BUTTERFLY VALVE

Abstract: A butterfly valve is provided having a rotary disc (22) in a housing (60,62) having a valve seat (24) of resilient material. The seat (24) has an outer wall and an aperture therein. A shaft (26,34) affixed to the disc (22) extends through the aperture. A ring (36) surrounds the seat (24) and prevents deformation of the outer wall. The ring (36) is of material much stronger and more rigid than the seat (24) and includes a lip defining an aperture therein in line with aperture. A cylindrical collar (42,44) surrounds the shaft (26,34) and is positioned within the cylindrical lip and supported thereby. The collar (44) provides a bearing surface for the shaft (26,34). The valve seat (24) further includes a pair of flanges (50,52) on the axial ends thereof projecting outward from the outer wall. The ring (36) is positioned between the flanges (50,52) and spaced therefrom creating a groove (54,56) on each side of the ring (36). The disc (22), the seat (24), the shaft (26) and the ring (36) form a unitary valve assembly. The housing is in two sections (60,62), each including projections (64,66) mating with grooves (54,56) to hold the unitary valve assembly within the housing (60,62). The shaft (26) has one end (28) affixed to a hub (29) on the disc (22) by splines which interfere with the hub (29) by a maximum dimension of .030 inch. The hub (29) has a stress less than 20,000 p.s.i. The shaft (26) and the disc (22) are joined by machining the hub (29) with a hole having a diameter slightly smaller than that of the shaft (26). The shaft (26) is pressed into the hole, such that the splines cut grooves in the hole. A retaining ring (108) frictionally engages the shaft (26) and abuts a bearing (106) to ensure that fluid leaking along the shaft (26) past a seal (102) does not eject the bearing (106) and cause injury.

Description: "Butterfly Valve" The present invention relates generally to butterfly valves and more particularly to butterfly valves having an improved cartridge type construction with improved bearings for the valve shaft. In the butterfly valve art valves have been constructed wherein the valve seat, the actuator shaft, and the valve disc are removable from the valve as a single unit, thereby facilitating repair of the valve in the field. For example, U.S. patent Nos. 2,740,423 and 2,994,342 to Stillwagon and U.S. Patent No. 3,241,806 to Snell, Jr. all illustrate such a concept. however, to date, no such valve has been developed which is capable of deadend service; i.e., retaining pressure within a line whc the valve is in the closed position and the conduit cn one side of the valve has been removed. Another problem that has existed with such valves is that the bearing required for the disc shafts have been difficult to align. Therefore, rather expensive machining operations have been necessary to provide good shaft alignment. The present invention also relates generally to butterfly valves and more particularly to a butterfly valve having an improved connection between the valve shaft and the valve disc. Butterfly valves have historically been provided with one of two general types of connections between the actuator shaft and the valve disc. In one type of connection the disc includes a portion of increased thickness running longitudinally down the centre of the disc and the actuator shaft is passed completely through the centre of the disc and pivoted for rotation at the top and the bottom of the valve. While such connections have been generally successful, they suffer from the disadvantage of being relatively expensive due to increased material and machining costs and also suffer from the disadvantage that a onehat increased restriction to flow is presented when the valve is in the open position. A second general type of actuator shaft connection has been generally called a stub shaft connection. In stub shaft butterfly valves the disc includes portions of increased thickness at the top and the bottom of the disc only. The actuator shaft is partially inserted into the disc at the top of the disc and a small shaft is inserted into the bottom of the disc. Such stub shafts have been connected to the disc in a variety of manners. In some instances the shafts have been pinned or bolted to the disc. Another approach has been to use a broached type connection such as a square connection or a hexagonal connection. Such connections have been subject to the disadvantages of leaking, providing protuberances into the flow stream, or looseness of connection resulting in a backlash making it difficult to close the valve tightly, providing poor control with automatic actuators, or even permitting shaft blow out. Another type of connection which is known and which tends to