JP2599548B2 - Pressure equipment for integrated in-wall elastomer seals. - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001] This application is a continuation-in-part (CIP) of Patent Application No. 07/757536, filed in the United States on September 12, 1991.
Application).

[0002]

2. Description of the Related Art A standard for positively and hydrostatically sealing the gap between a tube or other conduit and a passage or casing which typically extends across and through a wall. The integrated seal assembly that became the device was 19
Barton US Patent No. 35, issued September 15, 1970
No. 28668. Some variations of this integral seal structure are described in US Pat. No. 3,649,034 to Barton, issued Mar. 14, 1972, and US Pat.
No. 703297. Each of these annular seals consists of a number of elastomer seal blocks with two sets of pressure plates applied to both sides. Bolts connecting the pressure plates on both sides to each other can connect these blocks in a ring.

[0003] This annulus is formed around a conduit passing through the wall. Once the annular structure is in place, the bolts are tightened and the pressure plates on both sides are pulled toward each other. At this time, the elastomeric seal block is compressed in a direction parallel to the conduit and expanded radially outward into the gap between the conduit and the in-wall or other passage.
In this way, a highly flexible and economical seal structure is formed using a single set of components that can be used for many different sizes of conduits. Years of rigorous practical testing have demonstrated that this integral annular conduit-wall opening seal is far superior to most other seal configurations.

[0004]

Despite these proven versatility and utility, the integral annular seals of the above-mentioned Barton and Gignac patents, particularly US Pat. No. 3,528,668, have several technical difficulties. It turns out that there is. That is, especially when the size is large, the weight of the entire assembly becomes considerably large, and it becomes difficult for a worker to install the seal. The cause is, among other things,
Relatively large and heavy metal parts are used in pressure equipment for joining and expanding and / or contracting multiple elastomer seal blocks. The pressure equipment used, especially metal parts, are non-standard parts and their cost tends to be higher than desired. further,
Depending on the environmental conditions, the exposed metal often undergoes undesirable corrosion, especially galvanic corrosion.

[0005] In some cases, the strength of the seal may be lower than a desired level. Metal parts, especially nuts, are easily lost, which further increases costs. Perhaps the most important issue with this type of seal is the consistency with the required expansion and / or contraction during field installation. It is not previously impossible to determine the tightness of the pressure equipment required to achieve the desired secure sealing effect without unduly stressing the pressure equipment or any other parts of the seal block assembly. Even so, it was extremely difficult.

Accordingly, it is a primary object of the present invention to effectively and economically reduce or eliminate the technical difficulties of the previously known seal assemblies as described above. That is, to provide a new and improved pressure equipment for use with multiple elastomer seal blocks in a seal block assembly for forming an integral annular conduit-wall opening seal.

More particularly, an object of the present invention is to provide a new and improved pressure equipment for use in a seal block assembly for forming an integral annular conduit-wall opening seal from a number of elastomeric seal blocks. Identifies certain torque loads that should be applied to the pressure equipment to ensure a seal that is structurally simple and economical, does not easily lose parts, and effectively damages the pressure equipment without damaging it To provide pressure equipment that can

[0008]

SUMMARY OF THE INVENTION Accordingly, the present invention provides
A plurality of elastomeric seal blocks interconnected in a ring around the conduit, each seal block having at least one pressure bolt hole extending through the block parallel to the conduit; The seal blocks are axially compressed and radially expanded to form an integral annular conduit wall opening gap seal of the type wherein a seal is formed between the conduit and the wall surrounding it. For a seal block assembly. The assembly includes a plurality of sets of pressure equipment for compressing and expanding the plurality of seal blocks, and each set of pressure equipment includes a multi-faceted piece of predetermined size and shape integral with one end of the bolt shaft. Including a bolt having a bolt head. The bolt shaft has a threaded portion extending longitudinally from the other end toward the bolt head.

