Patent Abstract:
A gasket for converting a standard mechanical joint into a restrained mechanical joint without the need for altered configuration of the bell, spigot, or gland of the joint, and without the need for additional fittings or devices. In the practice of the present invention, a standard mechanical joint&#39;s bell and gland configuration can be employed to connect a spigot end of one pipe length to the bell end of another pipe length in a restrained relationship, with the restraint based on forces superior to rubber-to-pipe friction. In more particular discussion of the embodiments taught, the invention includes forming the gasket to fit within the bell in such a manner that a void, or gutter, exists during rest, into which void the gasket compresses, which in turn influences the rotational motion of the segment. In this manner, the configuration of the gasket influences the timing and extent of rotation throughout the process of securing the gland to the bell.

Full Description:
This is a continuation in part of currently co-pending application Ser. No. 09/590,586 filed on Jun. 8, 2000, to which this application claims priority and benefit, and which hereby is incorporated by reference. 

   BACKGROUND OF THE INVENTION 
   1. Field of the Invention 
   This invention relates generally to connections between lengths of pipe, or between pipes and fittings. More particularly, the invention is directed toward a device and method of connecting two lengths of pipe that maximizes the advantages of both restrained push-on joints as well as mechanical joints, as are known commonly in the art. The invention has application to long-run pipe lengths as well as fittings, appurtenances, and connections. 
   2. Description of Related Art 
   Due to thrust forces, earth movement, and external mechanical forces exerted on pipes, the industry has focused substantial attention on the problem of maintaining connections between adjacent lengths of pipe after installation. The result of this attention is a library of differing solutions and approaches known in the art. The majority of these solutions can be categorized as either “push-on” joints or “mechanical joints.” References to “pipe” made by the inventor with respect to application or use of the present invention shall be understood to include fittings, connections, and any other appurtenances to pipes. 
   The most common connection device used in the art for connection of straight-run lengths of pipe is a “push-on” pipe/bell configuration. These push-on solutions are exemplified by U.S. Pat. No. 2,953,398, and account for the majority of straight-run pipe connections. In a typical configuration, a spigot end of a pipe slides into a bell end of another pipe past a tightly fitted gasket. No follower ring, stuffing box, or other external compression means typically is present in a push-on joint. Additionally, the typical push-on joint does not include a restraining means, though such means as tie bars, concrete thrust blocks, screws, and additional ring attachments have been employed in some cases to effect restraining to the joints. Advancements in the art have led to innovations and modifications of push-on joints to include restraining means. Examples of such restrained push-on joints include U.S. Pat. Nos. 5,295,697; 5,464,228; and 5,067,751. The securement of the connection in such advancements may be effected by locking segments or wedges within the gasket that engage the spigot. The locking segments are oriented in such a manner as to allow entry of the spigot into the bell, but upon counterforces tending to effect removal of the spigot, the segments pivot toward a biting engagement with the spigot, stopping further removal. The effect is much like a child&#39;s “finger lock” toy, the stronger the attempt to remove the pipe, the greater the locking effect exerted by the inserts. These push-on type joints enjoy superior flexibility and resistance to both axial and para-axial separative forces. Meaningful difficulty has been experienced in the industry, however, in applying these connections to fittings, where it may be impracticable to secure the fitting sufficiently to exert the high installation pressures necessary initially to push the spigot into the bell in such configurations. 
   A “mechanical joint” is a well-known standardized connection device widely employed in the pipe industry. Such a joint fluid-seals two lengths of pipe together by compressing a gasket around a spigot and within a bell at the intersection. Mechanical joints are characterized by an outwardly flanged bell of a receiving pipe, into which a spigot of a second pipe is inserted. The bell is adapted to seat a gasket that fits snugly about the circumference of the spigot of the second pipe, and further to receive a supporting compression ring or gland. In assembly, the spigot is fully advanced into the bell and the gasket is firmly seated within the bell and around the spigot. The gland is then forced against the gasket by fastening it securely to the bell flange through such means as fastening bolts tightened under relatively high torque. This configuration typically includes a lip about the inner diameter of the gland that upon securement extends axially within the bell. The configuration of the gland is such that as the lip is forced against the gasket, the gasket becomes compressed under pressures sufficient to deform the gasket. As the gasket is compressed between the bell and the gland, the gasket therefore is squeezed inwards toward and into sealing contact with both the exterior of the inserted pipe section and the interior of the bell. This deformation enhances the sealing effectiveness of the gasket beyond that which can be readily obtained in the absence of compression or high insertion forces 
   The mechanical joint enjoys wide acceptance in the industry, and is the subject of national and international standards such as ANSI/AWWA C111/A21.11-95. Given the industry affinity for such joints and the embedded nature of these standards into specifications, any mechanical joint should conform to these specifications to gain optimal acceptance. Numerous attempts have been made to improve upon the standardized mechanical joint. These attempts are almost uniformly characterized by the inclusion of an additional mechanism or attachment, creating a mechanical connection resistive to separation of the pipes. Such attempts that require modification of the bell or gland (or both) are exemplified by U.S. Pat. No. 784,400 to Howe, which employs locking inserts recessed within the gland; U.S. Pat. No. 1,818,493, to McWane, which discloses a modified gland that relies upon specially modified bolts having toothed cams that both pivot on and bite into the spigot as the bolts are hooked under a modified lip of the bell and forced into grooves in the gland. 