overcome some of the aforementioned difficulties is a knurled or upset interference fit between the shaft and the valve disc. In this type of connection the shaft is provided with projections on the end thereof, which when forced into contact with the hole in the top of the disc tend to radially deform the hole thereby resulting in an interference fit. This type of connection has suffered from the disadvantage that where a good connection-has been made, high stresses are created in the valve disc, which is usually cast iron, increasing the possibility of failure of the valve disc. These high stress levels are required because the disc hub stresses must create a high compressive frictional force in order to fully transmit the valve shaft torque in addition to preventing backlash and preventing the shaft from blowing out due to normal or abnormal internal pressures. While the disc hub may be made larger to reduce the stresses, this increases the cost of material. Furthermore, in those instances where the interference fit is not tight enough, valves may fail under pressure by forcing the shaft axially out of the hole, or by the interference connection being inadequate to transmit the required torque from the shaft to the disc. The present invention relates generally to butterfly valves and more particularly to a butterfl valve having a retaining ring for preventing unwanted ejection of the bearing between the shaft and the housing of the butterfly valve. Butterfly valves have historically been provided with seals and bearings between the housing and the shaft The bearing generally supports the shaft and the seal prevents fluid from leaking along the shaft to the bearing. It has been found that fluid pressure within the butterfly valve may build up behind the seal and bearing causing the bearing to eject from the valve in a bulletlike manner. As a general rule, the valve actuator is located on the shaft and may stop the bearing from causing any serious injury or damage. However, in situations where the actuator has been removed from the valve shaft, the ejection of the bearing from the valve could easily cause serious personal injury or property damage, either from the bearing itself or the resultant expulsion oi - pipeline fluid and pressure. Accordingly, a butterfly valve has been provided having a disc adapted to be rotated between an open and a closed position. A valve seat made of resilient material is adapted to engage the disc in the closed position. The valve seat has an outer wall surrounding the disc and has an aperture therein. A shaft has one end affixed to the disc and extends outwardly through the aperture. A ring surrounds the valve seat and is permanently affixed thereto for preventing deformation of the outer wall of the valve seat. The ring is made of a material that is much stronger and more rigid than the valve seat and includes a cylindrical lip defining an aperture in the ring. This aperture is in line with the aperture in the valve seat wall with the lip projecting into the aperture in the valve wall. A cylindrical collar surrounds the shaft and is positioned within the cylindrical lip and supported thereby. The collar provides a bearing surface for the shaft. The valve seat further includes a pair of flanges on the axial ends thereof projecting outward from the outer wall. The ring is positioned between the flanges and spaced therefrom creating a pair of grooves, one groove being on each side of the ring. The disc, the valve seat, the shaft, and the ring form a unitary valve assembly. A housing is provided including two sections, each section including a pair of projections on the inner surface thereof for mating with the pair of grooves. The sections are joined and co-operate with the ring and the outer wall of the valve seat to hold the unitary valve assembly within the housing. The butterfly valve has a disc with a hub adapted to be rotated between an open and a closed position and a valve seat adapted to engage the disc in the closed position. A shaft has one end affixed to the hub and extends outwardly therefrom to permit torque to be transmitted to the disc from a point external thereof. The end of the shaft affixed to the disc includes a plurality of splines for securing the shaft to the disc. Each of the splines has a sharp leading edge and interferes with the hub by a maximum dimension of .030 inch. The hub has a stress that is less than 20,000 pounds per square inch. The shaft is joined to the disc by forming the valve disc with a portion of increased thickness (hub) relative to the main portion of the disc. The portion of increased thickness is formed adjacent the circumference of the disc. A hole is then machined into the portion of increased thickness parallel