In addition, the method includes a first molded resin pressure plate having one recess, the recess being larger than the bolt head,
The bolt head is seated so that it can rotate freely within the recess with the wrench accessible to the periphery of the bolt head and no metal-to-metal sliding contact occurs when the bolt is tightened. The recess has a sufficient depth that the bolt head does not substantially protrude from the recess. The first pressure plate further has a first bolt hole therethrough centered with the recess, the first bolt hole being large enough to allow the bolt shaft to pass therethrough. , So small that the bolt head cannot enter. Each pressure piece includes a multi-faced nut of predetermined size and shape having an internal opening threaded to engage the threaded portion of the bolt shaft, and a second molded resin pressure plate. Each second
With dimensions and shapes corresponding to the molded resin pressure plate nut
The nut has an inner polyhedral socket portion seated in a non-rotating relationship within the socket portion and an outer socket portion having a transverse dimension greater than a maximum transverse dimension of the inner socket portion, and a shelf at an outer edge of the inner socket portion. Exists. A flange integrally formed with the nut is seated on the shelf.

The second pressure plate further has a second bolt hole therethrough, the bolt hole being smaller than the nut and being aligned with the socket, and The other end can engage the nut. Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS FIGS. 1 to 3 show a product name "LINK-SEAL" in the United States.
Shows a seal block assembly 20 for a prior art integral annular conduit-wall opening gap seal using a structure already available for many years, available from Thunder-line Corporation of Belleville, Michigan. . This seal block assembly 20 comprises a number of elastomeric seal blocks 21, which are designated by reference numerals 21A-21D in FIGS. These seal blocks are interconnected to form a ring around a conduit 24 (FIG. 3). FIGS. 1 and 2 each show only a part of the assembly 20. Each block has two holes for receiving one pressure bolt. One such hole 22 is seen in FIG. Pressure bolts 23A, 23B, 23C are also seen in FIGS. A number of such pressure bolts extend through the holes to connect the blocks together to form an assembly, i.e., form a seal.

Each pressure bolt has a conventionally shaped bolt head 25, such as the bolt heads 25A through 25C shown in FIG. The other end of the bolt shank, the bolt end opposite the bolt head, includes a relatively long threaded portion. FIG. 1 shows the ends 27A to 27C of such bolts, and FIG.
7B and 27C appear. The head 25 of each bolt 23 engages a metal and plastic composite pressure plate.
That is, looking at FIG. 1, the bolt heads 25A, 25B,
25C is a plastic pressure plate 29A, 29B, respectively.
Metal pressure plates 31A, 31 placed in recesses in 29C
B, 31C. The orientation of these components is also seen on the left side of the assembly 20 in FIG.

In each case, the bolt head projects completely outside the composite pressure plate. At the end of each bolt is a plastic pressure plate 33, which is a large nut 35
Has a recess or receptacle located therein.
Pressure plates 33A-33C and nuts 35A-35 of FIG.
See C. This part of the assembly is best seen in FIG.
That is, as shown in FIG.
C are each rectangular and are fitted in the receptacles or recesses of the corresponding plastic pressure plates 33B and 33C. In practice, the plastic pressure plate on the opposite side of the assembly may be of the same shape.

To complete the seal of the gap between conduit 24 and sleeve 26 through concrete wall 28 (see FIG. 3), elastomer seal block 21 first includes bolts 23, pressure plates 29, 31, 33 and nuts. 35 together form a band. The length of this band is determined by the number of sealing blocks used, while the number used is determined by conduit 24 (FIG. 3).
Is determined by the length of the circumference. A band of sealing blocks is placed around the conduit and the ends of the band are joined by a last set of pressure equipment to form an annulus surrounding the conduit. The seal assembly is then pushed longitudinally along the conduit into position on the wall sleeve 26 (FIG. 3).

At this point, the pressure bolts are tightened and the pressure plate compresses the elastomer block 21 in a direction parallel to the conduit 24. This causes the elastomer block to bulge in the radial direction of the conduit, so that the tube in the wall, e.g.
A continuous air-tight and liquid-tight seal is formed in the gap between the sleeve and the sleeve 26. 4 through 10 show a seal block assembly 50 incorporating one embodiment of the improved pressure equipment of the present invention.
It shows. The seal block assembly 50 shown in FIGS. 4-6 may include the same elastomer block members as used in the prior art seal assemblies described above.