   Further solutions employ additional restraining devices or teeth interposed between the gasket and the gland, which are driven into the spigot as the gland is tightened. Included among these devices are U.S. Pat. No. 4,664,426, to Ueki; and U.S. Pat. No. 5,297,826, to Percebois, which each require the use of multiple additional locking devices in addition to the standard mechanical joint&#39;s simple bell-gasket-gland configuration. U.S. Pat. No. 4,878,698, to Gilchrist, U.S. Pat. No. 5,335,946, to Dent, et al, and U.S. Pat. No. 5,398,946, to Hunter, et al., appear susceptible to, possible early engagement of the biting teeth prior to full seating of the gland. U.S. Pat. No. 5,803,513, to Richardson and others attempt to solve this potential problem by use of sacrificial skid pads to prevent early engagement of the teeth. 
   Additional solutions employ a bolting assembly attached to (or incorporated into) the bell, which assembly is oriented such that upon tightening of certain specially configured bolts, the bolts or a device actuated thereby are driven into the outer surface of the spigot. These bolting schemes are exemplified by devices sold by EBAA Iron, commonly known in the art under the trademark MEGALUG (Registration No. 1383971) Further examples of this type of solution include U.S. Pat. No. 4,647,083, to Hashimoto, which modifies the standard gland to include bolts that act upon locking wedges when tightened. When a pipe is installed in a ground-bedded environment, it is typically inconvenient to have multiple additional bolting requirements on the underside of the pipe as laid. Such underside boltings increase the cost and time of installation. If, however, the bolt-in locking scheme employs only a few bolt locations, the inward pressure of the bolts may in some conditions tend to deform the cross-sectional profile of the spigot. For example, employment of only three bolt locations in some circumstances may exhibit an undesirable possibility of deforming the spigot into a slightly triangular shape. 
   It will be noted by those reasonably skilled in the art that each of these configurations also suffers from practical issues, such as the expense of manufacture of additional components and the fact that additional components increase the potential for unacceptable failure. 
   Furthermore, each of these solutions may be considered a “static” connection. Although pipelines are traditionally considered to be rigid and immobile structures, a durable connection must allow for a certain amount of flexibility and “play” at joints. Such accommodation to movement is necessary because the environments in which pipelines lay are not truly static. Thrust forces may create non-longitudinal, or para-axial, loads that tend to drive a pipe length toward an angle from the longitudinal axis of the lengths to either side of such axis. As the pressures of the material being transported within the pipe vary, the forces will similarly vary. Additionally, locations in which pipes are run rarely are as stable as commonly believed. In fact, pipes may be run above ground, in which cases such pipes do not enjoy the benefit of any stability enhancing factors of bedding or trenched installation. Finally, even typical earth-bedded pipes must endure shifting due to sedimentation, erosion, compaction, mechanical forces (such as nearby construction), and earth movement (such as earthquakes). 
   A variation of the push-on joint is evidenced by U.S. Pat. No. 2,201,372, to Miller, which employs a compression snap-ring fitted within a special lip of the bell, in order to exert pressure onto the locking segments and thus drive them into the spigot. Alternatives in Miller similarly drive locking segments into the spigot upon installation. U.S. Pat. No. 3,445,120, to Barr, likewise employs a gasket with stiffening segments completely encased therein that are generally disposed in a frustroconical arrangement. Such segments are stated to give the gasket a resistance to compression along the plane that includes both ends of the segment. When a spigot is subjected to withdrawing forces, the gasket rolls with the movement of the pipe. As the gasket rolls, it is intended to eventually encounter a position in which the stiffened plane needs to compress for further rolling. In optimal conditions, due to the stiffening, the gasket cannot compress and therefore cannot roll further. As the rolling stops, the gasket becomes a static friction-based lock between the spigot and the bell. Notably, among other distinctions, the arrangement taught by Barr remains a rubber-to-pipe frictional connection. 
   OBJECTS OF THE INVENTION 
   The following stated objects of the invention are alternative and exemplary objects only, and no one or any should be read as required for the practice of the invention, or as an exhaustive listing of objects accomplished. 
