Corrugated-core flanges for spools and reels

A flange design providing improved strength, fracture resistance, and the like using corrugations extending substantially radially from an arbor aperture toward a rim portion. A spool or reel may include a tubular member to receive a stranded material wrapped therearound. A first flange comprising a core portion and an outer portion may secure to one end of the first flange engaging the tubular member.

A second flange may secure to the other end of the tubular member. The core portion of a flange may comprise an arbor wall defining the perimeter of an arbor aperture. The arbor wall may be directly contacted and supported by a plurality of corrugations extending radially therefrom. The outer portion of a flange may contact the core portion and extending radially away therefrom to an outer edge to restrain the stranded material in an axial direction.

The first flange further comprising corrugations substantially rectangular in radial cross section and extending radially from proximate the core radius to proximate the outer radius, the corrugations comprising a plurality of webs, each web of the plurality of webs being offset axially from and dimensionally of the same order of magnitude am adjacent webs of the plurality of webs, and a plurality of connecting walls, each connecting wall of the plurality of connecting walls extending between two adjacent webs of the plurality of webs, the connecting walls and webs being molded of a homogeneous material.

Spools and reels have suffered from a lack of intelligent application of technology for many years. Spools date back hundreds if not thousands of years. Wooden spools and reels have been used in the textile industry as well as various electrical industries for many years with almost no innovation in their structures. Some use of plastic materials began a few decades ago. Nevertheless, manufacturing techniques continue to fall short of implementing all of the principles of engineering that are available.

Manufacturing techniques tend to focus on the simplicity of manufacture, and the simplicity of design, rather than the optimization of strength, weight, stiffness, non-catastrophic failure modes, and the like. Some of these latter considerations have been found to be significant in the manufacture and use of plastic spools and reels. Accordingly, developments by Applicant have provided improved methods for providing spools and reels having substantially reduced weight with improved stiffness and cost. Moreover, failure modes are available to provide "graceful degradation" of performance rather than catastrophic failure of spools and reels in situations such as the dropping of loaded reels or spools.

Spools and reels are used in many industries. However, in the wire and cable industry, the comparative weight of stranded material on a reel or spoon is greater than others of similar size in other industries. Fracture of flanges near an outer diameter thereof is common if dropped. Likewise, due to the conventional shapes of central tubes (hubs, cores, etc.), the junctions with flanges are not inherently resistant to fracture from impact loads caused by dropping. Dropping from a working bench is common for reels and spools. Manufacturing processes for manufacturing reels and spools, as well as manufacturing processes for wire and other stranded materials, typically compels smooth circumferential edges at the outermost diameter of a flange. Accordingly, a spool not retained on an arbor during use (using the wire, rather than manufacturing and taking up the wire) may roll easily across any flat surface. Thus, while a spool or reel is considered tare weight in shipping wire and cable, and a disposable item whose cost is to be minimized a spool or reel must function reliably and durably during its entire useful life.

Otherwise, a substantial length of stranded material may be damaged beyond use. The material held on a spool or reel having a value of a few dollars may itself have a value of one thousand times the cost of a spool. A value two orders of magnitude greater than that of the spool is routine for wire of common usage.

In the art, a typical spool has a tube portion extending between two flange portions positioned at either end of the tube portion. A spool may have a rounded rim or rolled edge at the outermost diameter. This rim serves structural as well as aesthetic and safety purposes. Spools may be manufactured in a variety of tube lengths. Each flange is fitted by some fixturing to one end of the tube and there retained. Details of spools are contained in the U.S. Pat. No. 5,464,171 directed to a mating spool assembly for relieving stress concentrations, incorporated herein by reference.

The impact load of a spool of wire dropping from a bench or other work surface to a floor in a manufacturing environment is sufficient to fracture the spool in any of several places. Fracture may damage wire, preclude removal, or release the wire in a tangled, useless mass.

Spools may break at the corner where the tube portion meets the flange portion or may fracture at an engagement portion along the tube portion. Spools may break near the corner between the flange and the tube portion where a joint bonds or otherwise connects the tube portion to the flange portion.

In drop tests, a spool may be dropped axially, radially or canted off-axis. In a radial drop, spools that break typically fail near the middle of the length of the tube. In axial drops, flanges may separate from tubes in failed spools. In an off-axis drop, flanges typically fracture, and may separate from tubes, releasing wire.

Large spools are typically called reels in the wire industry. Heavy-duty reels of 12 inches in diameter and greater (6 feet and 8 feet are common) are often made of wood or metal. Plastic spools of 12-inch diameter and greater are rare and tend to be very complex. The rationale is simple. Inexpensive plastics are not sufficiently strong or tough to tolerate even ordinary use with such a large mass of wire or cable wrapped around the spool.

Moreover, large flanges for reels are very difficult to manufacture. Likewise, the additional manufacturing cost of large spools is problematic. High speed molding requires quick removal after a short cycle time. Flanges are typically manufactured to have very thick walls. Increased thicknesses directly lengthen cycle times. Thus, designs do not scale up. Therefore, the flanges have very slow cooling times and molding machines have low productivity in producing them.

The reels have an additional difficulty when they are dropped during use. The flange do not stay secured. The flange and tube are often precarious wooden assemblies held together by three or more axial bolts compressing the flanges together. The tube is prone to slip with respect to the flanges, breaking, tilting or otherwise losing its integrity under excessive loads. Such loads result from the impact of dropping onto a floor from a bench height or less. For the largest reels, rolling over or into obstacles or from decks during handling is more likely to be the cause of damage.

Hinged annular shaft flange

An annular shaft flange that can be positioned along the length of a shaft and secured to the shaft to prevent movement of an article along the length of the shaft. The annular shaft flange includes a pair of nesting ends that are attachable to each other using a mechanical interlocking member.

Previous devices, such as snap rings, cotter pins or flip pins require the shaft to be machined or drilled, thereby weakening the shaft and adding additional cost to the manufacturing process. A locking ring requires no machining, but has a greater cost penalty and can only be placed on the shaft if the diameter of the shaft is constant or has an area of reduced diameter.

Presently, annular shaft flanges, such as shown in Nell U.S. Pat. No. 5,857,800, owned by the assignee of the present application, have been successful in providing a method of securing an object along a shaft and preventing the object from moving along the length of the shaft. However, the shaft flange taught by the Nell '800 patent preferably uses a spot weld to secure the two ends of the shaft flange in place. Although spot welding has proven to be an effective method of retaining the two ends of the shaft flange, a need has arisen to provide alternate methods of securing the two ends of the shaft flange to eliminate the need for a spot weld. The apparatus and method of the present invention address this need in a novel manner.

In a first embodiment of the invention, the annular shaft flange includes a flange body that is movable between an open position and a closed position. A hinge is formed in the flange body to permit movement of the flange body between the open and closed positions.

The flange body includes an inner curved engagement surface that is sized to interact with the outer surface of the shaft when the shaft flange is moved to the closed position. The curved inner engagement surface provides an area of frictional engagement between the shaft flange and the annular shaft.

The body of the annular shaft flange extends between a first end and a second end. The first and second ends are spaced from each other when the shaft flange is in the open position. The first end of the flange body includes a first attachment projection, while the second end of the flange body includes a second attachment projection. When the shaft flange is moved to the closed position, the first attachment projection is positioned in contact with the second attachment projection.

The first and second attachment projections of the shaft flange extend generally parallel to the longitudinal axis of the shaft to which the shaft flange is being attached. Each attachment projection projects radially away from the shaft to provide areas for joining the first and second ends of the flange body to each other. Preferably, an attachment member, such as a rivet, passes through the first and second attachment projections such that the attachment member can secure the flange body in the closed position.

