MECHANICAL SEAL ASSEMBLY

Abstract

A mechanical seal assembly has two axially-spaced apart seals and including a rotary component that includes rotational members of each axially-spaced apart seal and a stationary component that includes stationary sealing members of each seal. A sleeve is located radially inwards of the rotational sealing members. An element, such as fluid ports, directs barrier or buffer fluid towards the sleeve and between the two axially-spaced apart seals. The sleeve is provided on its outer surface with means, such as recesses or protuberances, which displace barrier/buffer fluid axially towards both axially-spaced apart seals.

Claims

1. A mechanical seal apparatus having two axially-spaced seals, comprising: a rotary component comprising at least one rotational member for each axially-spaced seal of said two axially-spaced seals; a stationary component comprising at least one stationary sealing member of each said axially-spaced seal of said two axially-spaced seals; a sleeve located radially inwards between said at least one rotational member for each said axially-spaced seal of said two axially-spaced seals; and, means for directing barrier or buffer fluid towards said sleeve between said two axially-spaced seals, wherein said sleeve has on its outer surface means for displacing the barrier or buffer fluid axially toward said two axially-spaced seals.

2. The mechanical seal apparatus having two axially-spaced seals according to claim 1, wherein said means for displacing the barrier or buffer fluid comprises a plurality of circumferentially-spaced apart recesses, protuberances or both recesses and protuberances.

3. The mechanical seal apparatus having two axially-spaced seals according to claim 2, wherein the recesses or protuberances are elongated, extending axially along said sleeve.

4. The mechanical seal apparatus having two axially-spaced seals according to claim 2, wherein the recesses or protuberances extend radially by an amount that increases circumferentially from a first edge to a second edge of each of the recesses or protuberances.

5. The mechanical seal apparatus having two axially-spaced seals according to claim 4, wherein a circumferential extent of the recesses or protuberances is reduced at a mid-point thereof for providing a fluid cutting effect.

6. The mechanical seal apparatus having two axially-spaced seals according to claim 5, wherein said circumferential extent of the recesses or protuberances being reduced is provided by a substantially triangular-shaped element extending into the recesses or protuberances from the first edge with the first edge having a greater depth than the second edge.

7. The mechanical seal apparatus having two axially-spaced seals according to claim 6, wherein the recesses or protuberances are arranged in circumferentially-spaced apart pairs, the first edges having the greater depth being adjacent each other.

8. The mechanical seal apparatus having two axially-spaced seals according to claim 1, wherein said stationary component surrounds at least a portion of said sleeve with a radial gap therebetween, the radial gap varying circumferentially for aiding axial and radial movement of the barrier or buffer fluid.

9. The mechanical seal apparatus having two axially-spaced seals according to claim 1, further comprising at least one angled barrier or buffer fluid port, wherein the barrier or buffer fluid is fed rearward of said at least one stationary sealing members for aiding in cooling said at least one stationary sealing components.

Description

BRIEF DESCRIPTION OF THE DRAWING FIGURES

[0017] In the drawing, wherein similar reference numerals and symbols denote similar features throughout the several views:

[0018] FIG. 1 is a cross-sectional view of a mechanical seal assembly in accordance with the present invention;

[0019] FIG. 2 is an alternative cross-sectional view of FIG. 1, which shows the plurality of springs which provide the spring force to the sealing faces;

[0020] FIG. 3 is a top view of the sleeve of the assembly of FIG. 1 showing the detailed recessed sections which promote axial movement of the barrier/buffer fluid;

[0021] FIG. 4 is a detailed view from FIG. 3 showing the flow paths of the barrier/buffer fluid in a counter-clockwise rotation of the shaft;

[0022] FIG. 5 is an alternative detailed view of FIG. 3 showing the flow paths of the barrier/buffer fluid in a clockwise rotation of the shaft;

[0023] FIG. 6 is an alternative cross-sectional view showing the radial offset which is present in the apparatus between both stationary faces and the sleeve;

[0024] FIG. 7 is an auxiliary view of the mechanical seal showing the direction of the barrier/buffer fluid with respect to rotation of the shaft;

[0025] FIG. 8 is an isometric view of the sleeve which gives a visual representation of the sleeve design; and,

[0026] FIG. 9 is a detailed view of FIG. 8 showing the variation in depth of the recesses.

