Pipe coupling flow controller

Abstract: A flow controller in the form of segmented pipe coupling comprises e.g. a butterfly valve (14), and preferably has opposing coupling segments (10,12) provided with oppositely angled end faces (44,46) of saw tooth configuration at the respective ends of the coupling segments, thus allowing the inclined end faces to emerge at the axial end faces of the coupling at or closely adjacent to the X-Z plane of an axially long coupling. A slow motion rotary drive (54) for the butterfly valve (14) is also provided.

Description: Field of the Invention This invention relates to a segmented pipe coupling flow controller assembly assembled from coupling segments. Optionally, the coupling provides a "rigid" pipe coupling in the fully assembled condition of the coupling, or, a flexible pipe coupling. A "rigid" pipe coupling is one in which the segments of the pipe coupling are capable of moving relative to each other during tightening down of a coupling assembled from such coupling segments, to permit keys of the segments to come into rigid clamping engagement with grooves formed in the ends of pipes or the like. A "flexible" pipe coupling is one in which the end faces of the coupling segments engage each other prior to the coupling segments clamping down on the pipe exterior. This provides for limited movement of the pipe ends relative to each other. Throughout the discussion of this invention, reference is made to pipes, it being understood that one or other of the pipes, or both, can be provided by a nipple, a flanged coupling, or any other fitting incorporating a nipple construction. The invention finds particular utility in providing a segmented pipe coupling that incorporates a flow controller in the form of a butterfly valve, plug valve, ball valve or the like, as a sub-assembly insertable into the coupling segments prior to assembly of the pipe coupling. Background of the Invention A flow controller assembly according to the features defined in the preamble of claim 1 is known from FR-A-1581092. This teaches a pipe coupling comprising two pipe members, with inclined flanges and a groove at one end face of the pipe, a tubular rubber sleeve and two coupling segments. The rubber sleeve fits into the grooves of two mutually presented end faces of the pipes. The coupling segments are mounted on the rubber sleeve/pipe assembly with complementary grooves in the coupling segments fitting onto the inclined flanges of the pipes. Tightening of traction members in the coupling segments pushes the pipes together to form a sealing relationship with the rubber sleeve. Flow control means are provided by a valve within the coupling assembly made accessible via a spindle member extending through the rubber sleeve and a coupling segment. According to the invention we provide a flow controller assembly in the form of a segmented pipe coupling, comprising a complete flow-controller sub-assembly having a valve body, a valve seat provided within said valve body for cooperation with a rotatable valve member, a rotatable valve member supported within said body for rotation relative to said valve seat and into seating relation therewith, and means for rotating said valve member relative to said valve seat; at least two coupling segments arranged in encircling relation with said valve body, said coupling segments having keys for reception in grooves in the ends of pipes; and traction means for securing said coupling segments to each other in encircling relation with said pipe ends and said valve body; at least one of said couplings segments providing access to said valve member rotating means from a position exterior of that coupling segment characterised by a first gasket member axially separable from the valve body for forming a seal between the valve body and one pipe and a second separable gasket member also axially separable from the valve body, for forming a seal between the valve body and a second pipe at the opposite side of the valve body. It would also be desirable to provide such a flow-controller in which the respective coupling segments retain their ability to rotate about the Y-Y axis of that coupling segment, but, to only a determined angular extent in order to provide either a rigid pipe coupling, or, a flexible pipe coupling. A further, preferred, aim is to provide a flow-controller that is insertable into the respective coupling segments at the time they are assembled into the segmented pipe coupling in order to provide an in-coupling flow-controller, which preferably is in the form of a butterfly valve, but which equally well could be in the form of a plug valve or ball valve, a butterfly valve being a hybrid form or a plug valve. Other preferred aspects of the present invention are set out in the sub claims. A preferred segmented pipe coupling of the present invention comprises coupling segments each having an end face at the opposite ends thereof the respective end faces of the coupling segments being oppositely inclined with respect to the X,Z plane of that coupling segment. The respective end faces each are comprised of first and second end face portions each inclined in the same direction relative to the X,Z plane, and, a third end face portion extending between the adjacent edges of the first and second end face portions at an angle to said first and second end face portions to provide a saw tooth configuration