In the preferred embodiment of the invention, the annular shaft flange includes a shaft engagement lip that extends axially from the first end face of the flange body. The shaft engagement lip increases the overall axial width of the shaft flange and combines with the flange body to define the curved engagement surface. The shaft engagement lip increases the surface area contact between the annular shaft flange and the shaft to further prevent movement of the shaft flange along the shaft.

In an alternate embodiment of the invention, the annular shaft flange includes a flange body having a flange portion having a width defined by a first end face and a second end face. The first and second end faces are spaced from each other along the longitudinal axis of the shaft to which the annular shaft flange is mounted. The flange body includes a hinge that allows the flange body to move from an open position to a closed position. The flange body defines an inner curved engagement surface that contacts an outer surface of the shaft when the shaft flange is positioned along the shaft and in a closed position.

The shaft flange of the second embodiment of the invention includes first and second nest ends that are spaced from each other when the shaft flange is in an open position. The first nest end includes a first attachment lip, while the second nest end includes a second attachment lip. Both the first and second attachment lips have width of approximately one-half the axial width of the flange portion of the shaft flange. When the shaft flange is moved to the closed position, the first and second attachment lips overlap each other.

When the shaft flange is in the closed position, a mechanical attachment member is positioned to extend between the first and second attachment lips to hold the shaft flange in the closed position. In one embodiment of the invention, the mechanical attachment member is a rivet, while other types of mechanical attachment means, such as Tox-Loc?, are contemplated as being within the scope of the invention.

The first and second attachment lips include an inner edge surface that is spaced radially from the outer surface of the shaft to which the flange is applied. The spacing between the shaft and the inner edge of each attachment lip provides additional room for utilizing the mechanical attachment member to hold the shaft flange in its closed position.Various other features, objects and advantages of the invention will be made apparent from the following description takentogether with the drawings.

Flange device and flange method with component protection

A flange device for roll-flange a rim of a component includes a flange head, a first flange roller which is mounted by the flange head and can be rolled off on the rim during roll-flange, and a second flange roller which is mounted by the flange head and forms a counter pressure roller for the first flange roller, the flange device including a stable protective structure which is or can be fastened to the component and forms a rolling surface for one of the flange rollers or supports a rolling surface.

A method for roll-flange a component along a flange edge, using a flange device according to claim 1, comprising the steps of: a) positioning the protective structure along the flange edge relative to the component; b) rolling thefirst flange roller off on a rim strip which extends along one side of the flange edge and is to be at least partially beaded around the flange edge; and c) rolling the second flange roller off on an area of the component which extends along theother side of the flange edge, the second flange roller acting as a counter pressure roller for the first flange roller; wherein one of the flange rollers rolls off on a rolling surface formed by the protective structure or on a rolling surfacesupported by the protective structure.

The situation presented, in which an outer part of the body has to be connected to an inner part by hemming, arises for example in the case of wheel arches of vehicle bodies. The outer shell of the body has a circular arced, preferablysemi-circular section, on the rim of which the so-called wheel arch is fastened on the inner side of the body. The problem here is that the outer side of the outer shell should not be deformed or at least deformed as little as possible, i.e. must notfor example receive any dents or scratches, since these would be immediately visible when the outer shell is subsequently painted, and would spoil the aesthetic effect which the vehicle body is intended to impart.

In principle, this therefore prohibits using hemming device comprising pressing and counter pressure rollers, since the counter pressure roller would then run along the outer side of the outer shell and could deform it. The solutions knownhitherto get by using sliders which are moved radially outwards behind the rim of the outer shell, with respect to the wheel section, and thus turn it inwards. Since a counter pressure is omitted here, the quality of the hem is not always satisfactory. Moreover, this is relatively involved equipment which only caters specifically for the body of one type of vehicle in each case, which makes using it in production facilities in which different types of body are built problematic.

The invention relates to a flange device for roll-flange a rim of a component or other work piece along a flange edge, and to a flange method. The flange device preferably forms a hemming device for producing a hem connection. Thecomponent is preferably a body part, as such or already assembled. The invention is then particularly advantageous if the body part forms a viewed area, for example an outer part of the body, in the subsequent finished product, preferably a vehicle.

The invention preferably relates to a device for hemming the rim of a first body part which preferably forms an outer side of a body, wherein the rim of a second body part which for example forms an inner part of the body lies in the hem slot ofthe first body part. The device comprises a flange head with at least one counter pressure roller supported on the outer side of the first body part and preferably at least two pressing rollers which oppose the counter pressure roller or each opposeone counter pressure roller, for successively turning over the rim of the first body part.

It is an object of the invention to turn over the rim of a component, preferably vehicle a body part and in particular an outer metal sheet, using simple means, such that the component is not deformed. The device should also be configured suchthat it can be quickly adapted to different component shapes.

The invention relates to a flange device comprising a flange head, at least one first flange roller and at least one second flange roller which are each pivoted by the flange head. In the case of roll-flange, the first flangeroller forms a pressing roller which rolls off on a rim to be beaded, preferably a narrow rim strip of the component. The second flange roller acts as a counter pressure roller for the first flange roller, i.e. it takes up the force to be applied bythe first flange roller in order to bead the rim strip by for example 30° or 45°. In accordance with their respective function, the first flange roller is referred to below as the pressing roller and the second flange roller isreferred to below as the counter pressure roller. The flange head can in particular be fastened to one end of a robot arm which preferably exhibits all six degrees of freedom of movement, but at least exhibits the degrees of freedom required for theflange process itself.

In accordance with the invention, the flange device further includes a stable protective structure which can be fastened to the component or is fastened during roll-flange. For the counter pressure roller, the protective structure eitherforms a rolling surface itself, on which the counter pressure roller rolls off during roll-flange, or it only forms the rolling surface indirectly, by supporting a rolling surface on which the counter pressure roller directly rolls off. In the firstcase, an inner side of the protective structure abuts the component and is preferably shaped so as to be adapted to its surface. An outer side of the protective structure forms the rolling surface for the counter pressure roller. In the second case,the protective structure is arranged in the inner region of the flange edge to be formed and abuts the inner side of the component, wherein the protective structure is preferably shaped so as to be adapted to the surface of the inner side. Because itis supported on the inner side, the component can itself form the rolling surface for the counter pressure roller in the second case and is nonetheless not deformed by the pressing counter pressure roller, or far less than without the support on theinner side.

If the protective structure forms the rolling surface itself, the counter pressure roller does not roll off directly on the component, but on the protective structure which preferably forms a sort of matrix which is adapted to the inner side ofthe outer contour of the component, such that even the smallest spatial configurations of the component can be exactly copied and deformations need not be feared. The flange head itself can be a standard type which can also be used for other flangeprocesses. Above all, this has the advantage that a number of different bodies can be processed for example on a production line for vehicle bodies, preferably automobile bodies. It is merely necessary to retain respectively adapted protectivestructures which can be initially placed onto the body or inserted in the inner region of the flange edge, before the flange process is started.

In preferred embodiments, the area of the protective structure with which the protective structure abuts the area to be protected is shaped so as to conform to said abutting area of the component, such that the protective structure and thecomponent abut full-face.

The bodies and the protective structure preferably each have at least one marker which allows the protective strip to be placed in an exact fit on the rim to be flanged over. The at least one marker on the body can be a contour or edge which isinherently predefined, such as sections for doors, beams or the like. At least one hole can also be specifically introduced. In preferred embodiments, the protective structure possesses a centring element, preferably a positioning pin, and at least onestopper element which is used as a contour abutment. Alternatively, the protective structure can also be provided with just two centring elements, preferably positioning pins, or with just two stopper elements. Using such pairs of positioning meanswhich co-operate with corresponding positioning means of the component or--in the assumed example--with the body, the protective structure is exactly positioned relative to the flange edge when it abuts the abutting area of the component. In thealternative embodiment, in which the protective structure is arranged in the inner region of the flange edge, a single positioning element--preferably a stopper element--can be sufficient for positioning.