That is, as shown, the elastomer blocks 21A through 21D are illustrated as being joined together by bolts 23 extending through bolt holes 22 (FIGS. 5 and 6) in the blocks. The bolt heads 25A to 25D are not different from those of the prior art. In fact, the bolt 23 is compatible between the conventional assembly and the new assembly. However, other parts of the pressure equipment are shown in FIG.
To 10 to provide improvements to the present invention. Each set of pressure equipment used in the assembly 50 includes the previously known bolts and first molded resin pressure equipment 59 described above. Three of these resin pressure plates, 59A, 59B and 59C are shown in FIG.
And one pressure plate 59B is also shown in FIG. The construction of these pressure plates is shown in more detail in FIGS.

That is, each pressure plate 59 has a recess 61 in the center.
have. The recess 61 is larger than the bolt head 25 seated therein (see FIGS. 4, 6, 7), so that the bolt head is free to rotate within the recess. A lateral recess 63 is provided on the outside of each resin pressure plate 59 opposite to each other, primarily for the purpose of reducing the cost of the pressure plate. 6 and 7, the recess 61 is sized to access the outer edge of the bolt head 25 so that a wrench can be applied to the bolt head 25 seated in the recess.

At the bottom of the recess 61 is a metal washer 65. It is located between the bolt head 25 and the base of the recess. The depth of the recess 61 is set such that the bolt head 25 does not substantially protrude from the recess, but the outer surface of the bolt head is slightly above the plastic pressure plate 59 (see FIG. 7). The height at which the bolt head 25 exceeds the pressure plate 59 is preferably no greater than 0.125 inches (0.3 cm). The plastic pressure plate 59 has a bolt insertion hole 67 penetrating the bottom thereof and aligned with the recess 61. This hole 67 passes the shaft of the bolt 23,
The size is such that neither the washer 65 nor the bolt head 25 can enter.

There is a second molded resin pressure plate 69 for each bolt 23 of the assembly 50. This pressure plate 69
Is best shown in FIGS. 4, 5, 9 and 10. That is, each second pressure plate 69 is a multi-sided socket 71
And an adjacent concave portion 7 opening outward from the socket portion 71.
And 2. The dimensions and shape of the socket part 71 are the same as those of the polyhedral nut 73 included in each set of the improved pressure equipment.
Corresponding to the size and shape of Each nut 73 can be a normal hexagonal nut, but in the case of a large seal, a nut having a flange 75 that sits on the upper rim portion of each socket is preferable. According to this structure, a larger area for absorbing the force applied to the second pressure plate 69 by the nut 73 is obtained. The adjacent recess 72 is cylindrical and has a diameter such that the nut 73 can be inserted into the socket 73 with its flange 75 positioned in the recess 72.

Of course, in the structure shown, each nut 73
Is locked in the socket 71 so that the nut does not rotate in the socket. Each second pressure plate 69 has a central through hole 77 through which a bolt is screwed into a nut 73 (FIG. 9). Also, the second pressure plate 69 preferably has a recess 79 to reduce weight and cost. 11 and 12
Shows another embodiment of the second molded resin pressure plate. The second pressure plate 89 of this embodiment has an improved retention capability to prevent rotation of a nut inserted into the pressure plate socket. Further, according to the structure of this embodiment. The pressure plate 89 can securely secure the nut 93 at a position in the socket portion of the pressure plate. 11 and 12
As shown in FIG. 7, the pressure plate 89 has a multi-sided socket portion 91 in which the nut 73 is used in the above-described embodiment.
Are inserted into the socket portion 71 in the same manner (FIG. 9).

Most of the molded resin pressure plate 89 including the socket portion 91 is the same as the pressure plate 69 shown in FIG. However, the socket portion 91 of the present embodiment
Has a six-sided opening for receiving the corresponding hexagonal nut 93, but three of the six sides 97 have an axial direction partially projecting into the socket portion 91. Crush rib 101 protruding inwardly extending
Is provided. These ribs are formed integrally with the pressure plate 89, and every other surface 97 of the socket portion 91 is formed.
Are provided with one crash rib 101, respectively.
This crush rib is preferably V-shaped. However, other shapes can be used. The number of the crush ribs is preferably three, but this number is not critical. These ribs 101 are provided with nuts 93 in socket portions 91.
When it is fitted and screwed down in the socket portion 91, it engages with the nut and is crushed or deformed by the nut.