to the disc, with the hole having a diameter slightly smaller than the diameter of the shaft. Splines are formed on one end of the shaft and the shaft is then pressed into the hole, cutting grooves in the side walls of the hole1 thereby forming á permanent connection between the shaft and the disc. The butterfly valve has a disc with a hub. The disc is adapted to be rotated between an open and closed position. A housing has a valve seat that is adapted to engage the disc in the closed position. A shaft has one end affixed to the hub and extends outwardly of the housing to permit torque to be transmitted to the disc from a point external thereof. A seal is provided for preventing fluid from passing between the shaft and the housing. A bearing supports the shaft in the housing at a point where the shaft extends outwardly over the housing. A retaining ring frictionally engages the shaft and abuts the bearing to ensure that fluid leaking along the shaft does not eject the bearing and cause injury. Thus an object of the present invention is the provision of a butterfly valve having an improved unitary assembly which may be removed from the valve housing and which is capable of containing normal desired pressures without support from the valve housing. Another object of the present invention is the provisions of a butterfly valve including an improved unitary valve assembly which is capable of use in deadend service. A further object of the present invention is the provision of a butterfly valve having improved bearings which are easy to align and therefore inexpensive to manufacture. Yet another object of the present invention is the provision of a butterfly valve having improved shaft seals for preventing leakage along the axial intershaft. Yet another object of the present invention is the provision that a butterfly valve having an improved unitary valve assembly which is both inexpensive and easy to manufacture. Yet another object of the present invention is the provision of a butterfly valve having a stub shaft connection with the valve disc which will not be subject to failure due to the internal pressure of the valve. Yet another object of the present invention is the provision of a butterfly valve having an improved stub shaft connection to the disc which eliminates anx mechanical backlash between the disc and the shaft. Yet another object of the present invention is the provision of a butterfly valve having an improved stub shaft to disc connection wherein the torque transmitting capability of the connection exceeds that of the shaft. Yet another object of the present invention is the provision of a butterfly valve having an improved stub shaft to disc connection which leaves the disc in a condition of low residual stress. Still another object of the present invention is the provision of a butterfly valve having an improved stub shaft to disc connection which does not create any additional protuberances into the flow stream when the valve is in the open position. Still another object of the present invention 1S the provision of a butterfly valve having an improvec stub shaft to disc connection that requires low resicua' hub stress to prevent backlash and shaft blow out but IJC extra stress is required to transmit shaft to disc torque. A still further object of the present inlentir is the provision of a butterfly valve having an improved stub shaft to disc connection which is both simple in construction and inexpensive to manufacture. Still another object of the present invention is the provision of a butterfly valve having a means for protecting persons and property adjacent the valve in cases where high pressure caused ejection of bearing as,d fluids from the valve. Still another object of the present invention is the provision of a butterfly valve having the safety feature referred to above and wet being relatively easy to assemble. Still another object of the present invention 1 the provision of a butterfly valve having the safety feature referred to above and being relatively inexpensive to manufacture. Other objects, advantages and novel features of the present invention will become apparent from the following detailed description of the invention when considered in conjunction with the accompanying drawings. Figure 1 shows a longitudinal cross section view of the butterfly valve of the present invention; Figure 1A shows a top view of a retaining ring shown in Figure 1; Figure 2 shows a longitudinal cross section of the valve seat and bearing assembly of the o'iteri valve shown in Figure 1; Figure 2A shows a modified end structure on the ring illustrated in Figure 2; Figure 3 shows a partial longitudinal cross sectional view of the valve seat and valve housing of t,e butterfly