In one development, the flange head mounts a third flange roller which forms another counter pressure roller for at least one of the first flange roller and the second flange roller in a flange process. A closed flow of force may beobtained by means of such a third flange roller. Such an embodiment is particularly advantageous for a protective structure arranged in the inner region of the flange edge. The third flange roller, acting as a suppressor, can also serve to fastenthe protective structure. Thus, in particular in a protective structure arranged in the inner region of the flange edge, an additional fastening can even be completely omitted. In principle, this also applies to a protective structure abutting on theoutside.

In another development, a sensing element is fastened to or formed on the flange head, preferably pivoted as a sensing roller, in addition to the at least two flange rollers, and the protective structure forms a guiding path for the sensingelement, preferably another rolling surface, which follows the course of the flange edge. The sensing element, which is guided on the guiding path along the flange edge in a flange process, in turn guides the flange head, enabling theexpenditure which has to be made for controlling the movements of the flange head, in particular the measuring expenditure, to be reduced. For roll-flange along the flange edge, it is in principle even possible to completely omit controlling orregulating on the basis of positional signals obtained by measurement. If the flange head is guided along the flange edge by means of a sensing element, by guiding the guiding element on a guiding cam which is preferably formed by the protectivestrip but could in principle for example also be formed by the flange edge itself, the flange head is preferably mounted such that it can move back and forth in a direction pointing at least substantially normally with respect to the guiding path,preferably against an elastic restoring force. The elastic restoring force can expediently be a pneumatic force.

Advantageously, a sensor, preferably a distance sensor, is provided. The sensor is preferably mounted on the flange head or a platform to which the flange head is fastened. By means of the sensor the distance between the flange head andthe component or the protective structure can be ascertained. The sensing element can be replaced by a distance sensor which operates without contact, by moving the distance sensor along the guiding path described with respect to the sensing elementduring roll-flange, constantly measuring the distance without contact, and using the readings to regulate the movement of the flange head. A 1D sensor is sufficient as the distance sensor.

In developments, a two-dimensional sensor is provided which operates without contact, i.e. a 2D sensor using which the position of the flange head relative to the component, in particular its flange edge, can be ascertained in a plane of viewonto the component. The 2D sensor is preferably mounted on the flange head or a platform to which the flange head is fastened. In the preferred application--roll-flange on a body part--the plane of view extends in the XZ plane of the usualco-ordinate system of vehicle bodies. This sensor system is only required, and in advantageous method embodiments also only used, to place the flange head for roll-flange on the flange edge. If a mechanical sensing element or the distance sensorcited is not provided, the 2D sensor or another substitute sensor system, for example two 1D sensors, can also be used to regulate the movements of the flange head during roll-flange. Preferably, however, the 2D sensor system is provided in additionto the sensing element or distance sensor cited. Sensing and regulating in the XZ plane is particularly advantageous for hemming a so-called drop flange.

If, however, it may be assumed that the components to be flange always assume the positionprovided for roll-flange with sufficient accuracy, and are themselves always shaped with sufficient accuracy, then a 2D sensor system can be omitted, since in this case, it is possible to rely on the fact that it is sufficient if the flange headmoves to a predefined position, for example a pre-programmed position. In the circumstances cited, the sensing element and the distance sensor can also be omitted.

Flange lubricator attachment to a composite brake shoe

A device for lubricating a flange portion of a railroad wheel attachable to a composition brake shoe. The device comprises at least one lubricating member formed from a polymer based compound selected from the group consisting of phenolic resins, epoxy resins, polyamides, polytetrafluoroethenes, and various combinations thereof. The lubricating member has a substantially flat first side engageable with a longitudinal flat surface of such composition brake shoe and a radially opposed second side that has a substantially flat portion for contacting such flange portion of such railroad wheel. The device further includes a means for attaching the lubricating member or members to such composition brake shoe.

Many railroad locomotives and cars use wheel tread braking which provides the braking effort required by forcing a brake shoe formed with a friction composition material against the tread of the steel wheel. Brake shoe engagement with the wheel tread produces friction that dissipates the energy of momentum in the form of heat. In order for such braking to be effective, however, wheel rotation is required. The adhesion due to the friction between the wheel tread and rail tends to maintain such wheel rotation as the brake shoe engages the wheel tread during a braking operation.

Excessive wheel wear and brake shoe change outs have been found to be cyclically high during the winter season. One theory attributes this, at least in part, to the more pronounced cleaning effect that the brake shoe has on the wheel as the result of higher moisture contact during wintertime. In that such cleaning action tends to increase the contact friction; or adhesion between the wheel and rail, increased contact stresses are created in the wheel. Such contact stresses being especially high during the guiding and steering action of the wheel set, particularly, when encountering track curvature. Similar problems of wear are also a concern with the flange portion of the wheel. These stresses can be reduced with lubrication.

Wayside lubricators have been a part of railroading for many years. These are placed in curved territory to reduce wheel and flange wear particularly where the wear is the greatest on the curved portions of the track. Emphasis has shifted in recent years to on board lubricators which are locomotive mounted units that are designed to provide lubrication on tangent track as well as in the curved territory in an effort both to reduce wear and also to improve fuel consumption.

Thus, the railroad industry is constantly trying to find methods and/or equipment that can be used to reduce the wear that occurs on both the wheel surface that contacts the rail and also the flange portion and at the same time possibly decrease fuel consumption by providing improved lubricity.

The present invention provides a device for lubricating a flange portion of a railroad wheel attachable to a composition brake shoe. The device comprises at least one lubricating member formed from a polymer based compound selected from the group consisting of phenolic resins, epoxy resins, polyamides, polytetrafluoroethenes, and various combinations thereof. The at least one lubricating member has a first predetermined shape, wherein the first predetermined shape has a substantially flat first side engageable with a longitudinal flat surface of such composition brake shoe and a radially opposed second side that has a substantially flat portion for contacting such flange portion of such railroad wheel and a substantially arcuate portion for contacting the arcuate interface of such flange portion and a tread portion of such railroad wheel. The device further includes a means for attaching the lubricating member or members to such composition brake shoe.

In another embodiment of the invention a device is in combination with a brake block of a railway vehicle having a backing plate and a brake lining affixed to said backing plate and further having a braking surface engageable with a wheel tread of a wheel of such railway vehicle, said brake lining formed from a predetermined composition material. The improvement comprises the device for lubricating a flange portion of such railroad wheel. The device is attachable to the brake lining of such brake block. The device comprises at least one lubricating member formed from a polymer based compound selected from the group consisting of phenolic resins, epoxy resins, polyamides, polytetrafluoroethenes, and various combinations thereof.

The at least one lubricating member has a first predetermined shape, wherein the first predetermined shape has a substantially flat first side engageable with a longitudinal flat surface of such composition brake shoe and a radially opposed second side that has a substantially flat portion for contacting such flange portion of such railroad wheel and a substantially arcuate portion for contacting the arcuate interface of such flange portion and a tread portion of such railroad wheel. The device further includes a means for attaching the lubricating member or members to such composition brake shoe.

Such lubricating member 20 when attached to the brake lining 6 will provide lubrication for the flange portion of the railroad wheel by transferring solid lubricant to the flange as wheel rotates and the flange comes in contact with the lubricating member 20. After the lubricating member has been worn away to the point where it no longer contacts the flange it can be discarded and replaced with a new lubricating member.