of the respective end faces in the direction of the Z-Z axis but inclined relative thereto. The third end face portion can extend in the X,Y plane of the coupling segment, but preferably is arranged at an acute positive angle relative thereto. In this manner, a pair of coupling segments when assembled into a segmented coupling are capable of moving in opposite directions relative to each other during tightening down of the segmented pipe coupling about the Y-Y axis of the respective coupling segments. Movement of the ends of the coupling segments and rotation of the coupling segments about their respective Y-Y axis will proceed under the influence of forces exerted during the tightening down of the coupling segment. Those forces will include a camming action between the respective juxtaposed end face portions as the respective coupling segments move towards each other in the radial direction of the pipe, and will include various other forces produced by traction bolts employed for securing the ends of the coupling segments to each other as produced during the tightening down of those traction bolts. The extent to which the coupling segments can move about the Y-Y axis will depend on the accuracy of formation of the pipe groove itself. Pipes vary in external diameter within a determined range of manufacturing tolerances, and, unless the pipe groove is lathe turned, the actual diameter of the axial wall of the pipe groove also will vary in dependence on those manufacturing tolerances. As the grooving of pipe ends commonly is performed in the field as opposed to a workshop, which renders lathe turning impractical, the common manner of grooving pipe ends is by the use of a grooving tool that employs the external surface of the pipe as the reference for the radial position of the axial wall of the pipe groove. Thus, due to the manner of formation of the groove, the radius of the axial wall of the groove will vary in direct relation to the manufacturing tolerances in the pipe itself. This raises limitations on the extent to which the X,Y plane of the respective coupling segments can be brought into coincidence with the X,Y plane of the pipe. Coincidence can be obtained at only one diameter of pipe groove. However, unless the pipe groove is lathe turned, the diameter of the pipe groove cannot be guaranteed and will vary within the range of manufacturing tolerances. As the disparity between the minimum and the maximum range of manufacturing tolerances is quite small, in all instances, the coupling segments will be moved into very closely approximate coincidence of their respective X,Y planes upon tightening down of the coupling, the coincidence being so closely approximate that it is of little consequence in the finally assembled segmented pipe coupling. It is particularly desired to ensure that any divergence of the X,Y plane of the coupling segments from the X,Y plane of the pipe is maintained within a determined range and that the Y-Y axis of the respective coupling segment remain in the X,Y plane of the pipe. Typically the respective coupling segments are configured for them to receive and contain a sub-assembly including a flow-controller that can be rotated between an open and a closed position by means of an actuating shaft assembly extending though the aperture of one of the coupling segments, the shaft being journalled at its other end in a bearing assembly that is received in the aperture of the diametrically opposite coupling segment. For all but the largest sizes of segmented pipe couplings, the pipe coupling usually comprises two coupling segments that interfit to provide a complete coupling. For larger sizes of coupling, the coupling can comprise more than two coupling segments. In such a coupling comprised of multiple coupling segments, the coupling segments each can remain identical one with the other. However, in such a construction it is more practical to provide identical diametrically opposite coupling segments an intermediate coupling segments in which the apertures do not exist. The flow-controller is in the form of a complete sub-assembly comprised of a body adapted to be received within and securely held by the coupling segments. The interior of the body can be configured in any manner compatible with its intended function. In the case of a butterfly valve, the body will be provided with a central aperture in which the butterfly valve is positioned and rotatable about the axis of the actuating shaft. The central aperture can be appropriately configured to accept either a plug valve or a ball valve, and, for it to provide the required seatings for those valves. Conveniently, an actuating mechanism is provided for the valve, the actuating mechanism being connected to the valve sub-assembly exteriorly of the assembled coupling either prior to or subsequent to tightening down of the coupling. Also, the above-mentioned sealing members (formed e.g from an elastomeric material) may be provided internally of the assembled coupling, and cooperate both with the coupling segments and with the contained valve flow-controller as well as with the pipe ends. As will be appreciated, the addition of the flow-controller sub-assembly to the segmented coupling will result in an increase in the width of the coupling in the direction of the Z,Z axis. In the absence of the saw tooth formation of the end faces of the coupling segments, this