valve shorn in Figure 1; Figure 4 shows a plan vie of the valve shaft of the butterfly valve showy in Figure 1; Figure 5 shows a front view of the shaft s}Jcçm. in Figure 4; Figure 6 shows an enlarged partial front view of the shaft shown in Figure 4; Figure 7 shows a longitudinal cross sectional view of the valve disc of the butterfly valve shown in Figure 1 as the shaft shorn in Figure 4 is being inserted in; Figures 8 and 9 show in schematic form the method of making the valve shaft of the present invention; Figure 10 shows a portion of the butterfly valve including an alternate retaining ring; Figure 11 shows a top view of the retaining ring shown in Figure 10. Figure 1 shows a butterfly valve 20 including a disc 22 adapted to be rotated between an open and a closedposition. A-valve seat 24 made of resilient material, preferably rubber, surrounds the disc 22 and is adapted to engage the disc when the valve is in the closed position. A shaft 26 has one end 28 affixed to the disc 22 at hub 29 and extends outwardly therefrom. The other end of shaft 26 is connected to an actuator of any desired type (not shown). As is best seen in Figure 2, the valve seat 24 includes an outer wall 25 having a pair of apertures 30 and 32 therein. The shaft 26 extends through the aperture 30 and a second shaft 34 is affixed to the bottom of disc 22 and extends outwardly therefrom through aperture 32. A ring 36, preferabl made of steel, surrounds the outer wall 25 of valve seat 24 and is permanently affixed thereto, preferably by vulcanization, in order to prevent deformation of the outer wall of the valve seat. It is important that the ring 36 be made of a material that is much stronger and much more rigid than the valve seat 24. Preferably, ring 36 should be strong enough to support the rated pressure of the valve, even without the housing. The ring 36 further includes a pair of cylindrical lips 38 and 40, each defining an aperture in the ring. The cylindrical lips 38 and 40 are located snugly within the apertures 30 and 32, respectively. A cylindrical collar 42 surrounds the shaft 26 and is positioned within the cylindrical lip 38 in such a manner that the lip 38 supports the collar 42 and the collar 42 in turn provides a bearing surface for the shaft 26. Likewise, a cylindrical collar 44 surrounds the shaft 34 and is positioned within cylindrical lip 40 in such a manner that the lip 40 supports the collar 44 and the collar 44 in turn provides a bearing surface for the shaft 34. It is a particularly important feature of the present invention that b inserting the collars 42 and 44 into the valve seat 24, the bearing surfaces provided for the shafts 26 and 34 respectively are positioned as close as possible to the disc 22. This has the greatly beneficial effect of reducing bearing loads by minimiz- ing the moment between the shaft and the bearing. It has the additional beneficial effect of making it easy to align the bearings with the shaft. The collars 42 and 44 are also preferably vulcanized into the valve seat 24 to create a unitary structure with the valve seat 24 and the ring 36. The upper and lower apertures 30 and 32 in the outer wall of valve seat 24 includes a means for sealing the outward portion ow aft 2' from the disc 22 whereby fluid is prevented from leaking along the shaft 26. This is accomplished by radially extending flange 46 extending inwardly from the wall of the aperture 3(s JJear the toj: of the disc 22. The end of tlje cylindrical lip 30 and the end of the collar 42 abut the top surface of the flange 46, which has an inside diameter that is slightly smaller than the inside diameter of collars t" and 44. The inner surface of the projection 46 contacts ttie shaft 26 above spline 70 to effectively seal the shaft 26 from the disc 22, due to radial compression of the elastomeric flange 46. Referring to Figure 2A, there is shoT a modified ring 36'. In situations where the bearing loads are increased, such as in larger butterfly valves, a cylindrical ember 38' may be welded to ring 36'. The member extends radially inwardly and outwardly of ring 36' for added support for collar 42. As is best seen in Figure 3 the valve seat 24 includes a pair of flanges 50 and 52 on the axial ends thereof projecting radially outwardly from the outer wall 25. The ring 36 is positioned between the flanges 50 and 52 and spaced therefrom creating a pair of grooves 54 and 56, with one groove being on each side of the ring 36. At this point it should be apparent that the disc 22, the valve. seat 24, the shafts 26 and 34, the ring 36, and the collars 42 and 44 form a unitary valve assembly or cartridge. The butterfly valve 20 further includes a housing having an upper section 60 and a lower section 62. Each of the sections 