The main use of this flange lubricator is to transfer the polymer based compound onto the flange and vicinity of the flange of a railroad wheel used by all types of railway rolling stock. The deposit of the polymer compound alters the friction between the flange of the railway wheel and the rail, especially at track curvatures. The polymer based compound deposited on the flange will substantially minimize flange wear.

Hydraulic Flanged Tube and Four-Bolt Split Flange Type

Scope--This SAE Standard covers complete general and dimensional specifications for the flanged heads and split flange clamp halves applicable to four-bolt split flange type tube, pipe, and hose connections with appropriate references to the O-ring seals and attaching components used in their assembly. (See Figures 1 and 2.) Also included are recommended port dimensions and port design considerations.

The flanged heads specified are incorporated into fittings having suitable means for attachment of tubes, pipes, or hoses to provide connection ends. These connections are intended for application in hydraulic systems, on industrial and commercial products, where it is desired to avoid the use of threaded connections.

THE RATED WORKING PRESSURE OF A HOSE ASSEMBLY COMPRISING SAE J518 HOSE CONNECTIONS AND SAE J517 HOSE SHALL NOT EXCEED THE LOWER OF THE TWO WORKING PRESSURE RATED VALUES.

Flanged heads shall be as specified in Figure 3 and Table 1. Split flange clamp halves shall be as specified in Figure 4 and Table 1. Port dimensions and spacing shall be as specified in Figure 5 and Table 2.

O-ring seals, having nominal dimensions as indicated in Table 1, are used in conjunction with these connections. They shall conform to the seals specified in SAE J120, Table on Dimensions and Tolerances.

Bolts for use with these connections shall be of the sizes and lengths indicated in Table 1. They shall be of SAE Grade 5 material or better as specified in SAE J429. Socket head cap screws of SAE Grade 5 material or better are acceptable.

Lock washers, if used, shall be in accordance with the light spring lock washers specified in SAE J489, Dimensions of Light, Medium, Heavy, Extra Heavy, and Hi Collar Spring Lock Washers, and of sizes applicable to the corresponding bolts.

The following general specifications supplement the dimensional data contained in Table 1 with respect to all unspecified detail.

This specification covers the pipe material and wall thickness applicable to lap joint flange pipe ends, manufactured by a mechanical forming process.

The lap joint flange connection has been widely used for low-pressure systems in the marine, process piping, and similar industries.

The values stated in SI units are to be regarded as the standard. The values given in parentheses are for information only.

This Standard covers the complete general, dimensional, mechanical, and performance data for metric prevailing-torque hex nuts and hex flange nuts of property classes 5, 9, and 10 as defined in ASTM A563M.

The inclusion of dimensional data in this Standard is not intended to imply that all of the nut sizes in conjunction with the various options described herein are stock items. Consumers should consult with suppliers concerning lists of stock production prevailing-torque hex and hex flange nuts.

Thickness Selection For The Flanges

ESDU 03013 presents a Fortran 77 computer program that calculates the thicknesses for the flange and webs of laminated composite I-section beams that are required to withstand or transmit given bending moments and shear forces.

The section is treated as “thin-walled” so that the top and bottom flange thicknesses and the web thickness are small compared with the overall beam width and depth. These overall dimensions are prescribed by the user, and the program provides efficient thicknesses for the flanges and web, for given bending moments and shear forces applied in the plane of the web, and for a specified flexural rigidity.

The sketch shows the various layers in the cross-section. It is noted that the laminates that make up the beam are all of the same unidirectional composite plies layed-up in 0° and/or +45° and –45° layers. It can be seen that the connection between the web and flange is made by continuing the web layers around to the inner faces of the flanges. Continuous ±45° layers are added to the outer flange faces as shown. These layers provide transverse strength to the flanges, and prevent the separated web layers from splitting at the top and bottom of the web. Because the web lay-up is constrained to be symmetric, this arrangement means that two of the flanges will have a symmetrical lay-up while the other two will be antisymmetric. It is, however, assumed in the analysis that all the flanges are symmetric and it is anticipated that any coupling terms that arise in the constitutive equations for the antisymmetric flanges will be small and can be neglected.

The loading on the beam is assumed to consist of given combinations of bending moment and shear force at the critical section of the beam along its span. The user provides values for the moments and shear forces for up to ten different load cases and the computer program calculates flange and web thicknesses for given overall beam section width and depth.

The analysis to obtain the layer thicknesses for the flanges and web of the I-section is controlled by a set of constraints that finally determine the detailed solution for the various stacking sequences. The constraints are as follows.

Allowable unidirectional layer strains in tension, compression and shear.

Buckling constraints for flanges and web.

Satisfaction of a minimum stipulated value for the overall flexural rigidity of the beam.

The user is required to provide the overall beam dimensions and loading, and the mechanical properties for a single unidirectional fibre-reinforced material. With this information a rough estimate for the flange and web thicknesses is obtained by assuming a uniform shear load in the web and uniform end-loads in the flanges. The procedure is known as “initial sizing”, and takes into account web and flange buckling and fibre failure. At this stage the top and bottom flanges have the same thickness.

Having obtained a rough first estimate for the design, the various thicknesses are then adjusted using a more precise direct and shear load distribution across the section and more precise equations for flange and web buckling. The ensuing reserve factors are utilized to adapt thicknesses to satisfy the constraints. This re-design procedure thickens or thins layers according to certain rules that are based on expectations of how the layers will best reinforce the beam. These are referred to as heuristic design rules and allow for failure due to excessive strains, flange and web buckling, and low flexural rigidity.

The design procedure is iterative, and is terminated when the minimum reserve factor is between 0.99 and 1.05 inclusive, indicating that any one layer just reaches one of the allowable strain values of the material, or that buckling is about to occur, or that the minimum required overall flexural rigidity of the beam is about to be reached. No other optimisation is performed and it is not possible to ensure that all of the above conditions are met at the same time because of the complicated interaction between them when the thicknesses are changed. However, the procedure guarantees that the associated reserve factors are all greater than or equal to 0.99 and the final design will generally be an efficient solution to the problem.

The analysis provides two sets of thicknesses, one in which the top and bottom flange thicknesses are constrained to be equal, denoted Configuration 1, and the other where these thicknesses are determined independently and may be unequal, denoted Configuration 2.

For all runs the program outputs a standard header which is followed by an echo of the input data. The quantity of additional information provided in the output for successful computations is determined by the value assigned to the output specifier in the input.

For brief output, the echo of the input data is followed by a table which presents all relevant results for the design. The results include the thicknesses, number of layers, the final cross-sectional areas, together with the minimum reserve factors. This is supplemented with the number of iterations in which the computations reached a converged solution, or not, an abbreviated description of the failure mode and the load case number for which the minimum reserve factor was obtained.

For extensive output, the brief output described above is preceded by a listing of the initial design thicknesses and tables that contain detailed data generated by the program for each iteration step for both Configurations 1 and 2. The tables present the evolution of the thicknesses of the flange and web and, separately, the associated values of the reserve factors.

What Is a Wheel Flange?

A wheel flange is a round flat adapter hub that allows a wheel to be attached to an axle on a vehicle. The wheel is held tight to a wheel flange with nuts that thread onto lug bolts protruding from the mounting face of the flange. The lugs then protrude through tapered holes in the wheel as it is mounted to the flange. The nuts, being tapered themselves where they contact the wheel, serve to precisely center and lock the wheel. Wheel flanges and lug nuts are the customary mounting method for wheels on all motor vehicles.