   As suggested by the foregoing discussion, an an exemplary and non-exclusive alternative object of this invention is to provide a gasket interchangeable with gaskets of standard mechanical joints which allows for the transformation of the joint into a restrained joint without the need for any reconfiguration or adaptation of the bell, spigot, or gland of the mechanical joint involved. 
   A further exemplary and non-exclusive alternative object is to provide a dynamic connection for pipes that does not require high insertion pressures. 
   A further exemplary and non-exclusive alternative object of the invention is to provide for a cost effective manner and device of restraining a typically configured pipe joint. 
   The above objects and advantages are neither exhaustive nor each individually critical to the spirit and practice of the invention, except as stated in the claims as issued. Other objects and advantages of the present invention will become apparent to those skilled in the art from the following description of the invention. 
   BRIEF SUMMARY OF THE INVENTION 
   The present invention may be described basically as a gasket for converting a standard mechanical joint into a restrained mechanical joint without the need for altered configuration of the bell, spigot, or gland of the joint, and without the need for additional fittings or devices. In the practice of the present invention, a standard mechanical joint&#39;s bell and gland configuration can be employed to connect a spigot end of one pipe length to the bell end of another pipe length in a restrained relationship (restraint being defined as resistance to axial separation of a mated bell and spigot), with the restraint based on forces superior to rubber-to-pipe friction. In more particular discussion of some of the embodiments taught, the invention includes forming the gasket to fit within the bell in such a manner that a void exists during rest, into which void the gasket deforms, which in turn influences the rotational motion of the segment. In this manner, the configuration of the gasket influences the timing and extent of rotation during the process of securing the gland to the bell. Overpenetration may be avoided, while at the same time ensuring sufficient penetration at the proper moment in time. Controlling the timing and extent of locking segment rotation influences gasket performance and is addressed by the described embodiments of this invention. The extent of segment rotation affects the application of restraint. Once restraint occurs, which typically is when the segment has rotated into an interference position between bell and spigot, further meaningfully helpful gasket compression typically no longer occurs. Rotating the segment too early yields insufficient gasket compression for adequate sealing. Rotating the segment too late may not sufficiently restrain the joint. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
       FIG. 1  shows an diagram of the typical mechanical joint, having a gasket in place. 
       FIG. 2  depicts a cross-sectional view of an un-stressed gasket of the present invention in the initial phase, at a location in which the position and cross-section of the locking segment can be viewed. 
       FIG. 3  demonstrates the cross-sectional view of an embodiment of the gasket. 
       FIG. 4  is a depiction of the gasket and segment in the joint during the act of assembly, in the transition phase. 
       FIG. 5  shows an embodiment of a locking segment configuration useful in the present invention. 
       FIG. 6  shows the joint of the present invention following compression and in a locked state, restraining the joint. 
       FIG. 7  is an alternative embodiment of the locking segment useful in a gasket of the current invention. 
       FIG. 8  is a cross-sectional view of a gasket for use in the current invention, showing an alternate embodiment of the locking segment in place. 
   

   DETAILED DESCRIPTION OF THE INVENTION 
   The following is a detailed description of the invention. Those skilled in the art will understand that the specificity provided herein is intended for illustrative purposes with respect to the inventor&#39;s most preferred embodiment, and is not to be interpreted as limiting the scope of the invention. References to “pipe” herein shall be understood equally to refer to any pipe length, appurtenance, fitting, or any other connected device or element regardless of the method or material of manufacture. 
   Turning now to the drawings,  FIG. 1  presents a diagram of a typical mechanical joint. Assembly of the joint according to the current invention is practiced as known in the art. Particularly, but without limitation of the known variants which shall be as equally applicable to the present invention as they are to the known art, the joint contains the following elements in the following relationship. Compression ring or gland  11  is placed on spigot  10 , following which gasket  2  is placed around the exterior of spigot  10 . Spigot  10  is then advanced within bell  12  until the end  41  of spigot  10  is stopped by an annular shoulder  42  within bell  12 . Gasket  2  is advanced into bell  12  until it seats in the annular recess seat  43 , as shown. Gland  11  is then abutted against gasket  2  and is secured to bell  12  by securing devices  44 , which are presented for illustration here as bolts  45  passing through perforations  46  and engaged by nuts  47 . As is evident, upon drawing up or tightening of nuts  47 , gland  11  is compressed against gasket  2 , causing it to compress. Alternative securing means will be apparent to those in the industry, such as overcenter clamps, cam locks, ramped wedges, ramped annular rings, and rivets, and could include any mechanism that may be used to decrease the axial spacing between the gland  11  and the bell  12 . Due to the constraining presence of recess seat  43  and gland  11 , deforming of gasket  2  may be directed primarily radially inward toward and into sealing engagement with spigot  10 . The invention of the present disclosure builds upon this interrelationship and requires no changes to the spigot, bell, or gland, though such changes may be accommodated within the spirit of the invention if such modifications are otherwise desired. 