would limit the couplings to large diameter couplings, for example, of 100 mm [4 inches] I.D. or more. This is due to the fact that a planar surface passing through the X,Y,Z center of the coupling and which is inclined to the X,Z plane will emerge from the end faces of the coupling at a distance from the X,Z plane that progressively increases as the Z-Z length of the coupling is increased. However, as the arcuate extent of the coupling segments cannot exceed 180° if they are to pass onto a pipe, those portions of the coupling segments that extend beyond the pipe diameter must be formed as perpendiculars to the X,Z plane including the pipe axis. On the other hand, the angle of the end faces relative to the X,Z plane is required to be larger than the critical angle of frictional repose, which usually is in the order of 20°. If a coupling of only 25 mm [one inch] I.D. is to be provided, then, the coupling would then have to be considerably less than 45 mm [1.75 inches] in the Z-Z length, and, of approximately only 12.5 mm [0.5 inch] in the Z-Z length if the plane of separation of the coupling segments is to emerge at an acceptable position on the end faces of the coupling segments in which it is closely proximate to the X,Z plane. An added advantage of the saw tooth formation of the end faces is that by "folding" those faces by providing dual end face portions and an intermediate portion inclined thereto, they can be caused to exit the coupling at any desired position on the end face of the coupling, including the diametral X,Z plane of the coupling. Further, the saw tooth formation of the end faces may give an additional advantage in correcting the orientation of the respective coupling segments as they are assembled onto a pipe. Initially, the required seals are assembled onto the pipe. Then, one of the coupling segments and the flow-control sub-assembly is assembled onto the pipe. The other of the coupling segments is then assembled onto the pipe, this involving passing the said other coupling segment over the seals and over the flow-control sub-assembly. If misalignment of the seals or of the flow-control sub-assembly has occurred, this will cause mis-orientation of the said other coupling segment acting to force the said other coupling segment out of the X,Y plane of the coupling. However, the intermediate third end face portions then act to move the said other coupling segment into its required orientation, and, in turn move the seals and the flow-control sub-assembly into correct orientation with respect to the X,Y plane of the coupling. Description of the Accompanying Drawings The invention will now be described with reference to the accompanying drawings which illustrates preferred embodiments thereof, and in which: Figure 1 is a front elevation of an assembled segmented pipe coupling with a flow-controller sub-assembly contained within the coupling; Figure 2 is a transverse cross-section taken on the line Z-Z of Figure 1; Figure 3 is a traverse cross-section corresponding with Figure 2 and showing the flow-controller sub-assembly alone; Figure 4 is a view corresponding with Figure 1 and showing the flow-controller sub-assembly alone; Figure 5 is a plan view of Figure 4; Figure 6 is a plan view of one of the coupling segments of Figure 1; Figure 7 is an underside plan view of the coupling segment of Figure 6; Figure 8 is an end elevation of the coupling segment of Figure 6; Figure 9 is a front elevation, partially in section, of the coupling section of Figure 6; Figure 10 is a cross-sectional view corresponding with Figure 2 showing the coupling segments in assembled condition, and, with the flow-controller sub-assembly removed; Figure 12 is a view corresponding with Figure 2, but showing a control mechanism attached to the flow-control sub-assembly; Figure 13 is a front elevation of a scroll cam incorporated into the control mechanism of Figure 11; Figure 14 is a plan view of the control mechanism of Figure 11 with a cover of that control removed; and, Figure 15 is a plan view of the control mechanism of Figure 11 with the cover in situ. Referring firstly to Figures 1 and 2, there is shown a complete segmented coupling for pipes in an assembled condition of the coupling, and, in the form it will be supplied for subsequent disassembly and assembly onto the grooved ends of the pipes (not shown). The segmented coupling is comprised of an upper coupling segment 10, a lower coupling segment 12, and a flow controller sub-assembly in the form of a butterfly valve which is indicated generally at 14. The respective coupling segments each are provided with keys 16 at their end faces for reception in grooves formed in the ends of pipes, the respective coupling segments being secured to each other by traction bolts 18 that are employed for tightening down the assembled coupling. Located within the assembled coupling are sealing gaskets 20 formed from an elastomeric material, the sealing gaskets each having axially directed portions for sealing engagement, respectively, with the exterior surface of a pipe, and, with the contained flow-controller sub-assembly 14. The flow-controller sub-assembly 14 in this embodiment is in the form of a butterfly valve, and, is comprised of a circular valve body 22 having bosses 24 extending diametrically thereof. The bosses 24 are to be received in socket openings 26 in the respective gasket segments 10 