In the case of drive wheels on motor vehicles, wheel flanges are mechanically locked to one end of the drive axles or spindles. Spindles are short axles that are specific to only one wheel, on one side of the vehicle, while an axle can, and usually does, involve more than one wheel, and both sides of the vehicle. The other end of the axle is connected to or is part of the drive line of the motor vehicle. This is either through a series of gears, belts, chains, or shafts. With driving wheels, the bearings that resolve the rotary motion of the wheel to the vehicle are between the vehicle and the axle.

Free spinning wheels that do not drive a vehicle usually have their wheel bearings located between the wheel flange and the axle. The axles do not turn, but the wheels and wheel flanges as one assembly turn on them. Most trailers, such as boat trailers or truck trailers, use free spinning wheels. Wheel flanges also function as universal mounting adapters, in that they allow the same type of tire and wheel to be used for either driving or free spinning positions. They will also work with a variety of vehicle strategies, except where proprietary wheel flange designs, such as between car makers, restrict this freedom.

Modern braking systems place an individual disk or drum brake at each wheel of the vehicle to provide the best stopping performance. Many brake drums or disks are sandwiched between wheel flange and the wheel, and held tightly between them when the lug nuts are tightened. The stopping torque of the brake is transferred to the wheel through the circle of lugs. Other motor vehicle manufacturers integrate the wheel flange function into the brake disc. This allows either a drive spline or bearing hub to complete the final assembly and define the ultimate application as either a driving or free spinning wheel, respectively.

In a different context, a wheel flange can also refer to the beveled flat surfaces on the inboard side of train wheels that keep each axle centered on railroad tracks. The flanges contact the inner surface of each track. The flange on the right wheel would keep the train car from sliding to the right, and the flange on the left wheel would keep the train from sliding to the left. Similarly, wheel flanges can keep wheeled conveyors in industrial plants on their respective rails as they course their way through many turns around a building.

Ring seal with overlapping flanges for contaminant trapping

A flange is provided in the first member, projecting radially inward into the annular recess, thus forming an annular channel in the first member. An opening is provided, opening from the lowest point in the channel of the first member to the outer surface.

The first member is fixedly attachable to the housing so as to allow for free rotation of the shaft within the first member. A second ring member is positioned axially internal to the first member and is provided with an outer annular surface facing the inner surface of the first member and an inner annular surface facing internally of the housing.

The second member is fixedly attachable to the shaft and is provided with a flange which extends into the recess of the first member. A seal is thus provided which traps contaminants in the channel of the first member, allowing them to flow back to the atmosphere through the opening in the first member, whether the shaft is rotating or in a static position.

Many industries require the use of machines in which a rotatable shaft is contained by a housing. The housing usually contains lubricated bearings and sometimes additional attachments to the shaft such as turbine blades or gears. There are manytypes of seals provided between a shaft and a housing so as to prevent the leakage of lubricants from the housing and/or to prevent external contaminants from entering the housing along the shaft. In high speed operations of such rotating shaftmechanisms, contaminants to the internal lubricant result in increased wear, costly replacement of parts and, consequently, down time for the mechanism.

It is known to provide a sealing ring assembly comprising a first ring fixed to the housing and a second ring exterior to the housing and fixed to rotate with the shaft. Such an assembly is disclosed by U.S. Pat. No. 4,002,479, invented byDavid C. Orlowski and issued on May 10, 1977. In Orlowski, the first ring is held fixed to the housing by an o-ring and has an annular recess which matingly receives an annular flange of the rotating second member so as to allow free rotation withoutcontact between the flange and the recess. The contaminants are theoretically discharged through an opening in the bottom of the recess in the first ring. The second ring is secured to the shaft by an o-ring. This arrangement has failed to preventcertain contaminants from entering the housing.

An example of such a problem arises in the steam turbine industry, where such a seal is subject to an environment of steam, itself a contaminant, and also particles carried in the steam. In such anenvironment, steam easily penetrates the crevices between the first and second rings, condenses and is carried into the housing along the rotating shaft. An even greater contamination problem is created when the shaft is at rest and contaminants areallowed to build up and travel along the surfaces of the static rings to the static shaft which provides less frictional resistance to the contaminants than a moving shaft. A further problem arises when the o-rings or the sealing rings must be changed,which requires extensive down time while other components are removed in order to allow the sealing rings to be removed from the shaft.

Considering the above, it is an object of this invention to provide a ring seal between a housing and a rotatable shaft which prevents external contaminants such as steam from entering the housing, whether the shaft is rotating or static.

Accordingly, a ring seal between a housing and a rotatable shaft is provided, comprising a plurality of ring members generally concentric with the shaft. A first ring member is fixedly and sealingly attachable within the housing and has an outerannular surface facing externally of the housing and an inner annular surface facing internally of the housing. A second ring member is positioned axially internal to the first member and is provided with an outer annular surface facing the innersurface of the first member and an inner annular surface facing internally of the housing. The second member is fixedly and sealingly attachable to the shaft so as to rotate relative to the fixed positon of the first ring member.

The first ring memberhas an annular recess in its inner surface which receives an annular flange formed on the outer surface of the second member. A flange in the recess of the first member also forms a channel through which captured contaminants flow downward to an exitopening provided in the first member. The first and second ring members can be spilt so as to facilitate easy installation and removal. A third ring member is then provided which locks the second ring member into position and holds that positionrelative to the shaft and the first member.

Floor saver toilet flange

A toilet leak containment assembly for preventing water leaks from a toilet flange during flushing onto the support flooring into which the toilet is attached. The leak containment assembly contains a leak collector for installation between the toilet base and the support flooring for preventing the water leaks onto the support flooring during flushing.

The leak collector contains an attachment flange for attaching the leak collector to the support flooring, a collector pan for collecting water leaks during flushing, and an outlet pipe in fluid communication with the collector pan for channeling the leaks into the plumbing drain pipe. It also contains a leak seal assembly for installation and sealing between the toilet base and the leak collector. The leak seal assembly contains a flow channel for channeling water flow into the outlet pipe of the leak collector, and a seal for sealing between the toilet base and the leak collector.

A leak seal assembly for preventing water leaks from a toilet during flushing on to the support flooring to which the toilet is attached, the toilet including a toilet base mounted to the support flooring having an interior toilet passagethrough which water flows into a plumbing drain pipe during flushing; said assembly comprising: an annular flow channel for location between the toilet base and the drain pipe to channel water flow into the plumbing drain pipe; an annular flangesurrounding said flow channel, said annular flange includes an annular flat surface extending to an inclined annular surface for directing water into said flow channel, whereby, water leaks are directed into the annular flow channel for channeling waterflow into the plumbing drain pipe; a seal surrounding said annular flow channel for sealing between the toilet base and the plumbing drain pipe; and said annular flange overlying at least a portion of said seal.

One of the most common and more frustrating home repairs that needs to be made is the replacing of a rotted floor underneath a toilet caused by leakage over time. With the existing toilets and pipes, it is a foregone conclusion that, over time,some leakage will occur when a toilet flushes. The amount of water that does not go directly into the pipe should be forced down into the pipe over time and not be allowed to make contact with the floor or sub-floor where it can rot the floor and causesubstantial damage.

Traditionally, a toilet flange is placed in the sub-floor that receives the toilet bowl itself and the plumbing pipe and connects the two. These traditional flanges have four large areas for the placement of screws connecting the toilet to thetoilet flange and four additional screws for mounting the flange to the sub-floor. The holes that are used for the screws that connect the toilet to the flange allow for much exposed sub-floor upon proper installation of the toilet. The solution forfilling these holes so that no water reaches the sub-floor was the creation of a wax seal.