60 and 62 includes a pair of projections 64 and 66 on the inner surface thereof for mating with the pair of grooves 54 and 56 respectively. The sections 60 and 62 are joined, preferably by bolting, and co-operate with the ring 36 and the outer wall 25 of the valve seat 24 to hold the unitary valve assembly within the housing. Thus, the butterfly valve of the present invention is provided with the important con structional feature of having a complete valve cartridge within the valve housing which may be removed easily for servicing or replacement. Additionally1 in-' this valve cartridge includes a rigid retaining ring which co-operates with the valve housing, the valve mdY be utilized for dead-end service. This is so since even should the valve be in the closed position and the conduit dostream of the pressure be removed from conn- ection to the valve 20, the valve cartridge of the present invention is sturdy enough to retain rated pressure without being deformed radially, or displaced axially because of the co-operation of ring 36 and projections t)e and 66. As is showy in Figures 4 to 9 the butterfly valve 20 includes an improved connection between the shafts 26 and 34 and the disc 22. For simplicity the connection will be described with regard to shaft 26. The end 28 of shaft 26 which connects with disc 22 incl-U¯ a plurality of splines 70 for securing the shaft 26 to art disc 22. The height of eaci! of the splines 70 is defined as the space between a plane tangent to the outer surface of the spline 70 and a plane parallel to the-aforementicin- ed plane and tangent to the imaginary continuation of the grooves 72 interspersed between splines 70. This is illustrated as "h" in Figure 6. It is significant that this dimension "h" be no more than .030 inch. This figure is derived by adding the maximum interference between the splines and the hub, .025 inch, plus approx imately .005 inch for tolerances, Should the interference exceed .025 inch, the cutting stresses during shaft installation become unacceptable. While a clearance between groove 72 and hole 88 is not required, it is desirable to vent gas that may be trapped in cavity 7b Clearance between bore 88 and the surface 72 provides for venting of air. The interference between the splines and the hub is preferably .011 inch and the tolerance is preferably .003 inch. The clearance is preferably .005 inch. Each of the splines 70 includes a cylindrical top surface portion 75 and two side walls 74 and 76 extending therefrom toward the body of the shaft at an angle with respect to the plane tangent to the top surface portion at the centre thereof. This angle1 illustrated as X in Figure 6, is between 30 and 60 degrees and is preferably 45 degrees. The reasons for the above dimensional constraints are that it is important to minimize the amount of material removed from the disc 22 during the process of inserting the shaft 26 while at the same time attaining a strong joint. Additionally, it is important not to place undue stress on the disc 22 during this operation. Since there will be some removal of material during the insertion of shafts 26 and 34 into disc 22, it is important that the disc 22 be provided with internal cavities 78 and 80 for receiving any material removed from the interior of the disc during the process of joining the shafts to the disc. Since the shafts 26 and 34 must cut into the disc 22 it is imperative that these shafts have a hardness greater than the hardness of the disc 22. It has been found that the minimum difference between the hardness of the shaft and the hardness of the disc should be approximately 5 on the Rockwell C scale, with the shaft being the harder material. For example, the shaft may be made out of steel having a Rockwell C hardness greater than 33 and the disc may be made of cast iron having a Rockwell C hardness less than 27. It is also preferable that the length of the splines is approximately one and one-half times the diameter of the shaft and the width of the splines is approximately onequarter to approximately one-third the diameter of the shaft. For example, a shaft one-half inch in diameter could have six splines, each 0.158 inch wide and threequarters of an inch long. Thus, the circumference or the shaft will determine the number of splines there are. As is most apparent from Figure 7 the present valve is of the stub shaft type and thus valve disc 22 is formed with hub portions 82 and 84 having increased thickness relative to the main portion 86 of the disc. The portions of increased thickness 82 and 84 are adjacent the circumference of the disc 22. In smaller valve sizes (such as less than approximately three inches) the hubs may run together into one continuous cylindrical surface. The method