JPH0444144B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Field of Application) The present invention relates to an integral elastic seal spring supported by a self-lubricating bearing.

BACKGROUND OF THE INVENTION High-speed rotating metal parts have long had problems with lubrication and resulting wear because they must be housed in metal bearings with different coefficients of expansion. As a direct result, at high speeds, heat is generated despite adequate lubrication between the parts, resulting in opposing metal parts expanding at different rates and drawing lubrication away from the containing gearbox. Put it away. Once the lubrication leaks,
If the equipment undergoes significant wear and movement, its fate is sealed. Similar problems have been experienced with equipment that utilizes high speed reciprocating motion.

Seals located between metal parts in the form of bearings are
Advantageously, it accommodates these high speed relative movements for long periods of time and can be made of recently developed materials with high inherent lubricity. For example, bearing products sold under the trademark VESPEL are very expensive and must be machined, but they function as seals under the above conditions. However, this is a case where the sealing surface is gently, reliably, and continuously acted on without applying excessive pressure; if excessive pressure is applied, excessive wear may occur. This indicates that there is no structure so far devised or known that sufficiently provides such a seal. this is,
There was no known method to provide continuous and substantially uniform covert pressure between metal parts with standard dimensional variations over the temperature range encountered during long periods of high speed motion. be. There has been no known method for automatically adjusting this pressure to compensate for dimensional changes across the range of temperature changes that occur in the component.

(Problem to be solved by the invention) Compositions such as Vespel are already known;
Although their self-lubricating properties are recognized, the inventors have found that such simple annular bearings do not compensate well for differences in the expansion coefficients of different opposing metals. As a result, we used a split ring bearing that allows the circumference of the bearing to be changed. however,
It has been found that split ring bearings also do not work well except under limited circumstances. in this case,
Despite the variations in the initial dimensions of the installed components and the fluctuations that occur due to the generated heat, even moderate pressure, which causes the sealing surfaces of highly lubricated bearings to act lightly but reliably and evenly on the sealing surfaces, does not cause harmful creating a wear situation. Therefore, we considered using standard O-rings or QUAD rings of standard size and configuration, but found that neither would work satisfactorily. This is because these rings do not initially apply the proper pressure, or they overstress the bearing and the heat generated causes dimensional changes. This is because these rings overfill the grooves or become essentially incompressible rectangles, in which case the bearing surfaces would rather withstand high radial pressures without excessive wear. will be exposed to.

(Means for Solving the Problems) In order to solve these problems, the inventor of the present invention tried various tests and found that the bearing member
If it is made of a material that has inherent self-lubricating properties at pressure velocity values of 1800 or more at 100 ft/min and is formed into a split ring for circumferential adjustment, it may also flow easily, such as rubber. It has been found that when provided with a resilient back-up spring of suitable critical dimensions of the material, a long-lasting and effective seal for long-term high speed motion is provided.
To obtain such a seal, the cross-section is polygonal, of substantially equal transverse dimensions, with convex corner lobes and opposite concave sides, the degree of concavity and convexity and the maximum and minimum radial dimensions are within critical ranges. We designed an elastic back-up spring that meets the specified values. The backup spring is substantially symmetrical in cross-section.

The critical radial distance between opposite radially spaced working surfaces of two rings is 60− of the maximum radial distance of opposite corners on one side of the rings.
In the range of 75%, preferably 68%. The corner lobes are 14-
The radius of the convexity is 16%, preferably 16%. The recesses in the two opposing working surfaces are 17−1 of the above distance.
33%, preferably 28%.

(Function) An elastic ring that has a combination of these features has an excellent function and provides sufficient benefits, and is able to withstand all differences in dimension due to differences in expansion coefficients, as well as excessive radial radiation applied to the bearing. It has been found that any changes in initial dimensions are adequately compensated for without pressure. Relatively deep recesses in the opposing working surfaces and sharp convexities in the adjacent corners create a soft or slow pressure on the backside of the bearing seal and adjust this pressure radially to prevent excessive pressure fluctuations at the seal. Dimensional changes can be made without causing In this way, a sufficient seal can be provided without excessive heat or wear. The rubber of the convex corner lobes flows into a relatively deep recess in the adjacent working surface, which provides sufficient space for it to form a rectangular rubber block that is free-flowing but not compressible. It seems to be avoided. Instead, the elastic ring is
Continue to apply gentle pressure to the back of the bearing seal, similar to the pressure applied during initial installation. Backup springs are designed to provide a gentle, gradual pressure of approximately 1.9 to 3.0 pounds per square inch, which is held at a substantially constant level by the rubber flow described above. Therefore, sealed bearings are
Continue to provide sufficient sealing over the entire circumference of the sealed bearing without excessive wear.