The wax seal consists of a plastic insert that connects the toilet with the toilet flange enclosed in a wax seal. Under the pressure of the toilet upon placingthe wax seal in between the toilet and the flange, the wax seal is pressed downward and fills in any holes on the toilet flange and surrounds the base of the toilet. The wax seal provides three benefits, first it protects leakage from reaching thesub-floor by filling the holes, and second it does not allow any gas to escape, and, through it directs water flow to the main drain pipe.

While this system works initially, over time it begins to fail and allows water to reach the sub-floor. As the years and seasons progress, the alternating hot and cold weather expands and contracts the wax seal, thus leaving gaps in the holesthe seal had once filled on the toilet flange. By leaving these areas exposed, the water from any leakage may now seep into these holes and begin to damage the sub-floor.

Therefore, it is an object of the present invention to provide a floor flange that protects the sub-floor and floor from water seepage.

It is a further object of the invention to provide a seal assembly for use in combination with the flange that will further protect from any water seepage and use the seal primarily as a blocker of gas and not a protector from water damage.

Wide Flange Threaded Plugs suit paint masking applications

Wide flange threaded plugs are manufactured with nylon material, which absorbs paint, while wide flange keeps paint flakes away from hole during removal. Nitrile gasket seals plug to mating surface for liquid tight seal. Applied or removed by hand, screwdriver, or torque wrench, units can be used in intermittent temperatures up to 230°F.

Erie, PA - Alliance Plastics is pleased to add the wide flange threaded plugs to their product offering. The design of the product is superior for paint masking applications because paint flaking is kept to a minimum due to the material and engineering of the product. While the nylon material absorbs paint, thus keeping paint flaking to a minimum, the wide flange design keeps any possible flakes away from the hole during removal. The nitrile gasket seals the plug to the mating surface for a liquid tight seal. These plugs can be applied or removed by hand, screwdriver or with a torque wrench. This part is recommended for intermittent temperatures up to 230°F (110°C).

About Alliance Plastics

Alliance Plastics is a manufacturer and distributor of protection and finishing components for a wide range of industries and applications. Alliance Plastics operates predominantly in the United States, Canada, Mexico and Brazil but has a global presence through distribution in Europe and Asia.

Formed in 1968, Alliance Plastics employs more than 200 people in 10 locations throughout North and South America. The company's headquarters and primary manufacturing site are located in Erie, Pennsylvania, where significant investment in information technology, production machinery, tooling, and warehouse facilities drive ongoing improvements in customer service. Additional manufacturing operations were incorporated into existing distribution operations at the Sao Paulo, Brazil site in 2006. This site anchors the company's presence in the region.

Alliance Plastics is pleased to announce their new line of flange protector retainer plugs. These black PVC plugs are used to secure matching bolt hole flange protectors. Alliance Plastics carries a full range of sizes varying from 5/8" to 1-3/4" and are a nice addition to our ever increasing Pipe & Flange Protection product line.

Hydrodynamic bearings are designed for use in large electrical generators and motors, turbines, compressors, and pumps. Thin layer of pressurized lubricant is used between bearing surfaces, so there is no metal-to-metal contact and no maintenance required. Bearing assemblies are offered in pedestal, mid-flange, and end-flange configurations and bearing shaft sizes from 55-1,400 mm and frame sizes 7-112 are available.

GGB Bearing Technology, formerly Glacier Garlock Bearings, today introduced a line of fluid film bearings to complement its extensive plain bearing offerings. Designed primarily for use in large electrical generators and motors, turbines, compressors and pumps, these hydrodynamic bearings offer significant advantages over large roller bearings in high-load, high-speed applications.

Because they use a thin layer of pressurized lubricant between the bearing surfaces, there is no metal-to-metal contact, resulting in little to no maintenance and virtually infinite life. They also have an inherent dampening effect for quieter, smoother operation.

GGB will offer plain bearing assemblies in pedestal, mid-flange and end-flange configurations. Manufactured to the DIN/ISO standard, the bearings are available in shaft sizes from 55mm to 1,400mm and frame sizes 7-112. In addition GGB can provide custom designs for thrust blocks and radial/axial inserts.

Brennan Industries Introduces New Stainless Steel O-Ring Face Seal and Flange Adapters

Machined from round stock, flange adapters are hot-piercing bent for desired angle and do not have braze and weld points. Swept configurations enable performance in limited clearance applications and connection sizes range from ?-4 in. Operating in pressures as high as 6,000 psi, SS O-ring face seal fittings are designed to eliminate leaks in hydraulic systems on industrial/commercial equipment. They are available in 23 configurations and in 35 size combinations.

CLEVELAND - Brennan Industries Inc., a leading international supplier of hydraulic fittings and adapters, extends its stainless steel product offering by introducing new stainless steel O-ring face seal and flange adapters. Stainless steel offers a superior corrosion resistance and sealing for critical, harsh-duty applications.

"The new adapters are ideal in facilities alongside stainless steel instrumentation fittings and flareless bite-type fittings, as well as with other NPT and JIC products," said Bill Jarrell, vice president of marketing and procurement at Brennan Industries. "The new O-ring face seal and flange adapters are an important addition to our stainless steel offerings."

Machined from round stock, Brennan Industries flange adapters are hot-piercing bent for the desired angle and do not have braze and weld points. Swept configurations allow Brennan Industries flange adapters to perform in limited clearance application situations, while their construction enables them to endure extremely high working pressures and tensile strength. Brennan flange adapters range in connection sizes from 1/2 to 4 inches.

O-ring face seal fittings eliminate leaks in hydraulic systems, while permitting operating pressures as high as 6,000 psi. Developed for hydraulic systems on both industrial and commercial equipment, the product line is available in 23 different configurations, and in 35 different size combinations.

Brennan Industries' O-ring face seal fittings are designed specifically for applications where elastomeric seals are acceptable to overcome leakage and variations in assembly procedures. The fittings can easily be connected to a range of tubing grades by silver brazing. In addition, the fittings can easily be disassembled and reassembled.

About Brennan Industries

Supplying a wide range of industries throughout the world, Brennan Industries offers more than 25,000 standard and special hydraulic fittings and adapters in sizes ranging from 1/8 to 2 ? inches. These include a wide choice of fitting and adapter types such as tube, O-ring face seal, instrumentation, metric bite type, push-to-connect, conversion and flareless bite type. Brennan Industries also offers valves, clamps and swivels. Most products are available in carbon steel, stainless steel and brass, and meet or exceed J.I.C., S.A.E. and other specification.

Brennan flange products are stocked at six strategically located, full-service distribution centers in: Atlanta, Cleveland, Dallas, Los Angeles, Seattle and Toronto.

Camera with flange back adjusting mechanism

A camera includes a flange back adjusting mechanism in which the operation of the flange back adjusting mechanism is not obstructed, and the flange back adjustment is easily performed. A flange back adjusting mechanism which moves and adjusts a CCD in the direction of the optical axis can be operated by an operation section which protrudes to the outside of a case portion through an operation window. The operation window is opened in a side wall face of a camera chassis separating rearward from a lens mount portion along the direction of the optical axis and on a peripheral wall of a case portion of the camera chassis.

The illustrated camera with a flange back adjusting mechanism is disclosed in JP-B-7-8021, and includes: a camera chassis 5 having a lens mount portion 3 to which a lens is to be mounted and a case portion 4 which is rearward continuous to thelens mount portion 3; a device holder 9 which is supported by the camera chassis 5 so as to be movable in the vicinity of the imaging position of the lens mounted to the lens mount portion 3 and along the optical axis 7 of the lens; a CCD (charge-coupleddevice) 11 serving as a solid state imaging device which is held on the optical axis of the lens by the device holder 9 and which converts an incident optical signal into an electric signal and outputs the electric signal; and a flange back adjustingmechanism 13 which moves and adjusts the position of the device holder 9 in the direction of the optical axis of the lens.

