GB2134604A

GB2134604A - Rotatable shaft seals

Info

Publication number: GB2134604A
Application number: GB08302450A
Authority: GB
Inventors: Ralph Franklin John Flower
Original assignee: Cross Manufacturing Co 1938 Ltd
Current assignee: Cross Manufacturing Co 1938 Ltd
Priority date: 1983-01-28
Filing date: 1983-01-28
Publication date: 1984-08-15
Also published as: DE3402030A1; JPS59144859A; FR2540213A1; GB8302450D0; GB2134604B; US4526387A; FR2540213B1; JPH052869B2

Description

1 GB 2 134 604 A 1

SPECIFICATION Rotatable shaft seals

This invention relates to a seal assembly for a rotatabie shaft extending through a bore in a housing, which assembly is adapted to minimise the leakage of fluid through the bore, between the shaft and the housing. Although the seal assembly of this invention is applicable generally as a seal for a shaft rotatable within a bore in a housing, it has particular utility as a seal assembly for sealing the shaft of a turbo-charger rotor and the invention will hereinafter be described by way of example with reference to such apparatus.

A known form of seal assembly for a shaft extending through a bore in a housing and rotatable with respect thereto, to effect a fluid seal between the shaft and the housing comprises an annular groove formed in the shaft in the region thereof within the bore and an annular sealing member located in the groove in the shaft and bearing against the housing wall defining the bore. The sealing member may be metallic and have a radial gap at one point on the circumference thereof, whereby the ring may be expanded and contracted circumferentially to a limited extent. The 'natural' or free diameter of such a ring should be slightly greater than the bore diameter, whereby the ring when located in the groove and lying within the bore, is contracted circumferentially to a small extent, such that the ring may bear resiliently on the wall defining the bore. Such a sealing member for use in the just described kind of seal assembly is referred to hereinafter as a "split-ring sealing member".

A seal assembly including a split-ring sealing member often is used to form a seal between a rotatable shaft and a housing therefor particularly where the shaft is to turn at a relatively high rate -and hence to have a relatively high surface speed, which will preclude the use of a non-metallic resilient seal assembly, for example using a natural or synthetic rubber seal element. An example of such an application is in the case of the sealing of the rotor shaft of a turbo-chargipr, but due to the clearances necessary to permit the 110 shaft to rotate and also those arising as a result of wear, the leakage of fluid - such as lubricatingoil - often occurs through a seal assembly using a split-ring sealing member, particularly when the shaft is stationary.

It is an object of this invention to provide an improved seal assembly employing a split-ring sealing member, in an attempt to reduce the likelihood of leakage through the seal assembly.

Accordingly, this invention provides a seal 120 assembly for a shaft extending through and rotatable within a bore in a housing, which sealing assembly comprises an annular groove formed around a part of the shaft which lies within the bore in the housing, a first split-ring sealing member located within the groove, and at least one second split-ring sealing member located at least partially within the groove so as to overlie and be engaged by said first split-ring sealing member, the or each second split-ring sealing member also bearing agains the wall of the bore defined by the housing to effect a seal thereagainst.

In the seal assembly of this invention, one or more of the split-ring sealing members may have a simple radial gap, but it is preferred for at least one of the split-ring sealing members to be of the step-gap type, in which a portion of the end of the ring to one side of the gap lies axially alongside a portion of the end of the ring to the other side of the gap. Advantageously to enhance the sealing characteristics of the seal assembly, two or even more second split-ring sealing members may be provided, in an axially side-by-side disposition and each being engaged by said first split-ring sealing member.

Preferably, the first split-ring sealing member has a greater axial width than the width of the second split-ring sealing member, or of the total axial width of all of the second split-ring sealing members when disposed side-by-side for a case where more than such second split-ring sealing member is provided. The first split-ring sealing member should however be a free running fit in the groove, such that the first sealing member does not turn with the shaft but instead is maintained stationary by virtue of its engagement with the second split-ring sealing member. The clearances on the sides of the first split-ring sealing member, relative to the walls of the groove, should be maintained at a minimum, so as to give a minimum leakage, and to allow the ring to follow minor axial perturbations of the shaft.

The provision of two split-ring sealing members allows there to be sufficient axial clearance in the shaft groove for the second split-ring sealing member to allow working 'float' and to accommodate wear after an initial 'running in' period, whilst still permitting an excellent seal to be achieved because the first split-ring sealing member seres to effect a seal between the second split-ring sealing member and the shaft. Because the first split-ring sealing member only has to bear resiliently on inner diameter of the second split-ring sealing member and effect a seal against the walls of the groove, the first split-ring sealing member may have a lesser radial width than the or each second split-ring sealing member.

This invention extends to the combination of a housing having a bore, a shaft extending through the bore and mounted for rotation therewithin, and a seal assembly of this invention as defined above provided within the bore. The shaft and housing combination may comprise the shaft of a turbo-charger rotor and the casing therefor, respectively.

By way of example only, the invention will now be described in greater detail, reference being made to the accompanying drawings, in which:

Figure 1 is fragmentary longitudinal section of a part and of the rotor shaft and housing of a turbo charger, showing a seal assembly arranged in accordance with this invention; Figure 2 is a view similar to that of Figure 1, but 2 GB 2 134 604 A 2 showing an alternative form of seal assembly of this invention; Figure 3 is a view of a yet further alternative form of seal assembly of this invention; and 5 Figure 4 is a perspective view of a step-gap type of sealing member suitable for use in a seal assembly of this invention. Referring initially to Figure 1, there is shown a turbo-charger rotor shaft 10 mounted for rotation and extending with clearance through a bore 11 provided in a housing 12 of the turbo-charger, with clearances 13 and 13a between the shaft and the housing on the respective sides of the seal assembly 14 of this invention provided within the bore 11. The clearance 1 3a is preferably the 80 minimum effective running clearance for the shaft within its housing, so as to provide a minimum leakage path for fluid, such as lubricating oil.

