Rotary joint for a high pressure fluid

Abstract

The rotary joint for a high pressure fluid, comprising a stator body, a rotor body, a fluid seal interposed between the stator body and the rotor body, and a friction reducer interposed between the stator body and the rotor body, the friction reducer comprising at least a first plain bearing for sustaining axial loads, and at least a second plain bearing for sustaining bending loads, the first and second bearings being made of a polytetrafluoroethylene-based (PTFE) material.

Claims

1. A rotary joint for a high pressure fluid, comprising: an axially hollow stator body that is open at the ends, an axially hollow rotor body that is open at the ends, a fluid seal interposed between the stator body and the rotor body, and a friction reducer interposed between the stator body and the rotor body, wherein said friction reducer comprises at least a first plain bearing for sustaining axial loads, and at least a second plain bearing for sustaining bending loads, said first and second bearings being made of a polytetrafluoroethylene-based (PTFE) material, wherein the first plain bearing and the second plain bearing work simultaneously, wherein the first plain has an annular friction surface orthogonal to an axis of a joint, wherein the second plain bearing has a cylindrical friction surface arranged coaxially with the axis of the joint, wherein the first plain bearing engages a frontal surface of a projection of the rotor body in a recess of the stator body, wherein the first plain bearing is made of axially overlapping first and second flat annular surfaces, and wherein the first flat annular surface engages with the stator body, and the second flat annular surface engages with the rotor body.

2. The rotary joint for a high pressure fluid according to claim 1, wherein said first plain bearing is made up of a ring that has flat ends and is arranged coaxially with the axis of the joint.

3. The rotary joint for a high pressure fluid according to claim 1, wherein said second plain bearing is made up of a bushing-shaped strip arranged coaxially with the axis of the joint.

4. The rotary joint for a high pressure fluid according to claim 1, wherein said first and second plain bearings are spaced away from each other.

5. The rotary joint for a high pressure fluid according to claim 1, wherein said first and second plain bearings are juxtaposed.

6. The rotary joint for a high pressure fluid according to claim 1, wherein said first plain bearing is glued to said stator body or said rotor body.

7. The rotary joint for a high pressure fluid according to claim 1, wherein said second plain bearing is glued to said stator body or said rotor body.

8. The rotary joint for a high pressure fluid according to claim 1, wherein said fluid seal comprises at least one gasket made of a polytetrafluoroethylene-based (PTFE) material.

9. The rotary joint for a high pressure fluid according to claim 8, wherein said gasket is integrated with an elastomeric ring.

10. The rotary joint for a high pressure fluid according to claim 9, wherein said elastomeric ring is an O-ring.

Description

BRIEF DESCRIPTION OF THE DRAWING

(1) Further characteristics and advantages will become more evident from the detailed description of the rotary joint for a high pressure fluid according to the invention, which is illustrated by way of approximate example in the attached FIGURES, wherein:

(2) FIG. 1 is an axial section view of the rotary joint.

DETAILED DESCRIPTION

(3) With reference to the FIGURES cited, a rotary joint for a high pressure fluid is shown and indicated in its entirety by reference number 1.

(4) The rotary joint 1 comprises a stator body 2 that is preferably, but not necessarily made of metal, axially hollow and open at the ends and a rotor body 3 that is preferably, but not necessarily made of metal, axially hollow, open at the ends and coaxially intersecting in a given area with the stator body 2.

(5) In the area of the intersection of the stator body 2 with the rotor body 3, the external lateral surface 7 of the rotor body 3 faces the internal lateral surface 6 of the stator body 2.

(6) The stator body 2 is made up of two threaded lengths 2a and 2b that are fixed one to the other by screwing, and likewise, the rotor body 3 is made up of two threaded lengths 3a and 3b that are fixed one to the other by screwing.

(7) The lateral surfaces 6, 7 facing each other substantially have the configuration of cylinders oriented coaxially with the axis L of the joint 1 and exhibiting discontinuities in diameter.

(8) The discontinuities in the inside diameter of the stator body 2 in the area of the intersection with the rotor body 3 define a recess 14 that extends radially with respect to the direction of the axis L of the joint 1.