As shown in FIG. 12, the ribs 101 are preferably tapered outwardly such that the protrusion of the ribs into the socket portion 91 increases with the depth of the socket portion. Therefore, when the hexagon nut 93 is screwed into the socket portion 91 by the operation of tightening the bolt 23, the tapered edge of the crush rib 101 engages with the surface of the nut 93. As the nut 93 is pushed downward in the socket portion 91, the amount of the lateral space occupied by the rib 101 increases, so that the nut 93 crushes the lower portion of the rib 101. The crushed rib tightly engages the nut 93. As a result, even if the bolt 23 is completely removed from the nut, the nut 93 is securely secured in the socket portion 91 by friction with the rib. Keeping the seal nut 93 in the molded resin pressure plate 89 is advantageous when the seal block assembly is not already in place. This is because the number of loose parts to be stored in preparation for final assembly and installation of the seal is reduced. The chance of losing the seal nut is also significantly reduced.

As another manufacturing method, the nut 93 can be welded to the plastic material of the molded resin pressure plate 89 using a known ultrasonic welding technique. This manufacturing method requires an additional manufacturing step, but has the following advantages. That is, the nut 93 is always held in the pressure plate 89 without the crush rib 101. In addition, careful welding of the nut 93 provides better alignment for engagement of the nut with the bolt end 27.

FIGS. 13, 14 and 15 show a molded resin pressure plate 109 as another preferred embodiment of the second pressure plate used in the present invention. Pressure plate 10 of this embodiment
9 has a screw hole 111 that penetrates the central part of the pressure plate. This screw hole 111 replaces the through hole 77 of the pressure plate 69 (FIG. 9) of the embodiment. One end of the screw hole 111 in the plate surface facing the seal block is a bolt 2
Bevel rim chamfered to help insert 3
(beveled rim) 113.

Since the internal thread of the through screw hole 111 performs the same function as the hexagon nut 73 (FIG. 9), there is no need to use a nut. It has been found that the use of the molded resin pressure plate 109 of this embodiment having the screw holes 111 ensures good screw engagement with the bolts 23 and provides several advantages. A first advantage is that one removable part (nut) is not required. Second, the use of this completely non-metallic part reduces the potential for corrosion of the entire seal block assembly. Further, the use of the pressure plate 109 eliminates the need to use a hexagon nut for each pressure plate, thereby reducing costs. This also saves costs because the assembly of the seal is performed more quickly and easily.

The composition of the elastomer used for the elastomer seal block 21 may be the same as that conventionally used for various applications. Frequently used are specific gravity 1.09, tensile strength 1500 psi, elongation 57
EPDM (ethylene-propylene diene monomer) having a durometer A hardness of 50% and 0%. Other elastomers such as silicone elastomers can be used depending on the application and the needs of the user. Pressure plates 59, 6
9, 89 and 109 are preferably molded from fibrous thermoplastic polyamide. 30% of glass fiber 6
-6 nylon is preferred.

The pressure device according to the invention is lighter and less expensive than the prior art pressure devices for similar seals. The light weight makes it easy to attach large seals to conduits, for example, 18 inches (46 cm) in diameter or larger. The exposed metal is greatly reduced and the accessible metal parts are negligible. Thus, corrosion problems are reduced to a minimum. Moreover, despite the small number of metal parts, this seal structure is more robust than conventional ones.

FIGS. 16 to 19 show still another embodiment of the present invention. A feature of this embodiment is that the corrosion at the head 25 of the bolt 23 and the threaded portion 27 of the bolt receiving the nut 73 is further reduced. That is, as shown in FIGS. 16 and 17, in this embodiment, a bolt screw cap (corrosion prevention cap) 123 is provided. The cap has an inner chamber or socket 125 which houses the threaded end 27 of the bolt 23 used in each of the above embodiments. When the seal block assembly is installed and the bolts are tightened, the threaded end 27 of each bolt extends significantly beyond the washer 75, often more than one inch, as shown in FIG. Projecting upwards. The bolt 23 shown in FIG.
The distal thread 27 or threaded rod tip of the nut only slightly protrudes beyond the flange 75 of the nut 73 because the bolt has not yet been tightened. When the bolt 23 is screwed into the nut from this state,
The terminal thread 27 of the bolt projects significantly above the pressure plate 69 as shown in FIG. The inner surface of the socket 125 corresponds to the shape of the screw 27 at the end of the bolt. However,
Fitting is not necessary or particularly desirable. It should be noted that the second pressure plate and nut are often inaccessible once the seal block assembly has been installed between the conduit and the wall opening.

