact with the inner peripheral surface of the housing 2. In the intermediate body 9f, the butted surfaces 18f at both ends thereof do not contact the outer peripheral surface of the shaft 6.

  Thus, in the sealing device 8c of the fourth embodiment, the seal member 9 is not easily worn by contact with the outer peripheral surface of the shaft 6 or the inner peripheral surface of the housing 2, and has high heat resistance, high wear resistance, and high strength. And each performance of high gas leakage prevention can be stably maintained over a long period of time.

(Other embodiments)
FIG. 17 is a cross-sectional view of a sealing device 8d according to another embodiment.

  In this embodiment, the fastening member 11 is composed of bolts 11a and nuts 11b and 11c, and by these, the seal member 9 is pressed and compressed in the axial direction by the pressing plate members 10a and 10b from both sides thereof. The relationship between the seal width A of the seal member 9 and the protrusion amounts C1 and C2 in the radial direction from the pressing plate members 10a and 10b of the seal member 9 can satisfy the relationships of the above-described formulas (1) to (3). .

  FIG. 18 is a cross-sectional view of a sealing device 8f according to still another embodiment. In this embodiment, the fastening member 11 is a rivet, whereby the sealing member 9 is pressed and compressed by the fastening member 11 from both sides by the pressing plate members 10a and 10b. The relationship between the seal width A of the seal member 9 and the projecting amounts C1 and C2 of the seal member 9 from the pressing plate members 10a and 10b in the radial direction can satisfy the relationships of the above-described formulas (1) to (3).

  FIG. 19 is a cross-sectional view of a sealing device 8f according to still another embodiment. In this embodiment, it is an annular pressing plate member 10c having a cross-sectional piece “K” shape, and the pressing plate member 10c has annular grooves 10d and 10e on both sides, and the annular grooves 10d and 10e In addition, annular seal members 9a and 9b are arranged and are caulked in the annular grooves 10d and 10e by pressing in the arrow direction from the upper and lower surfaces against the pressing plate material 10c. By this caulking, both the seal members 9a and 9b are mounted in a state of being pressed and compressed in the axial direction on the pressing plate member 10c with the same action as the fastening member 11 of the embodiment. Even in this mounted state, the relationship between the seal width A of the seal member 9 and the protruding amounts C1 and C2 in the radial direction from the pressing plate members 10a and 10b of the seal member 9 satisfies the relationship of the above-described formulas (1) to (3). be able to.

  As described above, according to the present embodiment, the seal member 9 is made of braided inorganic fibers, and thus has high heat resistance, high wear resistance, and high strength, and the seal member 9 is a pair of Since the pressing plate material is pressed and compressed from both sides in the axial direction, the inorganic fibers are densely compressed, thereby having high-density sealing performance. In addition, the amount of protrusion of the inner end in the radial direction and the outer end in the radial direction of the seal member 9 can be appropriately controlled by adjusting the pressure compression by the pressing plate members 10a, 10b, and 10c. The outer peripheral surface of the housing and the inner peripheral surface of the housing 2 (extension housing 2b) are brought into contact with these surfaces with an appropriate surface pressure without damaging them, so that a sufficient sealing effect can be obtained. The target gap can be sealed to effectively prevent leakage of high temperature gas.

  The present invention is not limited to the above-described embodiments, and can be implemented in various other forms without departing from the spirit or main features thereof. Therefore, the above-described embodiment is merely an example in all respects, and the scope of the present invention is shown in the claims, and is not restricted by the text of the specification. Further, all modifications and changes belonging to the scope of the claims are within the scope of the present invention.