   As will be known in the art, traditional understanding counsels that the profile of the gasket  2  in a resting state substantially match with the internal profile of the bell  12  at the location in which the gasket  2  is intended to reside in final assembly. The purpose of such matching profiles is to allow for tight mating of the gasket  2  into the bell  12  to enhance fluid seal. In the shown embodiment, this conventional wisdom would counsel for the radially outward profile of the gasket  2  to have approximately the same configuration as recess seat  43  of bell  12 . As shown in  FIG. 1 , in a resting state the primary mating surfaces of a prior art gasket would mate smoothly with the internal surfaces of the bell  12 . Accordingly, in prior art gaskets, following assembly the profile of the gasket at these areas of sealing interface is substantially the same as the profile of the gasket in the resting state. 
   As is depicted in  FIGS. 2 and 8 , the locking segment  1  of the present invention may be constructed to fit within a gasket  2  that is configured to fit within any standard mechanical joint without necessitating changes to the configuration of the bell, gland, or spigot. Gasket  2  is an elastomeric or other resilient or deformable material, such as those in the art will understand may be used in the practice of a mechanical joint. A useful configuration of the gasket  2 , as shown in  FIG. 3 , is an annular ring with a radially inner surface  4  that is adapted to be in contact with spigot  10 , a gland face  7  that is adapted to be compressed by a gland or compression ring  11 , a front face  61  that leads in axial insertion, and a radially outer surface, shown in the drawings as having a configuration that does not mate smoothly with the recess seat  43  in a resting state. Particularly, in the shown embodiment, the radially outer surface of the gasket  2  has a compression seat surface  9  at the leading portion of the gasket  2  near the front face  61  that is designed to mate with and seal against an area of the recess seat  43 . Also characterizing the shown embodiment is a distortion control surface  62  that in the resting state leads away from the recess seat  43  to form a radially depressed gutter  63 , before the profile of the gasket  2  extends once again radially outward to meet the bell  12  in the area of rear seal  64 . Accordingly, the radially outer surface in the shown configuration is the entire area between and including the compression seat surface  9  through rear seal  64 ; stated differently with reference to the drawings, the radially outer surface is in  FIG. 3  the entire “upward” surfaces of the drawing combined. Although these surfaces are readily distinguishable in the drawings and as discussed herein, the transition among surfaces may not be as readily apparent in the uncompressed state as in the configuration shown. In the shown embodiments, gasket  2  conforms to all of the requirements of ANSI/AWWA C111/A21.11-95. In particular, for any given spigot  10 , gasket  2  may have a slightly smaller inner diameter than the outer diameter of the spigot  10 . Accordingly, placement of gasket  2  over the exterior of spigot  10  may require exertion of force to expand gasket  2  to fit around spigot  10 . 
   Alternatively described, it will be noted that the gutter  63 , being an annular depression (radially speaking) is characterized by the fact that if gasket  2  is advanced into the bell  12  as fully as is possible in the resting state (e.g., prior to deformation), and rotated to contact the bell  12  in the area of the recess-seat  43  as much as possible without deformation, a void remains between the gasket  2  and the recess seat  43 ; such depression or void is the gutter  63 . As shown  FIGS. 2 and 4 , in this embodiment a portion of the gutter  63  remains vacant of gasket material, even during some advanced stages of compression and assembly. It will be noted that the gutter  63  in other embodiments could be covered by a film of rubber or otherwise be a void below the radially outward surface of gasket  2 , and still be and operate as a gutter  63  in the spirit and scope of the invention. 
   Without limiting the application of the structure, effects, or scope of the invention or other possible advantages of practice of the invention, the operational aspects of having this void are believed in the shown embodiment to confer at least two advantages, either of which alone would be an advance in the art. (It should be noted that applicant does not limit the invention by this discussion to only embodiments that possess one or more of these advantages. First, the compression of compression seat surface  9 , and separately of distortion control surface  62 , against recess seat  43  in different locations is believed to create two separate areas of sealing, with gradients of compression between the points of initial contact with the recess-seat  43 , such that sealing efficiency is enhanced. Also, rear seal  64  in compressive contact with gasket land  49  may create yet another area of sealing. This appears to create maximum pressure against at least one point in the area of the gasket  2 , which serves to resist high fluid escape pressures, while still taking advantage of the flexibility and other advantages of high surface-area, lower-pressure sealing. 
   A second perceived benefit is an operational effect on the motion of the segment  1 , which is described in more detail, below. 