The corrosion protection cap 123 includes a base flange 129 extending at its base outside the cap.
In addition to the flange 129, the cap 123 includes a portion thereof that comprises one or more arcuate ribs 131. This rib portion may be a single annular rib. The outer diameter of rib 131 is slightly larger than the inner diameter of recess 72 in which flange 75 of nut 73 is seated. Therefore, when the cap 123 is inserted into the concave portion 76,
The rib 131 is force-fitted into the recess to form an interference fit between the two. In this state, the flange 129 is in the recess 7
2 and engages with the outer surface of the pressure plate 69. The engagement of the flange 129 with the pressure plate 69 does not necessarily provide a complete hydraulic seal, but in any case, the cover provided by the cap 123 for the bolt end 27 and the nut 73 is of a type consistent with the present invention. To prevent corrosion attacking the seal block assembly. A similar cap can be used with the pressure plate shown in FIG. 13, provided there is a suitable recess into which the cap fits.

FIGS. 18 and 19 show a cover or cap of the same type as above, namely the bolt head cap 1.
35 is shown. The inner surface 137 of this cap 135
Is shaped to effectively cover the bolt head 25. For example, as shown in FIG.
7 may be circular or hexagonal if the size of the nut 25 is standardized. The outer surface 139 of the bolt head cap 135 includes a cylindrical wall 141 and an outer flange 143. The cylindrical wall 141 matches the depth of the socket portion 61 or is slightly shorter. The cylindrical wall 141 is formed with one or more protruding ribs 145 which, together with the flange 143, serve to fit the cap into the socket part 61 for the bolt head 25. The annular flange 143 projects beyond the cylindrical wall portion 141 at a predetermined height.

The bolt head cap 135 is inserted into the socket part 61 over the bolt head 25 after the seal assembly is installed and the bolt 23 is tightened.
With this insertion, the flange 143 is securely engaged with the inner wall of the socket portion 61. Thus, the cylindrical wall 144 of the cap 135 and its rib 145 are interference-fitted with the inner wall of the socket portion 61 to effectively prevent corrosion of the bolt head in the use environment. The outer surface of the cap 135 is exposed to the external environment and prevents moisture and / or corrosive substances from penetrating into the socket 61. A preferred material for both the bolt screw cap 123 and the bolt head cap 135 is nitrile rubber having a Shore A hardness of about 75.

In yet another preferred embodiment of the second pressure plate, the embodiments and features of FIGS. 14-15 and the embodiments of FIGS. 16-17 are combined in a single structure. FIG. 20 is a cross-sectional view showing the second pressure plate 169. In the case of the pressure plate 169, the screw hole 171 penetrates the lower surface in contact with the elastomer seal block 21 (FIG. 1), but does not penetrate the upper surface of the pressure plate. That is, on the upper side of the pressure plate 169, the screw hole is formed as an integrally formed cap 173 extending from the upper surface of the pressure plate.
Covered in. Preferably, the cap 173 is integrally connected to the pressure plate 169 over the entire periphery where it connects to the pressure plate, thus preventing moisture from penetrating the screw holes.

The integral cap 173 is a screw 175 formed on the inner surface of the hole 171 as an extension of the screw of the screw hole 171.
including. The depth of the hole 171 is determined when the bolt 23 is tightened during use of the seal block assembly.
Deep enough to completely accommodate the in this way,
The embodiment shown in FIG. 20 has the advantage of eliminating the steel hex nut as well as the advantage of including the cap shown in FIG. As an additional advantage, when this embodiment is used,
Since one individual part is used, there is no need to worry that the cap, which is another part, will fall off the nut 23.
Further, by integrally molding the pressure plate 169 and the cap 173, there is obtained an advantage that there is no moisture intrusion passage.