DESCRIPTION OF SYMBOLS 1 High temperature gas valve 2 Housing 2a Main body housing 2b Extension housing 3 Partition 4 Passage side 5 Shaft drive mechanism side 6 Shaft 8 Sealing device 9 Seal member 10a, 10b Holding plate material 11 Fastening member A Seal width of sealing member 9 B Holding plate material 10a, 10b Pressing width C1, C2 Projection amount

Claims (6)

A sealing device that is incorporated in a gap between a housing and a shaft that rotates or reciprocates in the housing and seals the gap in the axial direction;
An annular seal member braided with inorganic fibers and wider in the radial direction than in the axial direction ;
A pair of pressing plate members that are sandwiched from both sides of the seal member and maintain the sandwiched state, and are wider in the radial direction than the axial direction ;
With
A radially inner end of the seal member protrudes radially inward from a radially inner end of the pressing plate member,
A radially outer end of the seal member protrudes radially outward from a radially outer end of the pressing plate member,
When the sealing member is compressed in the axial direction by the clamping force of the pressing plate member, the radial inner end of the sealing member further protrudes radially inward, and the radial outer end of the sealing member has a radius It is possible to protrude further outward in the direction ,
The seal member is formed of a plurality of intermediate bodies that are braided with the inorganic fibers and have different radii.
The intermediate bodies are juxtaposed in the radial direction and sandwiched between the pressing plate materials,
A sealing device characterized by that. A sealing device that is incorporated in a gap between a housing and a shaft that rotates or reciprocates in the housing and seals the gap in the axial direction;
An annular seal member braided with inorganic fibers and wider in the radial direction than in the axial direction;
A pair of pressing plate members that are sandwiched from both sides of the seal member and maintain the sandwiched state, and are wider in the radial direction than the axial direction;
With
A radially inner end of the seal member protrudes radially inward from a radially inner end of the pressing plate member,
A radially outer end of the seal member protrudes radially outward from a radially outer end of the pressing plate member,
When the sealing member is compressed in the axial direction by the force sandwiched by the pressing plate member, the radially inner end of the sealing member further protrudes radially inward, and the radially outer end of the sealing member has a radius It is possible to protrude further outward in the direction,
Each of the sealing members is composed of a plurality of intermediate bodies in which the sheet body braided with the inorganic fibers is rounded and the radii are sequentially different,
The intermediate bodies are juxtaposed in the radial direction and sandwiched between the pressing plate materials,
A sealing device characterized by that. A sealing device that is incorporated in a gap between a housing and a shaft that rotates or reciprocates in the housing and seals the gap in the axial direction;
An annular seal member braided with inorganic fibers and wider in the radial direction than in the axial direction;
A pair of pressing plate members that are sandwiched from both sides of the seal member and maintain the sandwiched state, and are wider in the radial direction than the axial direction;
With
A radially inner end of the seal member protrudes radially inward from a radially inner end of the pressing plate member,
A radially outer end of the seal member protrudes radially outward from a radially outer end of the pressing plate member,
When the sealing member is compressed in the axial direction by the clamping force of the pressing plate member, the radial inner end of the sealing member further protrudes radially inward, and the radial outer end of the sealing member has a radius It is possible to protrude further outward in the direction,
Each of the sealing members is composed of a plurality of intermediate bodies in which the sheet body braided with the inorganic fibers is folded and the radii are sequentially different,
The intermediate bodies are juxtaposed in the radial direction and sandwiched between the pressing plate materials,
A sealing device characterized by that. The relationship between the amount C1 of the radially inner end of the seal member protruding inward in the radial direction from the pressure plate and the seal width A in the radial direction of the seal member is 0.1 ≦ C1 / A ≦ 0.4. Satisfies the inequality,
The sealing device according to any one of claims 1 to 3 . The relationship between the amount C2 of the radially outer end of the seal member projecting radially outward from the pressing plate member and the seal width A in the radial direction of the seal member is 0.1 ≦ C2 / A ≦ 0.4. Satisfies the inequality,
The sealing device according to any one of claims 1 to 3 . When C1 = C2 = C, the relationship between the seal width A in the radial direction of the seal member and the protrusion amount C satisfies an inequality of 0.1 ≦ C / A ≦ 0.4.
The sealing device according to claim 4 or 5 .

Images