(9) The discontinuities in the outside diameter of the rotor body 3 in the area of the intersection with the stator body 2 define a projection that extends radially with respect to the direction of the axis L of the joint 1 and engages in the recess 14 to prevent the rotor body 3 from axially sliding off the stator body 2.

(10) The recess 14 and the respective projection 15 have frontal surfaces 8, 18 and 9, 19, 20, 21, respectively, that is to say surfaces that extend radially to the axis L of the joint 1.

(11) Specific fluid sealing means 4 and specific friction reduction means 5 are interposed between the stator body 2 and the rotor body 3.

(12) The friction reduction means 5 advantageously comprises at least a first plain bearing 10 for sustaining axial loads and at least a second plain bearing 11 for sustaining bending loads.

(13) The bearing 10 is operative between the frontal surfaces 8, 9 that face each other, whereas the bearing 11 is operative between the lateral surfaces 6, 7 that face each other.

(14) The first plain bearing 10 and the second plain bearing 11 are made of a polytetrafluoroethylene-based (PTFE) material, for example pure polytetrafluoroethylene (PTFE) or polytetrafluoroethylene filled with carbon, metal oxides, bronze or suchlike.

(15) The first plain bearing 10 is made up of a ring that has flat ends and is fitted onto the rotor body 3 coaxially with the axis L of the joint 1 and having an outside radius that is markedly greater than the height thereof.

(16) The second plain bearing 11 is made up of a bushing-shaped strip fitted onto the rotor body 3 coaxially with the axis L of the joint 1.

(17) The thickness of the wall of the first plain bearing 10 and of the second plain bearing 11 preferably ranges between 1.5 and 2.5 mm.

(18) The first plain bearing 10 is separated and axially spaced away from the second plain bearing 11.

(19) However, it is not excluded that the first plain bearing 10 second plain bearing 11 may be juxtaposed in a possible variant.

(20) The first plain bearing 10 and the second plain bearing 11 are fastened to the stator body 2 or the rotor body 3.

(21) In the illustrated solution, the first bearing 10 is glued to the frontal surface 9 of the projection 15, whereas the second plain bearing 11 is glued to the internal lateral surface 7 of the rotor body 3.

(22) The fluid sealing means 4 comprises at least one gasket 12 made of a polytetrafluoroethylene-based (PTFE) material, for example pure polytetrafluoroethylene (PTFE) or polytetrafluoroethylene filled with carbon, metal oxides, bronze or suchlike.

(23) The gasket 12 is integrated with an elastomeric ring 13, particularly an O-ring. The elastomeric ring 13 is preferably made of a material selected from among nitrile butadiene rubber (NBR), ethylene propylene, chloroprene, silicone or fluorocarbon.

(24) Compared to the friction reduction means 5, the fluid sealing means 4 is closer to the end of the rotor body 3 inside the stator body 2.

(25) In particular, with respect to the projection 15, the fluid sealing means 4 is arranged opposite the friction reduction means 5.

(26) The fluid sealing means 4 is housed in a recess 16 in the internal lateral surface of the stator body 2.

(27) The operation of the rotary joint 1 according to the invention appears to be clear from the description and illustration, and more specifically, it is carried out substantially as indicated herein below.

(28) The fluid under pressure subjects the joint 1 to an axial tensile force as a result of which the first plain bearing 10 is pressed against the frontal surface 8 of the recess 14.

(29) The first plain bearing 10 thus guides the rotation of the rotor body 3 and prevalently sustains the axial loads, whereas the second plain bearing 11, which exhibits an adequate axial extension, guides the rotation of the rotor body 3 and prevalently sustains the radial loads and the bending loads.

(30) The gasket 12 provides for dynamic sealing, whereas the elastomer ring 13 supplies the elastic energy needed to ensure sealing activation over time by the gasket 12.

(31) Owing to their special constituent material, the plain bearings 10 and 11 and the gasket 12 offer guarantees of adequate mechanical strength and chemical resistance, a high-lubricating capacity, high embeddability of abrasive particles with which they may come into contact, the absence of stick-slip, wear resistance, reliability over time, low friction resistance, low cost, and operability in a wide range of operating temperatures and pressures.