DETAILED DESCRIPTION OF THE DRAWING FIGURES AND PREFERRED EMBODIMENTS

[0027] The invention will now be described, by way of example only, with reference to the accompanying drawings:

[0028] Referring to FIG. 1 of the accompanying drawings, there is shown a mechanical seal assembly having a sleeve 1, which is detachably attached to a shaft 2 by means of a plurality of grub screws 3. The grub screws are housed within a clamp ring 4 and provide rotational drive to the sleeve 1 and rotational sealing members 5a, 5b.

[0029] A seal is created via the stationary sealing members 6a, 6b being in contact with the rotational sealing members 5a, 5b. The inboard rotational sealing member 5a is provided with a driving force by a drive pin 7. All the aforementioned parts are housed within a gland 11. Within the gland 11 there are housed inlet and outlet ports 10 angled towards the stationary sealing members 6a, 6b and rotary sealing faces 5a, 5b. The port 10 is positioned at angle a to provide both optimum flow and cooling. Generally, angle α is 20°. The port 10 is offset by distance β to produce an offset port 12 which is positioned directly at the inboard stationary face 6a. Generally offset β is 0.095 inches (2.413 mm.)

[0030] Referring to FIG. 2 of the accompanying drawings, there is shown an alternative cross-sectional view. The stationary sealing members 6a, 6b are provided with a spring force via a plurality of springs 8a, 8b. The outboard rotary sealing face 5b is provided with a driving force by a drive pin 9.

[0031] Referring to FIG. 3 of the accompanying drawings, there is shown a detailed view of said sleeve 1, where the axial flow inducing radially recessed sections 13 are located.

[0032] Referring to FIG. 4 of the accompanying drawings, there is shown the barrier/buffer fluid flow paths 14 which occur when rotational movement of the shaft is in a counter-clock wise direction A. As shown in FIG. 4, the flow paths 14 extend in both axial directions down the length of the shaft per the clockwise rotation A.

[0033] Referring to FIG. 5 of the accompanying drawings, there is shown the barrier/buffer fluid flow paths 15, which occur when rotational movement of the shaft is in a clockwise direction B. As shown in FIG. 5, the flow paths 15 extend in both axial directions down the length of the shaft per the clockwise rotation B.

[0034] Referring to FIG. 6 of the accompanying drawings, there is shown an alternative cross-sectional view. Shown is the radial offset between said stationary sealing faces 6a, 6b and the sleeve 1. This offset has a larger distance γ and a smaller distance 8 which allows all rotational and stationary components to be located at a safe distance with respect to one another. The offset γ, δ in addition creates a pressure differential to induce optimal flow rate around the system. Generally, the optimal offset δ is 0.030 inches (0.762 mm) and offset γ is greater than 0.070 inches (1.778 mm.)

[0035] Referring to FIG. 7 of the accompanying drawings, there is shown the directions of the barrier/buffer fluid flow D1, D2 with respect to the alternative shaft rotations A, B. Barrier/buffer fluid flows in direction D1 when the shaft is spinning in a counter-clockwise direction A. In this instance port 10 is the inlet port and port 16 is the outlet port for the barrier/buffer fluid. Barrier/buffer fluid flows in direction D2 when the shaft is spinning in a clockwise direction B. In this instance port 16 is the inlet port and port 10 is the outlet port.

[0036] Referring to FIG. 8 of the accompanying drawings, there is shown the elongated recesses 17 which extend axially along the sleeve 1. The elongated recesses 17 are spaced circumferentially around the periphery of said sleeve 1, preferably the elongated recesses 17 are spaced six times equally around the sleeve 1.

[0037] Referring to FIG. 9 of the accompanying drawings, there is shown a detailed view of the elongated recesses 17. The elongated recesses 17 are present in adjacent pairs 18a and 18b and shaped in such a way that the depth increases tangentially to produce a vertical section 19. The vertical section 19 acts to more effectively capture the barrier/buffer fluid as the sleeve 1 rotates. The circumferential extent of the elongated recesses 17 is reduced at the mid-portion 20. The mid-portion 20 is substantially triangular in shape and provides a fluid cutting effect.

[0038] While only several embodiments of the present invention have been shown and described, it will be obvious to those skilled in the art that many modifications may be made to the present invention without departing from the spirit and scope thereof.