   Gasket  2  incorporates at least one locking segment  1 , which may be configured as shown in  FIG. 5 , also shown as embedded in the gasket  2  in  FIG. 8 . In the usual practice of the invention, a number of locking segments  1  will be circumferentially dispersed about and within gasket  2 , and though preferable, the placement need not be precisely or even nearly symmetrical. The number of such segments  1  may be selected with reference to the expected separative forces to be encountered by the joint, with a higher force tending to recommend a larger number of segments  1 . The inventor prefers to use no fewer than three such segments  1 , but the invention is not so limited. For example, a preferred configuration of segments  1  for use with a pipe of eight inch diameter intended to carry fluids at pressures of 350 p.s.i. includes eight to ten segments  1  uniformly spaced around the spigot-facing circumference of gasket  2  (e.g., the radially inner surface  4 ). An alternative would allow a single segment  1  of a circumference appreciable to (at least one-half the size of) the circumference of gasket  2 . 
   Separative forces (shown diagramatically as vectors  50 ,  50   a  and  50   b  in  FIG. 1 ) tend to extract spigot  10  from bell  12 . As indicated by directional arrow  50 , some separative forces follow in-line with the common axis of assembled pipe lengths. Other separative forces are para-axial, as shown by vectors  50   a  and  50   b , which may be due to bedding shifting or non-uniform securement around the periphery of spigot  10 . Segment  1  is intended to grip spigot  10  and to translate separative forces into forces at least partially opposing bell  12 . To this end, segment  1  possesses teeth  6  that are adapted to protrude from inner surface  4  of gasket  2 , at least upon compression of gasket  2  by gland  11 . Teeth  6  are adapted to contact spigot  10 , and are most preferably fashioned of a substance that is harder than the material comprising the exterior of spigot  10 . In a particular embodiment, teeth  6  are, in the uncompressed state of gasket  2 , already exposed from the inner surface  4  as shown by  FIG. 8 . This exposure may be by protrusion from the inner surface  4 , or by slight recessing beneath inner surface  4  in combination with the absence of gasket material covering the teeth, which is the embodiment shown in  FIG. 3  and subsequent images. As shown in  FIGS. 3 and 8 , the gasket  2  may be configured with a recess about teeth  6  to prevent interference with penetration of such teeth  6  into spigot  10 . An alternative preferred embodiment presents teeth  6  slightly recessed within gasket  2 , and covered by a membrane or thin layer of compressible or puncturable material. The inventors suggest that at least some of the area between teeth  6  or immediately adjacent to teeth  6  be free of rubber to allow penetration of the spigot  10 . An advantage of initial concealment is that it allows for greater advancement of gland  11 , and thus greater compression of gasket  2 , prior to substantial engagement of teeth  6  into spigot  10 . A greater sealing effectiveness therefore may be achieved. 
   Preferably, segment  1  possesses a plurality of teeth  6 . In a tested configuration, the tips of teeth  6  are arranged in an arcuate relationship. The arcuate relationship enhances the ability of teeth  6  to bite into spigot  10  despite any variations in circumference of spigot  10  or the inner dimensions of bell  12 . This is because a larger gap (frequently due to manufacturing tolerances) between spigot  10  and the inner dimensions of bell  12  (particularly annular gasket recess seat  43 ) will cause segment  1  in assembly to be rotated upon compression of gasket  2  toward a steeper angle relative to spigot  10  than exists in the unstressed configuration as displayed in  FIG. 2 . Given the arcuate relationship of teeth  6 , upon such rotation of segment  1  the most axially inner teeth rotate into contact with spigot  10 . The arcuate configuration further urges at least two teeth  6  to be in contact with spigot  10 , regardless of the rotation of segment  1 . This is because in the arcuate configuration, a straight line can be drawn between any two adjacent teeth  6 . Beneficially, the presence of additional teeth  6  to either side of any biting tooth  6  tends to assist in preventing overpenetration of the spigot  10  by segment  1 , due to the fact that these adjacent teeth will be pointed at an angle to spigot  10  such that they are not optimally positioned for biting; rather, adjacent teeth  6  will tend to contact spigot  10  at an angle substantially more parallel to spigot  10  than those teeth  6  that are biting into spigot  10 . Accordingly, because of the more-parallel angle, adjacent teeth  6  act as stops to further penetration. 
   In a shown configuration as detailed in  FIG. 5 , segment  1  in cross section has a toothed edge  16 , with teeth  6  extending therefrom in the arcuate pattern as above discussed; and a back face  13 , extending radially and axially along a slope towards protrusion  17 . Back face  13  as shown is adapted to be in a close proximity to, or even in direct contact with, gland  11  when the mechanical joint is assembled. Connecting protrusion  17  in the axially inner direction with toothed edge  16 , is a surface, or a series of surfaces, denoted compression faces  15 . In this embodiment, back face  13  is in close proximity to gland  11  when the joint is assembled, and upper protrusion  17 , being the most radially outer area of the segment, is in close proximity to gasket land  49  of the bell. A greater volume of elastomeric material of gasket  2  exists between compression seat surface  9  (particularly shoulder  8 ) and segment  1  than is present between back face  13  and gland  11 . 