In this example, the lens mount portion 3 is formed separately from the case portion 4. The lens mount portion 3 has a substantially cylindrical shape, and includes a front escutcheon 3a which is formed integrally with the periphery of the mountportion. Four corners of the escutcheon 3a are fastened to a front face of the case portion 4 by screw members 15, whereby the mount is coupled and fixed to the case portion 4.

The device holder 9 has a rectangular recess 9a into which the CCD 11 is fitted. The periphery of the CCD 11 which is fitted into the recess 9a is pressed by a device pressing plate 17 which is screwed to a front face of the device holder 9 inorder to attain a state where the CCD is fixed to the device holder 9.

The device holder 9 is fixed to a chassis attaching bracket 19 by screw members 18. The bracket 19 is supported so as to be movable in the direction of the optical axis of the lens between a front wall 4a of the case portion 4 and the lens mountportion 3. The bracket 19 is urged toward the lens mount portion 3 by springs 21 which are inserted in a compressed state between the bracket and the front wall 4a of the case portion 4.

In the flange back adjusting mechanism 13, a stopper portion 23a which butts against a front end portion of the bracket 19 that is urged by the springs 21 in order to perform positioning of the bracket 19 in the direction of the optical axis, anda cam portion 23b which gives a displacement of the lens in the direction of the optical axis are disposed on a cam ring 23 which is fitted onto an outer periphery of the lens mount portion 3.

In order to attain the object, the camera with a flange back adjusting mechanism of the invention is a camera with a flange back adjusting mechanism including: a camera chassis having a lens mount portion; a device holder which is supported bythe camera chassis to be movable in a vicinity of an imaging position of a lens and in a direction of an optical axis; a solid state imaging device which is held by the device holder; and a flange back adjusting mechanism which moves and adjusts thedevice holder in the direction of the optical axis,

wherein the flange back adjusting mechanism includes: a cam ring which is supported to be rotatable about the optical axis in the camera chassis and in which a cam surface is disposed in a peripheral edge portion, a projection length of the camsurface in the direction of the optical axis being gradually changed in a circumferential direction; a positioning protrusion which protrudes from the device holder, a tip end of the protrusion butting against the cam surface; a holder urging springwhich urges the device holder toward the cam ring to maintain a state where the positioning protrusion butts against the cam surface; an operation window which is opened in a side wall face of the camera chassis, the side wall face extending along thedirection of the optical axis; and a ring driving mechanism which rotates the cam ring by an operation section that protrudes to an outside through the operation window.

According to the configuration, the operation section of the flange back adjusting mechanism for moving the device holder is placed on the side wall face of the camera chassis which is rearward separated from the lens mount portion. Even when aninterchangeable lens of a large aperture is mounted to the lens mount portion, therefore, the operation section does not hide in a valley portion behind the interchangeable lens.

In the camera with a flange back adjusting mechanism, preferably, the ring driving mechanism is configured to rotate a driving gear which meshes with the cam ring by the operation section, and includes an elastic member which applies to thedriving gear a load that blocks rotation of the driving gear when a rotation operating force is equal to or smaller than a reference.

According to the configuration, the load which is applied to the driving gear by the elastic member exerts a braking function which prevents rattling of the driving gear and the operation section due to backlash in a gear train used in the flange back adjusting mechanism, from occurring, thereby preventing an error due to rattling from being produced in transmission of the operating force.

Flange Turning Process Machine

A spiral pipe has an integrated radial flange. A machine for forming such a flange comprises a rotor which rotates and a flange roller mechanism connected to the rotor via slides. As the rotor rotates, the flange roller mechanism moves radially via the slides to form an integrated flange on an end portion of the spiral pipe.

A flange turning machine for creating a flange on a spiral pipe, the machine comprising: a mandrel; jaws configured to hold the spiral pipe against the mandrel; arotor configured to rotate; a slide configured to move radially from a start position on the rotor to an end position on the rotor; a central shaft slide configured to move from a rearward position to a forward position; a slide moving arm configuredto move the slide from the start position to the end position as the central shaft slide moves from the rearward position to the forward position; and a flange turning roller mounted on the slide, and configured to create the flange by deforming an endportion of the spiral pipe against the jaws as the rotor rotates and the slide moves from the start position to the end position.

Spiral pipe is used in a variety of duct work applications. Spiral pipe is typically manufactured from galvanized steel, and is available in a wide variety of diameters, ranging from 3-inches to 80-inches. Similarly, spiral pipe is available ina wide wall thickness, ranging from 26-gauge up through 16-gauge. Lastly, spiral pipe may come in a variety of lengths, ranging from 1-foot to 20-feet, with 10-feet lengths being standard.

Spiral pipe is made by forming a coil of metal into a rigid steal tube with a four-ply spiral lock seam. Though it is common in the art to refer to this type of pipe as "spiral pipe" pipe, the seam of the pipe extends helically along the lengthof the pipe. Forming the spiral pipe in this way results in the pipe having a resistance to crushing approximately 21/2times that of a longitudinally box seamed or longitudinally welded pipe. In addition, the spiral pipe has a smooth interior for lowfriction loss because the grooved seam is entirely on the outside. This low friction loss inside the spiral pipe allows the air to flow smoothly or "tumble" down the tube, increasing the efficiency of air flow through the spiral pipe.

Pipe-to-pipe connections are typically made using a fitting size coupling that slips inside the mating pipe sections. A stop bead runs around the middle of the coupling to center the coupling between the two pipe sections. The coupling is thensecured by installing sheet metal screws through the outer shell of the duct a half inch from the stop bead. This method is time-consuming, increases the labor lost, and requires the tools and space necessary to allow the coupling to be attached to thespiral pipes. Further, the resulting connection created at the coupling may reduce the efficiency of the air flow through the spiral pipes. Specifically, the air does not flow efficiently through the pipes due to the coupling, the screws attaching thecoupling to the spiral pipes, and any imperfections in the fit between the coupling and the two lengths of spiral pipe.

As an alternative to a coupling inserted between two pipes, it is possible to fit two lengths of pipe together using a flange integrally formed on the end of each pipe. However, it has proven especially difficult to manufacture spiral pipehaving an integrated flange at the end of the spiral pipe. A major challenge in forming a flange at the end of a spiral pipe is the four-ply seam which extends helically along the length of the pipe. It is difficult to bend the four-ply seam area ofthe spiral pipe to form the flange without damaging the spiral pipe. Often, the spiral pipe will break or crimp when attempting to form a flange at the location of the four-ply spiral seam.

Thus, there is a need in the art for a spiral pipe having an integrated flange located at the end of the length of pipe. Similarly, there is a need in the art for a method of manufacturing a spiral pipe having an integrated flange.

The present invention is a spiral pipe formed with an integrated flange, as well as a machine for forming an integrated flange on the spiral pipe. The machine comprises a mandrel and four jaws for holding the spiral pipe against the mandrel. The machine further comprises a rotor plate which is configured to be rotated. Mounted on the rotor plate are three flange turning rollers. The flange turning rollers are connected to the rotor plate via slides. The slides are configured to allow theflange turning rollers to move from a first position to a second position as the rotor plate is rotating.

The flange turning rollers are positioned so that when the spiral pipe is placed on the mandrel, the flange turning rollers are located on the inner diameter of the spiral pipe. As the machine operates, and the flange turning rollers are movedvia the slides from their first position to their second position, the flange turning rollers move radially from the inner diameter of the spiral pipe to an outer diameter. As the flange turning rollers move from the inner diameter of the spiral pipe toan outer diameter, the spiral pipe is deformed against the jaws by the flange turning rollers. In this way, an integrated flange is formed on the spiral pipe.