and 12, the respective bosses 22 providing a support for a rotatable spindle comprised of spindle portions 28 which are rigidly fixed to a butterfly valve 30. The butterfly valve is illustrated in a "closed" position, and is rotatable by the spindle 28 into an "open" position by rotating the butterfly valve about the Y-Y axis and towards or into coincidence with the Y,Z plane. Suitable bearings 32 and seals 34 are provided for the butterfly valves. The butterfly valve providing the flow-control sub-assembly 14 is shown separate from the coupling segments 10 and 12 in Figures 3-5. As a matter of convenience, the cylindrical valve body 22 is formed by casting or forging as two body portions 22A, 22B, which are assembled to each other on opposite sides of the butterfly valve 30, which itself is provided as a casting or forging integral with the spindle portions 28. The body portions 22A, 22B of the cylindrical valve body 22 are then rigidly secured to each other by rivets 36, the required bearings 32 and seals 34 having been pre-assembled onto the spindle portions 28. In this manner, a compact and relatively inexpensive butterfly valve construction is provided which readily can be removed from the coupling and replaced should servicing be necessary. As will be readily apparent, instead of providing a butterfly valve, the flow-control sub-assembly can provide different types of valves, such as a plug valve, or a ball valve by employing the same manner of construction. Without regard to the manner of configuration of the sealing surfaces of the flow-controller sub-assembly, a standard configuration of the outer surfaces of the flow-control sub-assembly can be provided. In this manner, interchangeability of any desired form of valve and the replacement of such valves can be accomplished using standard coupling segments that are identical in all respects one with the other. The formation of the coupling from identical coupling segments greatly reduces the manufacturing and warehousing costs, and also, eliminates the possibility of dissimilar coupling segments being incorrectly assembled one to the other. Referring now to Figures 6-10, a preferred configuration of the respective coupling segments 10, 12 is discussed, as is the manner of cooperation of those coupling segments one with the other to provide the benefits of the present invention. As will be more clearly apparent from Figure 9, the coupling segments 10 and 12 each have a semi-circular inner periphery adapting that coupling segment to be passed over the end of a pipe in a direction radially of the pipe axis. Tie respective coupling segments have bolting pads 40 having bolting faces for cooperation with either the head or the nut of a traction bolt 18, the bolting faces extending in a plane parallel to the X,Z plane of the coupling segment. Centrally of the coupling segment and arranged symmetrically around the Y-Y axis is a housing 42, which has internal surfaces configured to contain and locate a boss 24 of the flow-controller sub-assembly 14, the housing 42 providing the socket opening previously discussed. The respective opposite ends 44, 46 of the coupling segment are of identical configuration one with the other, but, reversed through 180° as viewed along the X-X axis. In this manner, any one end of any corresponding coupling segment will interfit with either end of an identical coupling segment. The respective end faces each are inclined with respect to the X,Z plane of the coupling segment, but, in opposite directions relative to the X,Y plane as illustrated in Figure 8. Thus, upon rotation of the coupling segment about the Y-Y axis through 180°, an end view of the coupling segment will be identical in all respects with that shown in Figure 8, and, the coupling segment will interfit with an identical coupling segment without regard to which of the end faces 44 and 46 of one of the coupling segments is presented to an end face 44 or an end face 46 of the other coupling segment. As will be observed from Figure 8, if the coupling segment is rotated 180° about the Y-Y axis, then, the end face 46 becomes the end face 44, and vice versa. In a preferred embodiment of the invention, and for purposes that will be discussed later with respect to Figure 10, the respective end faces each include two end face portions 44A and 44B, or, 46A and 46B. As is discussed later with respect to Figure 11, more than two end face portions can be provided. As shown in Figure 8, the end face portions 44A and 44B extend in planes parallel to each other, and similarly, the end face portions 46A and 46B extend in planes parallel to each other but reversed in direction with respect to the X,Z plane of the coupling segment. If the coupling segments are to be symmetrical and identical in all respects, this relationship has to be preserved. The respective end face portions 44A, 44B and 46A, 46B are interconnected at their adjacent ends by a further end face portion 44C or 46C, thus providing a sawtooth formation of the end faces as viewed along the X-X axis. The intermediate end face portions 44C and 46C must be positioned either coincident with the X,Y plane, or, as is preferable, displaced to opposite sides of the X,Y plane. This arrangement of the intermediate end face portions must be duplicated in reverse at the opposite end of the coupling segment, for otherwise the coupling segment will become asymmetrical. The