of joining the shafts to the disc ill be described only with respect to shaft 26, it being understood that the same process applies to shaft 34. A hole 88 is drilled in the portion 82 of disc 22. The hole 88 has a diameter which is smaller than the diameter of the shaft 26, but larger than the shaft surface diameter 72 to provide clearance. A slightly larger hole 90 is drilled as a pilot hole to facilitate the insertion of the shaft 26, and to allow for the "start" area of the splines, after the shaft is installed. As is shown in Figures 8 and 9 splines are formed on the end 28 of shaft 26 by cutting tool 92. The cutting tool 92 includes a plurality of cutting elements 94 for cutting grooves in the shaft 26. The shaft 26 is then pressed into hole 88, as is illustrated in Figure 7 thereby utilizing the splines 70 to cut grooves in the side walls of the hole 88 to form a permanent joint between the shaft and the disc. The resultant connection exceeds the torque transmitting capability of the shaft 26 and the strength of the disc 22. At the other end of shaft 26, there is provided a unique bearing retainer assembly 100. As is best seen in gure 1, assembly 100 includes an elastomeric tO" ril 102 compressed radially between shaft 26 and cylindrical bore 125 witb bearing 106 and shoulder 104 forming the walls of an "u" ring groove. "" ring 102 and bearing 106 may be made of any suitable material such as rubber and bronze, respectively. In order to ensure that fluid leaking along shaft 96 does not eject bearing 106 and cause personal injury or property damage, a retaining ring 108 is provided, abutting bearing 106. Referring to Figure 1A, retaining ring 108 includes a split ring portion 110, engage shaft 26, having ends 112 and 114. Each of ends 112 and 114 includes a hole 116 and 118, respectively. These holes may be used in assembling and disassembling retaining ring 108 on shaft 26. By merely inserting projections into the holes, retaining ring may be opened and closed The retaining ring may be made of any suitable material, such as carbon spring steel (SAE 1060-1090). The retaining ring exerts a frictional hold against axial displacement. Should fluid pressure become sufficient to eject bearing 106, the frictional grip of retaining ring 108 on shaft 26 will stop axial movement of bearing 106, because the shaft 26 is firmly retained in the valve dise 22 as described earlier. It may be desirable, as an added precaution, to provide an annular groove 120 in shaft 26 adjacent to retaining ring 108. In this case, even if a sudden high leakage pressure were sufficient to slide retaining ring 108 along shaft 26, retaining ring 108 (being sprung) would seat itself in groove 120 which prevents further axial movement of the retaining ring. The width of the groove should be at least slightly wider than the width of the retaining ring so that the retaining ring will easily fall into the groove. For example, the groove should be at least approximately .030 inch wider than the retaining ring. It is significant that the groove be spaced axially from the retaining ring. Since the groove is formed prior to assembly, it would be difficult to estimate the precise location of the retaining ring. By cpacing the groove from the retaining ring the manu fracturing process is simplified. Referring to Figures 10 and 11, there is shown a modified retaining ring 108'. In many cases, such as with small butterfly valves1 it may be sufficient to use a retaining ring such as the one illustrated in Figures 10 and 11. This retaining ring 108' includes a circumferentially extending portion 122 with a plurality of radially extending fingers 124. Retaining ring 108' may be slid over shaft 26 with relative ease since radially extending fingers 124 extend axially away from the direction of travel of the retaining ring as it is installed on shaft 26. Retaining ring 108' may be made of any suitable material, such as carbon spring steel. While it has not been illustrated in Figure 101 it may be desirable to include an annular groove on shaft 26 similar to the one that is used with respect to retaining ring 108. Should fluid pressure become sufficient to eject bearing 106, the frictional grip of retaining ring 108' on shaft 26 will be increased by the force of bearing 106 on the back of fingers 124 to stop ejection of bearing 108. While there has been described what is at present considered to be the preferred embodiment of the present invention, it will be obvious to those skilled in the art that various changes and modifications may be therein, without departing from the invention, and it is, therefore, deemed in the appended claims to cove all such changes and modifications as followed in th true spirit and scope of the invention.