Flanged valve connectors

A combination valve and flanged connector for connecting a metallic or non-metallic pipe directly to the valve body is disclosed. The flanged valve connector includes a radial flange secured on a longitudinal end of the valve body. Secured to the radial flange is a tubular member for receiving the end section of a pipe to be connected with the valve body.

The tubular member has a generally frusto conical end sized to snugly receive a sealing gasket in sealed relationship between the tubular member and the valve body. The tubular member also has a length sufficient to be engaged by a retainer for holding the sealed gasket in place and to also support a follower ring engaging the gasket retainer, the follower ring being provided with a deep, longitudinally extending strengthening flange.

In combination with a valve including a valve body having a longitudinal passageway therethrough, a closure element for said valve body intermediate its ends, operator means acting onsaid closure element to open and close the longitudinal passageway, a flanged valve connector comprising:radial flange means on said valve body on at least one of the longitudinal ends thereof for securing a bolt on compression coupling assembly to said valve body;an enlarged tubular member secured to said radial flange means and extending outwardly from said radial flange means and coaxial with said longitudinal passageway for receiving the end of pipe to be connected with said valve body;said tubular member having a generally frusto conical end opening outwardly and sized to snugly receive a sealing gasket in sealed relationship between said tubular member and a pipe to be connected with said valve body; and said tubular member having an axial length sufficient to be engaged by a gasket retainer having a cylindrical section sized to surround said sealing gasket and the end periphery of said tubular member and a radial section for snugly engaging saidsealing gasket arranged in union with said frusto conical end opening and to receive a follower ring having a deep longitudinal flange extending over the periperal length of said tubular member and engaging said gasket retainer, the follower ringfunctioning to secure the gasket retainer and gasket to said tubular member.

In the pipeline industry there has been a significant renewal of pipe particularly in gas transmission and distribution pipeline systems. In distribution systems cast iron and steel pipe is being replaced by plastic pipe. This replacement posesproblems both in the tie-in connection of the plastic pipe to the metallic pipe as well as in the installation of valves in the renewed pipeline. Where plastic pipe is connected to metallic pipe the connection may be with a mechanical bolt type couplingor with a special steel-to-plastic pipe transition fitting which is welded directly to both the steel and plastic piping.

If a steel valve was necessary at the tie-in connection or elsewhere in a plastic pipeline, it was necessary prior to this invention, to use a stub end valve and to first extend the stub end by welding a short length of steel pipe, or what isknown as a "pup", to each end. This was done in order for the valve ends to accept the installation of mechanical bolt-on type couplings. The valve was then installed into the pipeline by connecting one extended stub end to the metallic pipe with ametallic bolt-on type coupling and connecting the opposite extended stub end to the plastic pipeline with a mechanical bolt-on type coupling.

An alternative valve installation used when steel pipe and plastic pipe were involved, is to use a stub endvalve and to weld one stub end directly to the steel pipeline and to weld the special steel-to-plastic transition fitting to the opposite valve stub end and then to weld the fitting to the plastic pipeline. So far as is known, there has not beenprovided a valve structure which would solve this problem of connecting pipelines of dissimilar or incompatible material and also act to provide valving for the line.

My invention overcomes the aforementioned problems by providing a valve and connector structure which may be attached to the free end of a plastic pipeline or a metallic pipleine to both seal and hold the plastic or metallic pipe to the valvebody, and also to allow the other side of the valve to be welded to a metallic pipe line in the usual fashion.

It should now be clearly understood how the flange valve connector of this invention provides the advantage of a simple and inexpensive manner of connecting pipelines to the valve body forming part of my invention. My flange valve connectoreliminates the need of welding additional elements to the valve body and reduces the number of parts for connecting pipe to the valve body. Also, it should be readily apparent to those skilled in this art that the socket construction of my connector inits simplicity may be modified in structure to accommodate other particular type connector features without deviating from the scope of the invention.

Mounting Flange Allowing Simplified Rotor Removal and Replacement

A hub rotor assembly includes a hub, a rotor supported by the hub and a plurality of fasteners that connect the rotor to the hub. The hub includes a wheel mounting flange and rotor mounting flange to which a flange of the rotor is attached.

The rotor mounting flange has a larger diameter than the wheel mounting flange, or other hub elements outboard of the rotor mounting flange, so that the rotor can be easily removed from the hub. Features of the invention also include floatation elements associated with a fastener to fasten the rotor to the hub while allowing the rotor to move or float relative to the hub. A spring clip may be used with the floatation elements to prevent the rotor from rattling. The assembly is particularly suited for commercial highway vehicles and high performance vehicles.

A plurality of floatation elements connecting the rotor to the hub, the plurality of floatation elements being fixed with respect to the other of the hub and the rotor, each floatation element including a portion being disposed at least partially within one of the slots, the portion of each floatation element being disposed within one of the slots including a non-circular cross section, each floatation element being sized in relation to the slot within which it is disposed to allow at least one of radial, axial, or rotational relative movement between the floatation element and the slot, the relative movement between each floatation element and the slot within which it is disposed permitting relative movement between the rotor and the hub with respect to the central axis where in each of the plurality of floatation elements comprises a bobbin and a bolt used in association with each bobbin, the bolt being connected to the bobbin to connect the rotor to the hub.

The hub rotor assembly of claim 1, wherein the rotor has a mounting flange with an inner diameter, and the hub has a mounting flange, wherein the rotor mounting flange and the hub mounting flange overlap so that the floatation elements extend through the mounting flanges to connect the rotor to the hub.

Hat rotor hubs have a hat rotor that is detachable from a hub. These hat rotors are typically one piece metal castings having a rotor portion integrally cast with a hat portion. The hat portion of the hat rotor is a large flange that fits over a mounting surface of the hub. The hat portion includes wheel stud apertures through which wheel studs can pass. The hat rotor is loosely mounted on the hub until a wheel is subsequently mounted on the hub. As wheel lug nuts are tightened to the wheel studs, the hat rotor is sandwiched between the wheel and the hub, thus securing the hat rotor to the hub.

Another aspect of embodiments of the invention is to provide a hub and rotor where the rotor mounts to the hub independent of the wheel. Specifically, an aspect of embodiments of the invention is to provide a hub having a rotor mounting flange and a rotor which is mounted to a rotor mounting flange. The independent mounting of the rotor and a wheel to the hub rotor assembly of the present invention ensures that the rotor run-out will be unlikely to result from unevenly tightened lug nuts or an improperly manufactured wheel.

Also as a result of the independent mounting of the rotor and the wheel, wheel removal does not affect the mounting of the rotor to the hub. Consequently, upon removal of the wheel from the hub there is no potential for debris or other extraneous matter to become lodged between the rotor and the hub, causing rotor run-out.

Another aspect of embodiments of the invention is to provide a rotor design having simplified manufacturing compared to hat rotor hubs and integral rotor hubs. Specifically, an aspect of embodiments of the invention is to provide a hub having a rotor mounting flange and a rotor, which is mounted to the rotor mounting flange. This hub and rotor configuration provides a rotor that is as easily removable from the hub as a hat rotor, but does not have the deficiencies of a hat rotor. And, as there is no hat portion on the rotor, different rotors do not vary considerably in shape from one another. Consequently, unlike hat rotors and integral rotor hubs, a large number of rotors may be machined from a single rough casting. Tooling and manufacturing costs are greatly decreased as a result of this design. Additionally, as the rotor and the hub are manufactured separately, the hub and rotor can have different material specifications for optimal cost and performance.