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.