The seal assembly of this invention comprises an annular groove 15 formed around a portion of the shaft 10 which when assembled with the housing 12 lies wholly within the housing, adjacent a step 16 in the bore in the housing. The seal assembly further comprises a first split ring sealing member 17 located wholly within the groove 15 and a second split-ring sealing member 18, lying partially within the groove 15 in the shaft but also engaging the step 16 of the bore 11. Both split-ring sealing members are metallic and have resilient properties, such that the second split-ring 95 sealing member 18 bears against the wall of the housing defining the bore 11, and the first split ring sealing member bears on the inner diameter of the second split-ring sealing member.

As mentioned above, the first split-ring sealing member 17 is a close running fit within the groove 100 in the shaft, to give a minimum clearance leakage path, but the second split-ring sealing member 18 has a lesser axial width than the first split-ring sealing member 17, the assembly being such that neither the first nor the second split-ring 105 sealing members rotate with the shaft. However, the first split-ring sealing member 17 will follow small axial perturbations of the shaft 10 relative to the housing 12, whilst at all times covering the gap (not shown) in the second split-ring sealing 110 member 18, the second split-ring sealing member serving to effect a seal to the housing.

When in use, the seal assembly is subjected to gas pressure from the turbo-charger through clearance 13, but to oil pressure through the clearance 1 3a is found that the described seal assembly provides an improved form of seal, giving reduced leakages of fluid thereacross.

Figure 2 shows an alternative form of seal assembly of this invention, and parts similar to those illustrated in Figure 1 are given like reference characters; such parts will not be described again here. In the seal assembly of Figure 2, the single second split-ring sealing member 18 (Figure 1) is replaced by two split-ring 125 sealing members 20 and 21 disposed side- byside, such that the combined width of the two second sealing members 20 and 21 is comparable to the axial width of the single sealing member 18 of the assembly illustrated in Figure 1. It is of course possible to provide yet further second splitring sealing members side-by-side, provided that the overall combined axial width is still less than the axial width of the first split-ring seal member 17. With such an arrangement, the gap of one second sealing member 20 is unlikely to be aligned with the gap of the or each further second sealing member, thereby further reducing the likelihood of the leakage of fluid through the seal assembly.

Figure 3 shows a further alternative seal assembly of this invention, and parts similar to those illustrated in Figure 2 are given like reference characters. In the assembly of Figure 3, the two second split-ring sealing members 20 and 21 (Figure 2) are replaced by split-ring sealing members 25 and 26 each of the stepgap type, so as further to reduce the likelihood of leakage across the seal assembly. Figure 4 illustrates the step-gap type of sealing members used in the seal assembly of Figure 3, and from this Figure 4 it can be seen that a portion 27 of one end 28 of the ring 29 to one side of the gap 30 has a reduced axial width, the portion 31 of the end 32 to the other side of the gap 30 also having a reduced axial width but in a complementary sense, such that the two reduced portions 27 and 31 may overlie each other, side-by-side. It will be appreciated that a gap 30 having this particular configuration will serve to enhance the fluid sealing characteristics of the ring.

Claims

1. A seal assembly for a shaft extending through and rotatable within a bore in a housing, which sealing assembly comprises an annular groove formed around a part of the shaft which lies within the bore in the housing, a first split-ring sealing member located within the groove, and at least one second split-ring sealing member located at least partially within the groove so as to overlie and be engaged by said first splitring sealing member, the or each second split-ring sealing member also bearing against the wall of the bore defined by the housing to effect a seal thereagainst.

2. A seal assembly according to claim 1, wherein at least one of the split-ring sealing members is of the step-gap type, in which a portion of the end of the ring to one side of the gap lies axially alongside a portion of the end of the ring to the other side of the gap.

3. A seal assembly according to claim 1 or claim 2, wherein two second split-ring sealing members are provided in an axially side-by-side disposition, each second split-ring sealing member being engaged by said first split-ring member.

4. A sealing assembly according to any one of the preceding claims, wherein the first split-ring sealing member has a greater axial width than the width of the second split-ring sealing member, or a greater axial width than the total axial width of all of the second split-ring sealing members disposed side-by-side, when more than one Z V, 1 Ir GB 2 134 604 A 3 3 second split-ring sealing member is provided.

5. A seal assembly according to any of the preceding claims, wherein the first split-ring 15 sealing member is a free running fit in the groove in the shaft, so that in use the first sealing member does not turn with the shaft.

6. A seal assembly according to any of the preceding claims, wherein the first split-ring 20 sealing member has a lesser radial width than that of the or each second split-ring sealing member.

7. A seal assembly according to claim 1 and substantially as hereinbefore described with reference to and as illustrated in Figure 1 or in Figure 2 or in Figure 3 of the accompanying drawings.

8. The combination of a housing having a bore, a shaft extending through the bore and mounted for rotation therewithin, and a seal assembly according to any of claims 1 to 7 which assembly serves to seal the shaft to the housing.

9. A turbo-charger whenever having a seal assembly according to any of claims 1 to 7, to effect a seal between the shaft of the turbocharger rotor and the casing therefor.

Printed for Her Majesty's Stationery Office by the Courier Press, Leamington Spa, 1984. Published by the Patent Office, 25 Southampton Buildings, London, WC2A lAY, from which copies may be obtained.