   Upon insertion of spigot  10  into gasket  2 , toothed edge  16  of segment  1  may be forced radially outwardly by the presence of spigot  10 , and may cause pivoting of segment  1 . The volume of compressible material present between the segment&#39;s compression faces  15  and recess seat  43  allows for such outward movement or pivoting without compromising the integrity of gasket  2 . Given the arcuate configuration of teeth  6  along toothed edge  16 , even when rotated radially outwardly, at least one tooth  6  will be poised for contact with spigot  10  upon compression (though the inventor recognizes within the spirit of the invention that any or all of teeth  6  may be removed from direct physical contact with spigot  10  due to teeth  6  of segment  1  being recessed in gasket  2  or the presence of a thin layer of elastomeric material, or other substance, so long as the material, or substance is not sufficient to interfere with the effective grip of at least one of teeth  6  into spigot  10  upon full compression of gasket  2 , as is described below). Spigot  10  may be advanced as in the prior art until stopped by annular shoulder  42 . 
   Following such insertion of spigot  10  into bell  12 , gasket  2  will be in a position basically as represented in  FIG. 2 , and the gasket  2  may be already in contact with recess-seat  43  at some point. In any event, substantial compression of gasket  2 , as in compression sufficient to effect the sealing and securement of the joint is not at this point effected. Further assembly is carried out by advancing of gland lip  71  against the gasket  2  gland face  7 , and into the bell  12 . As will be evident to those skilled in the art, this advance of gland  11  will by contact with gasket  2  force gasket  2  inwardly into contact or more forceful contact with recess seat  43 . As shown from  FIG. 4 , gasket  2 , and in the shown embodiment specifically compression seat surface  9 , begins deformation against recess-seat  43 . Deformation of gasket  2 , particularly in the area of distortion control surface  62 , begins to occur in the shown embodiment prior to substantial rotation of segment  1 . This phase of the assembly operation is considered the initial phase and is characterized by substantially translational motion of the segment. The forces acting on the segment are principally balanced between gland  11  acting on the back face  13  of segment  1  and the compression energy stored in the gasket rubber trapped between segment  1 , spigot  10  and bell  12 . This compression energy acts on segment  1  at a location known as the “center of pressure” that is believed in the shown embodiments to be substantially in line with the force vector imparted by gland  11  acting on segment  1 . 
   As gland  11  continues to advance into bell  12  beyond the point shown in  FIG. 4 , segment  1  begins to rotate. This phase of the assembly operation is the transitional phase and is characterized by a relatively decreasing amount of translational motion of segment  1  and a relatively increasing amount of rotational motion of segment  1 . In other words, upper protrusion  17  advances into the bell at a faster rate than teeth  6  for a given input by gland  11 . This occurs because the center of pressure of the compression energy stored in the gasket moves closer to the teeth  6  of segment  1  and away from upper protrusion  17  as the gasket is compressed. Rotation of segment  1  at this point is influenced by the gutter  63  and is related to the movement of the center of pressure of the gasket toward teeth  6 . Because gutter  63  presents the area of least resistance to compression, and hence to deformation (it being known in the art that rubber tends to deform, in preference to compressing), the upper (as seen in the Figures) portion of the segment  1  rotates toward the gutter  63 , reducing the size of the gutter  63  as the gasket material deforms into the area. 
   Rotation of segment  1  continues substantially in this manner as the gland  11  advances until the point at which segment  1  is in resistive contact with both spigot  10  and bell  12 . This phase of the assembly operation shall be known as the final phase and in the shown embodiment is characterized by a substantially rotational motion of segment  1  and a substantial collapse of gutter  63 . This segment and gasket orientation is depicted by  FIG. 6 . The resistive contact in the shown embodiment is specifically between a tooth  6  and protrusion  17  of segment  1  and the corresponding joint surfaces of spigot  10  and bell  12 . Until the final phase of assembly is entered, if a tooth  6  is in resistive contact with spigot  10 , or protrusion  17  is in resistive contact with bell  12  it will be understood that this contact is of a sliding nature. Upon the substantial collapse of gutter  63  and the start of the final phase of assembly, further gasket deformation is extremely limited which effectively prevents further translation of segment  1  further in the axial direction. Any additional clamping force applied to the securing mechanism between gland  11  and bell  12  (e.g. the bolts  44 ) imparts a large rotational energy to the segment due to the imbalance between the force vector created by contact of gland  11  and segment  1  vs. the vector between the center of pressure of gasket  2  and segment  1 . Any further rotation of segment  1  now causes a penetration of segment  1  into spigot  10  by teeth  6  and a penetration of segment  1  into bell  12  by protrusion  17  via plastic deformation of spigot  10  and bell  12 . This penetration provides a mechanical lock between spigot  10  and bell  12  via segment  1  and thus joint restraint is obtained. 
