Rotary joint

Abstract: A novel rotary joint (2) or coupling which couples a rotating element (6) to a non-rotating element (7) and allows for the passage of a process fluid (24) from the rotating element (6) to the non-­ rotating element (7) or vice versa, and seals the flowing process fluid (24) from the external environment. A rotary joint (2) useful for connecting a stationary object (7) to a rotating object (6) comprising: (a) bearing housing means (4) adapted to be joined to either the rotating (6) or the stationary object (7); (b) fluid conveying means (5) (14) adapted to be joined to either the stationary (7) or rotating object (6) to which the bearing housing means (4) is not joined; (c) sealing means (16) (18) positioned between the fluid conveying means (5) (14) and the bearing housing means (4) for preventing migration of fluid (24) from the fluid conveying means (5) (14) into the bearing housing means (4); and (d) rotatable bearing means (9) (10) positioned between the bearing housing means (4) and the fluid conveying means (5) (14), and exterior to the sealing means (16) (18), said bearing means (9) (10) being lubricated and cooled by a lubricating means (32) (34).

Description: FIELD OF THE INVENTION This invention is directed to a novel rotary joint or coupling which is useful for coupling a rotating element to a non-rotating element. More particularly, this invention is directed to a novel rotary joint or coupling which couples a rotating element to a non-rotating element and allows for the passage of a process fluid from the rotating element to the non-rotating element or vice versa, and seals the flowing process fluid from the external environment. BACKGROUND OF THE INVENTION The problem of coupling a rotating element to a non-rotating element while permitting a fluid to pass from one element to the other without leakage has been a challenging engineering problem for many years. The problem is amplified when high temperatures or high process fluid pressures are encountered. Numerous solutions to this fundamental engineering problem have been proposed over the years and many rotary joints, couplings or seals have been invented and utilized in industry. Calender rolls operating at high speeds, high temperatures and high pressures for pressing paper in pulp and paper mills present a problem of this nature together with other problems. Heating water is passed through the calender rolls at pressures up to 2,068 x 10⁶ Pa (300 psi) and at temperatures up to 232°C (450 deg. F). The calender rolls rotate at high speed pressing and ironing the continuous paper sheet that passes between the rolls. Lumps are often present in the paper sheet and cause the rolls to separate suddenly and impact together suddenly. This causes shock waves to be generated and transmitted to the rolls and any equipment attached to the rolls. The pipes transmitting heating fluid to and from the calender rolls are stationary. Many designs of rotary joints or couplings have been developed over the years for the purpose of connecting the stationary pipes to the rapidly rotating calender rolls, while conducting heating fluid through the calender rolls. Notwithstanding the technology that has been developed in this area over the years, it is common for such rotary joints or couplings to begin to leak two to three months after installation from seal breakage due to shock transmission. In the higher temperature cases, the bearings in the rotary joints seize from seal breakage that occurs due to impact shock. The bearings on the rotary joints must then be replaced. A number of patents disclose rotary couplings or joints which are representative. U.S. Patent No. 3,833,273, Rickley et al., granted September 3, 1974, discloses, in a rolling mill, an interlocking labyrinth-type seal for a roll neck which is rotatably supported in a chock assembly. The seal includes an inner first sealing element which rotates with the roll neck, an outer second sealing element which is fixed in relation to the chock assembly, and a third sealing element which is carried on and movable axially along one or the other of the first or second sealing elements. The sealing elements have axially and/or radially spaced flanges and surfaces which cooperate to define an interlocking sealing labyrinth for preventing the escape of lubricating oil from the bearing, while at the same time preventing the bearing and lubricating oil from becoming contaminated with rolling lubricant cooling water, mill scale, dirt, and the like. U.S. Patent No. 4,071,255, Salter, Jr., granted January 31, 1978, discloses a flexible seal element with a reinforced drain labyrinth for use on the outer seal ring of a seal assembly located between a roll end face and a bearing chock in a rolling mill, particularly the bearing chocks of the upper backup roll and the work rolls in a four-high mill. The seal element has a circular body portion adapted to tightly surround the outer seal ring. A first circular lip