In the configuration of the present invention, no metal-to-metal sliding contact occurs when tightening the pressure equipment. This is not a conventional configuration. That is, in the conventional structure shown in FIGS. 1 to 3, high friction sliding contact occurs between the bolt head 25 and the metal pressure plate 31 adjacent thereto. In the pressure equipment of the present invention, the bolt head 2
5 and washer 65 rotate together when the bolt is tightened. Sliding engagement only occurs at very low friction levels between the washer 65 and the recess 61 (see FIG. 7). The present invention has the following effects. First, the contractor can tighten the pressure bolt more easily than before. Second, the seal supplier can specify the torque required to tighten the pressure bolts for perfect seal reliability.

A seal using one or more of the present invention can be completed by sequentially tightening its multiple pressure bolts according to a particular program of the escalation phase. In one exemplary program, all bolts included in one seal assembly are 0.68 kgw-m (5 feet-p) using a suitable torque wrench.
sound], 1.36 [kgw · m] (10 [ree
t · poun] d), 2.04 [kgw · m] (15f
eet · ound), 2.72 [kgw · m] (20
[Feet / ound]) is sequentially tightened. It has heretofore been impossible to specify a final torque (for example, 20 feet pound) for satisfactory seal formation. This is due at least in part to the metal-to-metal interface used in conventional pressure equipment. Further, the following effects can be obtained from the pressure equipment of the present invention. The corrosion of the steel bolts forming and fixing the seals can be suppressed or even eliminated. Lock nut loss is efficiently avoided. Overall component costs are saved without sacrificing structural integrity.

[Brief description of the drawings]

FIG. 1 is a plan view of a portion of a one-piece seal block assembly according to the prior art.

FIG. 2 is an elevational view of the prior art seal block assembly taken generally along line 2-2 of FIG. 1, with one pressure plate omitted.

FIG. 3 is a cutaway perspective view illustrating the use of the prior art seal block assembly shown in FIGS. 1 and 2;

FIG. 4 is a plan view showing a part of an integrated seal block assembly including the pressure equipment of the present invention, similarly to FIG. 1;

5 is an elevational view of the seal block assembly taken generally along line 5-5 of FIG. 4, with one pressure plate omitted.

FIG. 6 is a fragmentary elevation view from the opposite direction to FIG. 5;

FIG. 7 is a detailed cross-sectional view taken generally along line 7-7 of FIG. 6;

FIG. 8 is a detailed view taken substantially along the line 8-8 in FIG. 7;

FIG. 9 is a detailed cross-sectional view taken substantially along the line 9-9 of FIG. 5;

FIG. 10 is a detailed view taken substantially along the line 10-10 in FIG. 9;

FIG. 11 is a plan view of another embodiment of the first pressure plate.

FIG. 12 is a partially detailed elevation view of a section taken generally along the line 12-12 in FIG. 11;

FIG. 13 is a partially sectioned detailed sectional view of another embodiment of the second pressure plate.

FIG. 14 is a plan view of a second pressure plate shown in FIG.

FIG. 15 is an end view of the pressure plate shown in FIGS. 13 and 14;

FIG. 16 is a partially broken elevational view showing a cap of a bolt end screw portion in a second pressure plate.

FIG. 17 is a plan view of a cap of a bolt screw portion shown in FIG. 16;

FIG. 18 is a partially cutaway elevation view showing a cap of a bolt head in the first pressure plate.

FIG. 19 is a plan view of the cap of the bolt head shown in FIG. 18;

FIG. 20 is a sectional view of a second pressure plate.