   Following installation, it will be evident from the foregoing description that at least one tooth  6  remains in gripping contact with spigot  10  and protrusion  17  remains in contact with bell  12 . Any attempt of the spigot  10  to move outwardly of bell  12  urges at least this one tooth  6  to move axially outwardly of bell  12  along with spigot  10 , but axial movement is not possible due to the resistive contact between back face  13  and lip  71  of the gland and a rotation of the locking segment in a direction that exerts axial resistance as well as radial pressure among the segment  1 , the bell  12 , and the spigot  10 . This axial resistance, or restraint, is caused by the segment rotating into a direction in which its length is greater than the distance between the spigot  10  and the bell  12 . The balance between the axial load and the radial load imparted to the bell and spigot affects the performance of the invention and may be influenced by the configuration of segment  1 . As the forces trying to separate bell  12  and spigot  10  increase so does the axial resistance imparted to bell  12  and spigot  10  by segment  1 . The radial load also imparted keeps teeth  6  and protrusion  17  of segment  1  engaged with spigot  10  and bell  12  respectively. If the radial component is too low, then the segment  1  will disengage spigot  10  or bell  12 . If the radial component is too high, then excessive deformation or penetration of spigot  10  by segment  1  may occur. 
   The inventors note that this feature, like others shown in the embodiments, may exhibit particular advantages, but that the presence or absence of these features and advantages required of the scope of the invention only as limited in each particular claim. Except to the extent expressly included in a claim, the inventors do not consider these advantages, configurations, or possibilities to be limitations on the invention. 
   Manufacturing tolerances for spigots and bells are not precise; accordingly, in some installations, the distance between spigot  10  and bell  12 , including features of bell  12  such as recess seat  43 , will be greater or less than such distance in other installations. Under the above described embodiment of segment  1 , where the gap between spigot  10  and recess seat  43  is as intended or smaller, upon securement of gland  11  at least on of teeth  6  of segment  1  is driven into spigot  10  and and upper protrusion  17  is driven into bell  12 . The inventor believes that due to the supportive pressures of the gasket material, segment  1  does not begin biting engagement with spigot  10  until a generally effective seal among bell  12 , spigot  10  and gasket  2  has been effected by compression. Accordingly, teeth  6  are unable to prematurely engage spigot  10  in a manner that may adversely affect the ability to obtain optimal compression of gasket  2 . This delayed engagement can be manipulated by the means discussed above; namely, the configuration of the gasket, notably the gutter  63 , compression seat surface  9 , distortion control surface  62 , elastomeric characteristics of the gasket  2 , shape of segment  1 , position of segment  1  in gasket  2  or various combinations of these features. Due to contact with bell  12  in addition to gland  11 , separative forces are transferred by segment  1 , not just against gland  11  but also against bell  12 . This is significant in that it reduces a potentially substantial force that is resisted by bolts  45  and gland  11 . Under high loads, bolts  44  and gland  11  may distort, reducing sealing effectiveness of gasket  2 ; the current invention&#39;s ability to transfer a significant portion of the magnitude of the separative vector directly to bell  12  via segment  1  therefore enhances the effectiveness of sealing. 
   In contrast to situations as in the previous paragraph, in which the distance between spigot  10  and gasket recess seat  43  is relatively small, an exaggerated pivoting mechanism is believed to occur in segment  1  when the gap is larger, as follows: 
   The condition that exists in a large gap situation (e.g. when the manufacturing tolerances and assembly conditions exist such that bell  12  dimensions are at a maximum diameter condition and spigot  10  dimensions are at a minimum diameter condition) is such that upon initial assembly, neither gasket  2  or segment  1  may be in contact with either one or both spigot  10  or bell  12 . During the transition phase gasket deformation will occur, as previously described, due to compressive forces acting on gasket  2  by spigot  10 , gland  11  and bell  12  forcing gasket  2  into contact with both spigot  10  and bell  12 . At this point however, segment  1  may still not be in contact with either spigot  10  or bell  12 . Approaching the end of the transitional phase of assembly, as gutter  63  of gasket  2  closes up due to elastic deformation of gasket  2  caused by compression of gasket  2 , a dramatic rotation of segment  1  will occur due to the previously described shift in the center of pressure of the compressed gasket and its relationship to segment  1 . This dramatic rotation allows segment  1  to bridge large gaps for which restraint would otherwise be impossible to provide. The final phase of assembly then proceeds as previously described with teeth  6  embedding in spigot  10  and protrusion  17  embedding in bell  12 . 