extends outwardly away from the body portion at an angle relative to the axis thereof to frictionally contact the roll end face. The seal body has a drain opening which is arranged to be aligned radially with a drainage port in the outer seal ring. The drain opening is protected by a second lip which extends outwardly from the seal body in a direction opposite to that of the first mentioned lip. A relatively stiff baffle member is attached to the seal body at a location spaced radially inwardly from the second lip. The baffle member and the second lip cooperate in providing a reinforced drain labyrinth which effectively prevents cooling water, mill scale, and the like, from being centrifugally directed upwardly into the bearing from the rotating surfaces of underlying rolls. U.S. Patent No. 4,585,236, Divirgilio, granted April 29, 1986, discloses a circular coolant seal which has a base flange arranged in a base plane perpendicular to the seal axis. A flexible resilient sealing flange is internally joined at one edge to the base flange and terminated at its opposite edge in a sealing lip located in a sealing plane parallel to and spaced axially from the base plane. The sealing lip has a first portion extending from the base flange angularly away from the base plane and inwardly towards the seal axis to an intermediate hinge portion, and a second portion extending from the hinge portion away from the seal axis and angularly towards the sealing plane. The configuration, flexibility and resilience of the sealing flange is such that axial displacement of the sealing lip in relation to the base flange is accompanied by both axial and radial displacement of the hinge portion. U.S. Patent No. 3,167,332, Simmers, granted January 26, 1965, discloses an apparatus for cooling trunnions and bearings for converters in steel mills wherein a large quantity of heat is generated. The device is specifically directed to cooling a trunnion, its journal and bearing, which has no readily accessible open end to which a conventional cooling system may be attached. U.S. Patent No. 3,259,442, Boghosian, granted July 5, 1966, discloses a seal for use in a rolling mill and more particularly to a means of preventing contamination of roll neck bearings by foreign matter such as cooling water, mill scale, dust, and the like, while at the same time, preventing loss of lubricating oil from the bearing chocks. In contrast with present invention and as will become clear from the appended claims, Boghosian does not disclose a rotary joint with a unique combination of a separately cooled rotatable seal and a rotating bearing mounted externally relative to the rotating seal. U.S. Patent No. 3,420,555, Faccou describes a swivel joint for use in conductive corrosive fluids at elevated temperatures having two ball bearing races which are located radially externally of a packing which forms a fluid tight seal between two interfitting conduits. The packing constitutes a stationary seal and does not provide a rotatable seal. The Faccou joint rotates solely about the ball bearings and no use is made of a cooling fluid circulated through the packing. It will, therefore, be appreciated that Faccou does not disclose a rotary joint including a rotatable seal which is positioned between the fluid conveyed through the joint and a rotatable bearing which is separately lubricated. In the invention, which is defined in the appended claims, the rotatable bearings are located between the bearing tube and the bearing housing means and are isolated from the sealing means and the seal tube. The rotatable bearing means can comprise an inboard bearing and an outboard bearing. The inboard bearing is located towards one end of the bearing tube and bearing housing, and the outboard bearing is located toward the other end of the bearing tube and bearing housing. The inboard bearing and the outboard bearing can be taper roller bearings, which comprise rollers rolling between the respective inner and outer races. The lubricating means may comprise a bearing lubricant which is introduced through a port in the bearing tube to a location between the inboard bearing and the outer bearing. The bearing lubricant can exit from the bearing housing through a port in the stationary part of the joint. Inboard and outboard labyrinth means can be formed at either end of the bearing housing to prevent entry of foreign contaminants to the inboard and outboard bearings and the exit of the lubricant to the exterior environment. A port may be provided in the bearing tube to enable seal lubricating and cooling fluid to be introduced to the inboard seal and the outboard seal between the bearing tube and the seal tube. The seal fluid can exit from the space between the bearing tube and seal tube through a port in the bearing tube. A removable spacing means can be positioned between the inboard bearing and the outboard bearing. Access to the inboard and outboard bearings can be gained by means of a removable