intermediate end face portions 44C and 46C can extend parallel to the X,Y plane, but preferably are arranged at an angle to that plane converging towards that plane in the direction of the Y+ axis. The respective end faces 44A, 44B and 46A, 46B must be linear in the direction of the Z-Z axis. They do not necessarily need to be linear in the direction of the X-X axis but preferably are so. Similar considerations apply to the intermediate end face portions 44C and 46C as related to the X,Y plane of the coupling segment. Referring now to Figure 10, this Figure shows the ends of two coupling segments when arranged in interfitted relation, this interfitted relation having been produced by rotating the coupling segment 10 180° about the Z-Z axis for it then to become the coupling segment 12. In this interfitted relation of the end face portions, the end face portions 44A and 46A have become juxtaposed, and, the end face portions 44B and 46B have become juxtaposed, and, the intermediate end face portions 44C and 46C have become positioned in spaced parallel relation. In this relationship, the end face portions 44A, 44B and 46A,46B restrain the coupling segment 10 from movement in the Z- direction, and also restrain the coupling segment 12 from movement in the Z+ direction, any such movements producing interengagement of the respective end face portions 44A, 46A and 44B, 46B. Further, the coupling segments 10 and 12 can only move in the opposite direction by the distance B existing between the intermediate end face portions 44C and 46C. Thus, the coupling segments when assembled to each other are limited in the extent of their permitted movement about the Y-Y axis. Further, the interengagement of the respective end face portions 44A, 46A and 44B, 46B will act to orient the respective coupling segments in parallelism with, but not necessarily coincidence with the Y-Y axis of the pipe, i.e., lateral tilting of the respective coupling segments with respect to each other is eliminated. Upon tightening down of the traction bolts, the respective coupling segments are drawn towards each other into approximate coincidence with the X, Y plane, and, over-swinging of the respective ends of the coupling segments about the Y-Y axis is prevented. Such over-swinging of the ends of the respective coupling segments is to be avoided in that it can cause scuffing, distortion and dislocation of the seals 34 contained within the respective coupling segments, with consequential leakage at those seals in the finally assembled condition of the coupling. The more the respective coupling segments are drawn towards each other, the greater will be the compressive stresses exerted on the contained gaskets, which are then highly susceptible to scuffing, distortion and dislocation in the event that over-swinging of the ends of the coupling segments should occur. Over-swinging of the ends of the coupling segments is prevented by interengagement of the intermediate end face portions 44C and 46C, which determine the maximum extent of swinging movement. Provided that the intermediate end face portions 44C and 46C are spaced sufficiently from each other, then, the coupling of the present invention can accommodate all deviations within the range of manufacturing tolerances in the pipe and the consequential variations in the dimensions of the grooves. Referring now to Figures 12-15 an actuator for the flow-controller is illustrated. That actuator includes a housing 50 provided with a cover 52. The housing 50 is secured to the boss 24 of the flow-controller sub-assembly in any convenient manner in encircling relation with the spindle 28. The actuator includes a shaft 54, that can be rotated by a hand wheel, electric motor or any other convenient means, the shaft 54 having a threaded stem 56 which extends through the threaded bore of a travelling nut 58. The travelling nut 58 has oppositely extending bails or trunnions 60 that respectively extend into axially straight grooves 62 formed within the housing 50. Thus, on rotation of the spindle 54, the nut 58 will be caused to travel upwardly or downwardly within the axially straight grooves 62, depending on the direction of rotation of the shaft 54, in the absence of rotation of the nut. Surrounding the nut 58 and rotatably supported within the housing 50 is a sleeve 64, the sleeve 64 having circumferentially extending slots providing scroll cams 66, as illustrated in Figure 13. Thus, upon axial movement of the nut 58, the bales or trunnions will travel upwardly within the scroll cam slots 66, and in so doing, will cause the sleeve 64 to rotate. In this manner, a slow-motion drive is provided to the sleeve 64 requiring multiple turns of the spindle 54 to produce a 90° rotation of the sleeve 64. As shown in Figures 12 and 15, an indicator in the form of a pointer 68 is rigidly secured to the sleeve 64 and is journalled for rotation about the shaft 54. Thus, as the sleeve 64 slowly rotates, so will the indicator 68 slowly displaced between open and shut indications provided on the cover 52. As illustrated in Figure 14, this rotation of the sleeve 64 also can be utilized to actuate microswitiches 70 contained within the cover 52, the microswitches being operated by cam surfaces 72 on the sleeve 64. In this manner, an electrical signal can be provided to an indicator indicating the open or closed position of the butterfly valve 30.