Claims: CLAINS:- 1. A butterfly valve comprising: v a disc adapted to be rotated between an open and a closed position; a valve seat made of resilient material, and adapted to engage said disc in said closed position, said valve seat having an outer wall surrounding said disc, said outer wall having an aperture therein; a shaft having one end affixed to said disc and extending outwardly therefrom through said aperture; a ring surrounding said valve seat and permanently affixed thereto for preventing deformation of said outer wall of said valve seat, said ring being made of a material that is much stronger and more rigid than said valve seat, said ring further including a cylindrical lip defining-an aperture therein, said aperture being aligned with the aperture in said valve seat wall, said lip projecting into said aperture in said valve seat wall; and a cylindrical collar surrounding said shaft and positioned within said cylindrical lip whereby said lip supports said collar and said collar provides a bearing surface for said shaft. 2. A butterfly valve as defined in claim 1 wherein said ring is metal. 3. A butterfly valve as defined in claim 1 wherein said valve seat is rubber and wherein said ring and said bearing are vulcanized into a unitary structure. 4. A butterfly valve as defined in claim 1 wherein said valve seat wall includes another aperture and wherein said ring includes another cylindrical lip defining another aperture therein, said other aperture being aligned with said other aperture in said valve seat all, said other lip projecting into said other aperture in said vale seat wall; wherein said valve further includes another shaft having one end affixed to said disc and ext endinc outwardly therefrom through said other apertures and another cylindrical collar surrounding said other shaft and positioned within said other cylindrical lip whereby said other lip supports said other collar and said collar provides a bearing surface for said other shaft. 5. A butterfly valve as defined in claim 1 wherein said aperture in said outer wall of said valve seat includes m eans for sealing said outward portion of said shaft from said disc whereby fluid is prevented from leaking along said shaft. 6. A butterfly valve as defined in claim 5 wherein said aperture in said outer wall of said valve seat includes a projection extending inwardly from the walls thereof near the top of said disc, the end of said cylindrical lip and the end of said collar abutting the top surface of said projection, the inner surface of said projection contacting said shaft, whereby sad projection provides said sealing means. 7. A butterfly valve comprising: a disc adapted to be rotated between an open and a closed position; a valve seat made of resilient material, and adapted to engage said disc in said closed position; said valve seat having an outer wall surrounding sad disc, said outer wall having an aperture therein; a shaft having one end affixed to said disc and extending outwardly therefrom through said aperture; ; a ring surrounding said valve seat and permanently affixed thereto for preventing deformation of said outer wall of said valve seat, said ring being made of a material that is much stronger and more rigid than said valve seat, said valve seat further including a pair of flanges on-the axial ends thereof projecting outward from said outer wall, said ring being positioned between said flanges and spaced therefrom creating a pair of grooves, one groove being in each side of said ring; said disc, said valve seat1 said shaft, and said ring forming a unitary valve assembly; and a housing including to sections1 each section including a pair of projections on the inner surface thereof for mating with said pair of grooves, said sections being joined and co-operating with said ring and said outer wall of said valve seat to hold said unitary valve assembly within said housing. 8. A butterfly valve as defined in claim 7 wherein said ring is metal. 9. A butterfly valve as defined in claim 7 wherein said valve seat is rubber and wherein said ring is vulcanized into said valve seat as a unitary structure. 10. A butterfly valve as defined in claim 7 wherein said valve seat wall includes another aperture and wherein said valve further includes another shaft having one end affixed to said disc and extending outwardly therefrom through said other aperture; said disc, said valve seat, said shafts1 and said ring forming a unitary valve assembly. 