cover which is removably joined to the bearing housing, a portion of the mating surface of the cover and the bearing housing forming the outboard labyrinth. Cooling fins may be formed in the exterior surface of the bearing housing surface. A coil spring means encircling the sealing tube can be located between the inboard seal and the outboard seal. In the rotary joint, respective stationary elements of the inboard seal and the outboard seal can be secured to the bearing tube. In the rotary joint, force applying means can be used to cause the inboard bearing and the outboard bearing to be withdrawn as a unit from the interior of the rotary joint. DRAWINGS In a drawing which illustrates a specific embodiment of the invention, but which should not be construed as limiting or restricting the spirit or scope of the invention in any way: Figure 1 illustrates a side elevation section view of the rotary joint. DETAILED DESCRIPTION OF A SPECIFIC EMBODIMENT OF THE INVENTION Figure 1 illustrates a side elevation section view of a rotary joint 2 or coupling which contains seals and bearings. The rotary joint is used to couple a rotating element to a non-rotating element and allows for the passage of a process fluid, such as a heating fluid, from one element to the other. The fundamental purpose of the rotary joint is to seal the process fluid flowing through the centre of the rotary joint from leaking to the external environment while at the same time protecting the bearings both from leakage and the heat of the process fluid and any internal or external contamination that might attempt to invade the bearings. The bearings and mechanical seals used in the rotary joint are conventional and can be purchased from any one of numerous manufacturers. The rotary joint 2 is constructed principally of a bearing housing 4 and a bearing tube 5. The bearing housing 4 is typically bolted to a rotating calender roll 6 and the bearing tube 5 is attached to a process fluid conveying pipe 7 by a threaded connection 8. The bearing housing 4 and bearing tube 5 are coupled to each other by two taper roller bearings 9 and 10 which allow the bearing housing 4 to rotate relative to the bearing tube 5 while maintaining an axially rigid assembly. While Figure 1 depicts taper roller bearings 9 and 10, it will be understood that other suitable types can be used. A seal tube 14 is attached to the bearing housing 4 by a back plate 12. A double mechanical seal consisting of an outboard seal 16 and an inboard seal 18 is mounted on the seal tube 14 and is located diametrically inside a large portion of the inner surface of the bearing tube 5. These seals 16 and 18 are located in a seal cavity 20 which is defined by the inner diameter of the bearing tube 5 and the outer diameter of the seal tube 14. It will be noted that the seal tube 14 is recessed slightly under both the inboard and outboard seal areas to provide some deflection room when the seal encounters a shock and deflects momentarily. Thus the seal does not impinge against the inner surface of seal tube 14 and break. The inboard seal 18 and the outboard seal 16 are positioned at each end of cavity 20. A cool fluid lubricant, termed "seal water", is circulated through seal cavity 20 via seal water in-port 22 and out through a seal water out-port (not shown) in the bearing tube 5. The seal water, besides lubricating the sealing faces of seals 16 and 18, acts as a heat buffer or shield between hot process fluid 24 (which is passing through the interior of bearing tube 5 and seal tube 14) and bearings 9 and 10 by absorbing and removing heat conducted from the process fluid 24 before it reaches the bearings 9 and 10. This feature helps to keep bearings 9 and 10 cool (overheated bearings are a major failure point of conventional rotary joints in high temperature applications) and is believed to represent a novel aspect of the invention. In the event that inboard seal 16 fails, the seal fluid, because of the intervention of bearing tube 5, and labyrinth 26, bypasses the bearings 9 and 10 and passes between the back plate 12 and inboard labyrinth 26 to exit hole 28. The outboard labyrinth 30 protects the bearings 9 and 10 from external contamination penetrating into the bearing. When oil is used as a bearing lubricant, the inboard 26 and outboard labyrinths 30 prevent the oil from flowing out into the external environment. Bearing lubricant is introduced between the bearings via the bearing lubricant inport 32 and exits via bearing lubricant outport 34. Lubricant migrates to the outport from the inboard side of the bearings via holes 36 in the bearing housing. As seen in Figure 1, bearing housing 4 rotates while bearing tube 5 remains stationary. Three bearing spacers are utilized in the embodiment depicted in Figure 1. The centre spacer 40 allows for adjusting axial and longitudinal play of the bearing tube 5 relative to the bearing housing 4 and is conventional. The two outside spacers 42 and 44 can be of various