Claims: A flow-controller assembly in the form of a segmented pipe coupling, comprising a complete flow-controller sub-assembly (14) having a valve body (22), a valve seat provided within said valve body (22) for co-operation with a rotatable valve member (30), a rotatable valve member (30) supported within said body (22) for rotation relative to said valve seat and into seating relation therewith, and means (28) for rotating said valve member (30) relative to said valve seat; at least two coupling segments (10,12) arranged in encircling relation with said valve body (22), said coupling segments (10, 12) having keys (16) for reception in grooves in the ends of pipes; and traction means (18) for securing said coupling segments (10,12) to each other in encircling relation with said pipe ends and said valve body (22); at least one of said coupling segments (10,12) providing access to said valve member rotating means (28) from a position exterior of that coupling segment characterised by a first gasket member (20) axially separable from the valve body (22) for forming a seal between the valve body (22) and one pipe and a second separable gasket member (20) also axially separable from the valve body (22), for forming a seal between the valve body (22) and a second pipe at the opposite side of the valve body (22). The assembly of claim 1, in which said valve body (22) is a ring shaped member having bosses (24) extending diametrically thereof, said coupling segments each providing a housing for one of said bosses. The assembly of claim 2, in which said rotatable valve member (30) is supported for rotation by coaxially aligned shaft portions journalled for rotation within said bosses, at least one of said shaft portions extending to the exterior of the associated coupling segment and providing for rotation of said valve member. The assembly of claim 3, in which said valve member (30) is one of a butterfly valve, a plug valve, and a ball valve. The assembly of claim 1, including sealing members (34) interposed between said valve member and said valve body. The assembly of claim 1, in which said coupling segments (10,12) each include an end face at the respective opposite ends (44A,44B;46A,46B) of said coupling members, the end faces of each said coupling member being oppositely inclined with respect to an X,Z plane of that coupling member. The assembly of claim 6, in which said oppositely inclined end faces are each comprised of end face portions extending in parallel relation, and, an intermediate end face portion (44C,46C) interconnecting the adjacent ends of said respective end face portions. The assembly of claim 7, in which said intermediate end face portions are arranged at an acute angle to an X,Y plane of said coupling segment. The assembly of claim 1, including an actuator mechanism (50,52,54,58,62,64,66) connected to said valve body exteriorly of said coupling segments. The assembly of claim 9, in which said actuator mechanism includes a slow-motion rotary drive between said valve member rotating means and a drive shaft (54). The assembly of claim 10, in which said slow-motion rotary drive includes a rotatable sleeve (64) having circumferentially extending scroll cam slots (66), a drive nut (58) contained within said sleeve and having trunnions extending through said scroll cam slots and into axially straight guideways in a housing surrounding said sleeve, and, an axially fixed threaded shaft threadedly received within said notch, whereby rotation of said threaded shaft will produce axial movement of said nut, and in turn produce a slow motion rotary movement of said sleeve.

Inventors: MCLENNAN WILLIAM ROSS, MCLENNAN, WILLIAM ROSS
Applicants: VICTAULIC CO OF AMERICA, VICTAULIC COMPANY OF AMERICA
Application year: 1991
Main classification: F16K27
IPC codes: F16K27, F16L17