[Explanation of symbols]

 Reference Signs List 20 seal block assembly 21 elastomer seal block 22 bolt hole 23 pressure bolt 25 bolt head 27 bolt end 29 plastic pressure plate 31 metal pressure plate 33 plastic pressure plate 35 nut 24 conduit 26 sleeve 28 concrete wall 50 seal block assembly 59 1 Molded resin pressure plate 65 Metal washer 61 Depressed portion 69 Second molded resin pressure plate 71 Multi-faced socket part 73 Multi-faced (hexagon) nut 75 Flange 89 Second molded resin pressure plate 91 Multi-faced socket part 93 Multi-faced (hexagon) nut 101 Crush rib 109 Second molded resin pressure plate 111 Screw hole 113 Bevel rim 123 Bolt screw cap (Corrosion prevention cap) 135 Bolt head cap 141 Cylindrical wall part of cap 143 Flange part of cap 169 Second Cap integrally molded with the force plate 173 pressure plate

Claims (17)

(57) [Claims] 1. A replaceable unit having a plurality of elastomeric seal blocks annularly interconnected around a conduit for forming a seal against an opening between the annular conduit and a wall. A pressure device in a seal block assembly, wherein each seal block has at least one pressure bolt hole parallel to the central axis of the conduit and passing through the seal block, and wherein the seal block has a shaft. For compressing and expanding said plurality of sealing blocks, which are pressure equipment compressed in the direction and radially expanded to form a seal between the conduit and the wall surrounding it from outside. Each set of pressure equipment, including a plurality of sets of pressure equipment, has a multi-faced bolt head of a predetermined size and shape integral with one end of the bolt shaft, and the bolt shaft is separated from the other end. A bolt having a threaded portion extending longitudinally toward the bolt head, wherein the bolt head is accessible by a wrench around the bolt head and is metal when the bolt is tightened; A first molded resin pressure plate having a recess larger than the bolt head so that the bolt head can freely rotate within the recess without having a contact portion for sliding the metal and the metal; Wherein the recess has a sufficient depth such that the bolt head does not substantially protrude from the recess, and has a stepped socket for covering outwardly of the pressure plate. A second molded resin pressure plate, wherein the socket has an inner polyhedral socket portion having a predetermined depth and a predetermined maximum transverse dimension, and an outer socket portion having a transverse dimension greater than the maximum transverse dimension of the inner socket portion. Have A ledge at the outer edge of the inner socket portion has a socket portion that provides an annular bottom surface for the outer socket portion, the inner portion being configured so that the nut cannot rotate within the inner socket portion. A nut having a plurality of sides of a predetermined size and shape fully seated in the socket portion, wherein the nut has an internal opening threaded to engage the threaded portion of the bolt shaft; And an integral flange on the outside of the nut such that the nut engages a bottom surface of the outer socket portion to distribute stress from the bolt and the nut to the second pressure plate. Further, the second pressure plate has a second bolt receiving hole smaller in size than the nut and is aligned with the socket portion, and the other end of the bolt shaft portion is connected to the nut. Can be engaged Pressure equipment for elastomer seal block assembly having a second bolt receiving holes through the ability of the second pressure plate further. 2. A seal for an opening between an annular conduit and a wall of a replaceable unit having a plurality of elastomeric seal blocks annularly interconnected around the conduit. A pressure device in a seal block assembly, wherein each seal block has at least one pressure bolt hole parallel to the central axis of the conduit and passing through the seal block, and wherein the seal block has a shaft. Sets for compressing and expanding the sealing block, which is a pressure piece of material that is compressed in the direction and radially expanded to form a seal between the conduit and the wall surrounding it from the outside Each set of pressure equipment includes a bolt head having a plurality of sides of predetermined dimensions and shape integral with one end of the bolt shaft, and wherein the bolt shaft includes A bolt having an externally threaded portion extending longitudinally from an end to a bolt head end, wherein the bolt head has a wrench accessible around the bolt head and the bolt is tightened; A first mold having a recess larger than the bolt head so that the bolt head is free to rotate within the recess without having a sliding contact between the metal and the metal when A resin pressure plate, wherein the recess has a sufficient depth so that the bolt head does not substantially protrude from the recess, and the first pressure plate further comprises: A penetrating first bolt receiving hole is aligned with the recess, and the first bolt receiving hole has a size large enough to allow the bolt shaft to pass through the hole. The bolt head must be inserted into the first bolt receiving hole. The second bolt receiving hole has an internal threaded portion through which the other end of the threaded portion of the bolt shaft engages in the bolt tightening direction. A pressure material for an elastomer seal block assembly comprising: a second molded resin pressure plate having a bolt receiving hole. 3. The elastomer seal block set of claim 1 or 2, wherein each set further comprises a washer rotatably disposed within the recess between the bolt head and the bottom of the recess. Pressure equipment for 3D. 4. The pressure equipment for an elastomer seal block assembly according to claim 1, wherein the bolts included in each set of pressure equipment are steel bolts having a hexagonal head. . 