   In an embodiment of segment  1 , upper protrusion  17  may be formed in an angular configuration. Such an angular configuration will cause such points to bite into bell  12  when sufficient pressure is exerted between segment  1  and bell  12 . Although such biting can occur in any event under appropriately high pressures, particularly in the small-gap situation addressed above, the propensity to bite can be controlled by adjusting the acuteness of the angle. The inventor notes that the more acute the angle at either given point, the earlier along a pressure curve the point will likely bite into bell  12 . Accordingly, it is possible to adjust the tendency toward desired points of final rotation of segment  1  by adjusting the acuteness of angle of the upper protrusion  17 , which will in turn adjust the maximum probable radially outward movement of upper protrusion  17 . It should be noted that at pressures sufficient to drive upper protrusion  17  into bell  12 , rotation of segment  1  will be substantially prevented and will occur under conditions of plastic deformation of either segment  1 , spigot  10  or bell  12 . This mechanism can be employed to balance the rotation of segment  1 -and control the point of engagement. 
   Similarly, if upper protrusion  17  is configured in a radiused fashion, movement of segment  1  may be adjusted to allow axial movement of segment  1  until upper protrusion  17  obtains non-compressible abutment with bell  12 , at which point the axial and radial forces acting on segment  1  at upper protrusion  17  cause the pivot point to occur in its near vicinity. Variations of this allow further control of segment engagement and the balance of axial and radial loading distributed to all load carrying components of the invention. 
   An alternative embodiment, as shown in  FIG. 7 , may be to incorporate an elbow  3  into the back face of segment  1 . Elbow  3  will contact gland  11  during securement of the restraining devices  44  in the initial stages of the transitional assembly phase. The location and configuration of elbow  3  may be tailored to further alter the behavior of segment  1  during rotation, engagement and lockup. The location and configuration of elbow  3  may be further explained by addressing several characteristics of elbow  3  which may be modified to alter segment behavior. If elbow  3  is given a sharp radius, elbow  3  may be made to penetrate gland  11  at the contact point. This penetration will impart additional resistance to further rotation of segment  1  when the final assembly phase is complete thus relieving some of the reliance on the angle of the line of action segment  1  makes relative to spigot  10  and bell  12  when balancing the segments axial and radial load carrying distribution. Additionally, elbow  3  may be positioned radially outward or inward on segment  1 . Placing elbow  3  radially outward on the segment will increase the rotational tendency of the segment during the transitional phase of assembly promoting earlier engaement and lockup of segment  1 . Placing elbow  3  radially inward on segment  1  will have a correspondingly opposite effect. 
   If elbow  3  is made such that it penetrates gland  11  while at the same time upper protrusion  17  penetrates into bell  12 , a situation may be created whereas both axial and radial loads transferred into bell  12  may be balanced along multiple load paths. 
   Building upon the concept of altering the acuteness of elbow  3  and upper protrusion  17 , the transition between such points may be less pronounced than in  FIG. 2 . In fact, the transition may be so smooth as to create a general curve that acts as both elbow  3  and upper protrusion  17 . A curve could be adapted to effect biting engagement, whether by altering the radius of curvature, or by including nubs or other points to operate as engagement points (which, for purposes of this invention could be considered to be elbow  3  or upper protrusion  17 ). 
   Further alternative embodiments that may be included with the foregoing or otherwise substituted for gutter  63  or the area around gutter  63  include the strategic positioning of a secondary or tertiary elastomeric material having different deformation characteristics than the remainder of gasket  2 . Such strategic positioning may optimally include placement between frontal slope  15  of segment  1  in the vicinity of upper protrusion  17 . This placement would influence the potential of upper protrusion  17  to move toward annular recess seat  43 , thereby causing upper protrusion  17  to cease substantial rotation prior to biting into bell  12 . Similarly, such secondary or tertiary rubber may be placed radially outwardly of elbow  3  to influence the maximum ability of elbow  3  to move radially outwardly of spigot  10 . 
   Although much of the foregoing is discussed in terms of initial installation of a mechanical joint, the inventor notes the value and applicability of use of the present invention to “retrofit” or repair existing mechanical joints. By simply rejoinably severing the ring of gasket  2  (preferably at an angle to the radius) the gasket  2  can be fit over an existing spigot, and moved into place after removal of the old gasket. The gland  11  can then be re-attached, completing retrofitting of a standard mechanical joint to a gasket-restrained mechanical joint. 
   The foregoing represents certain exemplary embodiments of the invention selected to teach the principles and practice of the invention generally to those in the art so that they may use their standard skill in the art to make these embodiments or other and variable embodiments of the claimed invention, based on industry skill, while remaining within the scope and practice of the invention, as well as the inventive teaching of this disclosure. The inventor stresses that the invention has numerous particular embodiments, the scope of which shall not be restricted further than the claims as issued. Unless otherwise specifically stated, applicant does not by consistent use of any term in the detailed description in connection with an illustrative embodiment intend to limit the meaning of that term to a particular meaning more narrow than that understood for the term generally.

Technology Classification (CPC): 5