11. A butterfly valve comprising: a disc having a hub and adapted to be rotated between an open and a closed position; a valve seat adapted to engage said disc in said closed position; and a shaft havin one end affixed to said hub and extending outwardly therefrom to permit torque to be transmitted to said disc from a point external thereof, said one end of said shaft including a plurality of splines for securing said shaft to said hub, each of said splines interfering with said hub by a maximum dimension of .030 inch and said hub having a stress that is less than 20,000 pounds per square inch. 12. A butterfly valve as defined in claim 11 wherein said maximum dimension is .011 inch. 13. A butterfly valve as defined in claim 11 wherein said hub has a stress of approximately 12,800 pounds per square inch. A A butterfly valve as defined in claim 11 wherein each spline has a length approximately one and one-half times the diameter of the shaft an( a width from approximately one-quarter to approximately one-third the diameter of the shaft. 15. A butterfly valve as defined in claim 11 wherein each of said splines includes a cylindrical top surface portion and two side walls extending therefrom toward the body of said shaft at an angle with respect to the plane tangent to said top surface portion at the centre thereof, said angle being between 30 degrees and 60 degrees. 16. A butterfly valve as defined in claim 15 wherein said angle is 45 degrees. 17. A butterfly valve as defined in claim 11 wherein said hub includes a plurality of grooves mating with said splines and having a depth equal to the height of said splines for preventing relative movement between said disc and said shaft. 13. A butterfly valve as defined in claim 11 wherein said disc includes an internal cavity between said one end of said shaft and the centre of said disc for receiving any material removed from the interior of said disc during the process of joining said shaft to said disc. 19. A butterfly valve as defined in claim 11 wherein said shaft has a hardness much greater than the hardness of said disc. 20. A butterfly valve as defined in claim 19 wherein the difference between the hardness of the shaft and the hardness of the hub is approximately 5 on the Rockwell C scale. 21. A butterfly valve as defined in claim 19 wherein said shaft is made of hardened steel and said disc is made of cast iron. 22. A butterfly valve as defined in claim 19 wherein. said disc is made of a ductile iron. 23. A butterfly valve as defined in claim 11 further including another shaft having one end affixed to said disc and extending outwardly therefrom, said one end of said shaft including a plurality of splines for securing said other shaft to said disc, each of said splines having a height no more than ,030 inch. 24. A method of joining the shaft of a butterfly alve to the valve disc comprising: forming the valve disc with a portion of increased thickness relative to the main portion of the disc, said portion of increased thickness being formed adjacent the circumference of the disc; drilling a hole in said portion of increased thickness parallel to the disc, said hole having R diameter slightly smaller than the diameter of said shaft; forming splines on one end of said shaft; and pressing said one end of said shaft into said hole b cutting grooves in the side walls of said hole with said splines thereby forming a permanent joint between said shaft and said disc. 25. A method as defined in claim 24 wherein said splines are formed by cutting grooves on said one end of said shaft. 26. A butterfly valve comprising: a disc having a hub and adapted to be rotated between an open and a closed position; a housing having a valve seat adapted to engage said disc in said closed position; a shaft having one end affixed to said hub and extending outwardly of said housing to permit torque to be transmitted to said disc from a point external thereof; a seal for preventing fluid from passing between said shaft and said housing; a bearing for supporting said shaft in said housing, said bearing being at a location where said shaft extends outwardly of said housing, and a retaining ring frictionally engaging said shaft and abutting said bearing to ensure that fluid leaking along said shaft does not eject said bearing and cause injury or loss of fluid. 27. A butterfly valve as defined in claim 26 wherein an annular groove is provided in said shaft adjacent said retaining ring rllerebr, if said retainer ring were to slide axially along said shaft, said retaining ring wound seat itself in said groove to prevent further axial move ment. 28. A butterfly valve as defined in claim 26 wherein said retaining ring includes a split ring portion engaging said shaft. 29. A butterfly valve as defined in claim 26 wherein said retaining ring includes a circumferentially extending portion wit a plurality of radially inwardly extending fingers engaging said shaft.

Inventors: BARTHELEMY, PAUL JAMES, CLAUSING, DALE ROBERT, LIBKE, ALBERT WARNER, TROTT, DONALD ROSS
Applicants: GENERAL SIGNAL CORPORATION
Application year: 1979
Main classification: F16K1
IPC codes: F16K1