5. The pressure equipment for an elastomer seal block assembly according to claim 1, wherein said nut in each set is a hexagonal seal nut having an integral annular flange on one side thereof. 6. The pressure plate is made of 6-6 nylon containing 30% glass fiber.
Pressure equipment for an elastomer seal block assembly according to any of the preceding claims. 7. The first pressure plate further has a bolt receiving hole passing therethrough aligned with the recess, and the bolt receiving hole is large enough for the bolt shaft to pass through the hole. The pressure equipment for an elastomer seal block assembly according to claim 1, wherein the pressure equipment is sized so that the bolt head does not fit into the hole. 8. The elastomeric seal block assembly according to claim 1, wherein each pressure plate has a plurality of recesses on a side of an outer surface of the pressure plate to reduce the weight of the pressure plate. Equipment for pressure. 9. A monolithic, axially extending rib projecting into the socket so that at least one surface of the polyhedral socket for receiving the nut in the second pressure plate engages the nut. 2. The elastomeric seal block assembly of claim 1 wherein the rib is crushed by fully inserting the nut into the socket to provide a secure mechanical connection between the pressure plate and the nut. Pressure equipment for. 10. A bolt screw cap made of resin for covering a threaded portion of a bolt shaft projecting from a nut, the bolt screw cap having a base firmly attached to a socket of the second pressure plate. The pressure equipment for an elastomer seal block assembly according to claim 1. 11. The pressure equipment for an elastomer seal block assembly according to claim 1, wherein said nut is welded to said socket portion of said second pressure plate by ultrasonic welding. 12. The elastomer seal block set according to claim 2, further comprising a cap having a threaded portion for a resin bolt for covering the threaded portion of the bolt shaft protruding from the bolt receiving hole of the second pressure plate. Pressure equipment for 3D. 13. The pressure equipment for an elastomer seal block assembly according to claim 10, wherein the bolt screw cap is formed of a molded elastomer resin. 14. A cap having a threaded portion for the bolt is integrally connected to the pressure plate so as to completely engage the pressure plate with the periphery thereof, and the cap is further provided with a bolt shaft. The pressure device for an elastomeric seal block assembly according to claim 12, having an internal thread receiving the other end and engaging the bolt with it. 15. A bolt head cap made of resin for covering the bolt head, the bolt head cap having a base secured in the socket portion of the first pressure plate. 15. Pressure equipment for an elastomeric seal block assembly according to any of the preceding claims. 16. The pressure device for an elastomer seal block assembly according to claim 1, wherein the cap having the threaded portion for the bolt is formed of a molded elastomer resin. 17. A replaceable unit having a plurality of elastomeric seal blocks annularly connected to one another around a conduit for forming a seal against an opening between the annular conduit and the wall. A pressure device in a seal block assembly, wherein each seal block has at least one pressure bolt hole parallel to the central axis of the conduit and passing through the seal block, and wherein the seal block has a shaft. For compressing and expanding the plurality of sealing blocks, which are pressure devices that are compressed in the radial direction and radially expanded to form a seal between the conduit and the wall surrounding it from outside. The set of pressure equipment comprises: a plurality of second molded resin pressure plates each having a plurality of multi-sided sockets for covering outwardly of the pressure plate; wherein the socket comprises: Inaccessible when the sealing block equipment is in a position to provide a seal between the conduit and the wall, a corresponding plurality of nuts, wherein one of each nut socket is a respective nut. At least one integral rib projecting to engage the nut into the socket of each nut socket, the size and shape of the ribs matching the nut sockets in the second pressure plate. And each of the nut sockets having, so that sufficient insertion of the nut into the nut socket comprises:
A seal block assembly that curves the ribs while retaining the nut in the socket to provide a secure mechanical connection between the pressure plate and the nut.