required sizes and allow for a choice to be made between bearings obtainable from different bearing manufacturers whose bearings vary in width. The rotary joint of the invention represents a strong improvement over known technology in that normally the bearings and seals in a conventional rotary joint are mounted in a line on the same fluid conveying tube. This correlation arrangement provides the heat from the process fluid an easy conduction path through the tube to the bearings thereby causing bearing breakdown. The construction of the outboard mechanical seal 16 and the inboard mechanical seal 18 is conventional. This facilitates replacement when the seals wear out. The seals 16 and 18 are positioned so that the rotating elements 48 and 50 face one another. A coil spring 46 encircles the seal tube 14 and forces the rotating elements 48 and 50 respectively to impinge against respective outboard seal stationary element 52 and inboard seal stationary element 54. The outboard seal stationary element 52 is held in place by outboard seal carrier 56. Likewise, inboard seal stationary element 54 is held in place by inboard seal carrier 58. O-rings 60 and 62 provide seals between outboard seal stationary element 52, outboard seal carrier 56 and the inside of the outboard surface of bearing tube 5. Likewise, O-rings 64 and 66 provide seals between inboard seal stationary element 54, inboard seal carrier 58, and the inside of the inboard surface of bearing tube 5. As a general rule, the O-rings are located at the centre of mass axis for each component. This prevents the respective components from attempting to "tip" when the joint is subjected to a shock wave. Any tipping action could cause damage to each part. Outboard taper roller bearing 9 rolls between inner race 68 and outer race 70. Similarly, inboard taper roller bearing 10 rolls between inner race 72 and outer race 74. Outboard taper bearing 9 and inboard taper bearing 10, together with ancillary elements, are enclosed by front cover 76, which mates with the outboard face of bearing housing 4 and forms the outboard face of outboard labyrinth 30. Front cover 76 is held in place by bearing lock washer 78 and bearing lock nut 80. Access to outboard bearing 9 and inboard bearing 10, and ancillary parts, can be gained by removing bearing lock nut 80, bearing lock washer 78, and front cover 76. This is useful when the time comes to service or replace bearings 9 or 10, and ancillary elements. Cooling of bearing housing 4 is assisted by bearing housing cooling fins 38 in the exterior surface of a portion of the bearing housing 4. O-rings 82, 84, 86 and 88 are used at various joint locations in the rotary joint 2 in order to provide seals against any migrating fluids, and also provide some shock absorbing capacity. The seal tube 14 and accompanying seals 16 and 18, spring 46, and the like, can be removed and replaced as a unit by a unique combination. Cap screws 92 (usually six or more in number) can be unscrewed to enable back plate 12 to be removed. Then, two or three of the cap screws 92 can be screwed into two or three extraction holes 94 formed in inboard seal carrier 58. This applies a force against the bearing tube and draws out the entire sealing unit as one piece. Snap ring 90, which fits in the outboard end of seal tube 14 ensures that the seal elements will not slide off the seal tube 14 as it is withdrawn. A snap ring 96 at the inboard end holds the inboard end of the seal components together. It is believed that a principal point of novelty of the invention resides in the placement of the bearings away from the heat source, using the seal water circulating through the seal cavity 20 to remove the heat normally transferred to the bearings.

Claims: A rotary joint for connecting a fluid conveyor (7) to a rotating object (6) comprising a bearing housing (4) attached to one of the conveyor or rotating object, a bearing tube (5) attached to the other of the said conveyor or object, and a seal tube (14) within the bearing tube and fast with the bearing housing, the bearing tube being supported within the bearing housing by rotary bearings (9, 10) provided with lubricating means (32, 34) characterised in that an elongated cavity (20) between the bearing tube and the seal tube is sealed at its ends by seals (16, 18 and 64, 66) and is provided with an inlet port (22) and an outlet port whereby cooling water may be circulated through the cavity to prevent heat from the fluid within the conveyor from reaching the bearings. A rotary joint according to claim 1, further characterised in that the cavity between the bearing housing and the bearing tube containing the rotary bearings is sealed by labyrinth seals (26, 30) and is provided with an inlet (32) and an outlet (34) for lubricant.

Inventors: ANTHONSEN NIELS A, ANTHONSEN, NIELS A.
Applicants: INDU TECH ENTERPRISES LTD, INDU-TECH ENTERPRISES LTD.
Application year: 1989
Main classification: F16L27
IPC codes: F16C13, D21G1, F16L27