(Example) FIG. 1 shows the use of one of the integrated elastic seal springs of the present invention. As is clear,
High-speed rotating metal shaft 10 with an annular groove 11 provided on the outer surface
is opposed to a metal bearing member 12 surrounding the shaft 10. At this time, this shaft 10 rotates at high speed for a long period of time. Typically, the bearing 12 is attached to the shaft 1
Because of the different coefficients of expansion from the metals that make up the zero, the consequences of high speed and consequent dimensional changes with temperature increase for each of these metals are quite different. As a result, some air gap, indicated by 13, provided between the two members 10, 12 allows lubrication and its dimensions change substantially. Such substantial changes in dimensions result in loss of lubrication. As a result, the bearing member 12 will be damaged unless provision is made to prevent lubrication from escaping. To meet such requirements, the present invention provides a sealing means including a split ring bearing seal member 14, which has an outer circumference substantially equal to the bearing surface of the bearing 12 at the location of the air gap 13. have. The split ring bearing member is self-adjusting and is constructed from a self-lubricating material having a pressure velocity of greater than 1800 at a face velocity of 100 feet per minute. As shown in FIG.
, which extends axially outwardly and has an axis 10.
It fits into the opening 16 provided in the. This tongue 15 ensures that the bearing member 14 rotates together with the shaft 10 within the bearing 12.

Split ring bearing member 14 is shown in detail in FIGS. 5-7. As best seen in FIG. 7, it is cut diagonally 17 and has free ends 18, 19 which are circumferentially and axially movable relative to each other. This allows the bearing 14
When properly pushed outward by the integral elastic seal spring of the present invention shown between and the bottom of the groove 11, it provides automatic adjustment to dimensional changes due to temperature changes. It can be seen that the bearing 12 and the shaft 10 provide a support structure for the seal completed therebetween by the structure shown in FIG.

Groove 11 in supporting relation to bearing seal 14
Disposed within is one of the integral resilient seal springs of the present invention, commonly designated by the number 20. This sealing spring consists of an integral annular body whose cross section is usually a right-angled polygonal structure.
Made of a fluid, elastic material such as rubber. In fact, the present invention uses an elastomer compound instead of real rubber. The ring 20 is of uniform cross-sectional shape throughout and is symmetrical as best seen in FIGS. It can be seen that the ring 20 has opposing concave side surfaces 21 and 22, which are working surfaces and are radially spaced. The ring also has a pair of axially spaced concave sides 23,24. These concave sides are
It merges in a generally normal line with the convex corner lobes of the rings identified by numbers 25-28.

Ring 2 measured between the bottoms of recesses in two opposing radially spaced sides 21, 22
The minimum radial dimension of 0 is 60-75% of the maximum normal radial dimension between the working surfaces. This maximum radial dimension measures the maximum distance between two opposite corners of the sides of the ring, such as the distance between the points labeled 29 and 30 in FIG. The preferred range of this minimum radial dimension is 65-70% of the maximum radial dimension, and the ideal minimum radial dimension at the bottom of the opposing recess is 68% of the maximum radial dimension.
It is.

The corner lobes 25 to 28 have working surfaces 21,
It has a convexity of 14-16% of the maximum radial distance between 22. The preferred convexity is 16% of this maximum radius dimension.
It is.

The recess in each of the four sides 21 to 24 is substantial. These recesses span a range of 17-33% of the maximum normal radial dimension of the ring, as previously defined. This preferred range is 24-
30% and the ideal range is 27-29% of that dimension.
It is. A preferred single dimension is 28% of the maximum normal radial dimension between active surfaces.

It has been found that the dimensions defined above can provide an effective long-term seal between metal surfaces moving past each other at high speed over long periods of time. This operation is
As shown in FIG. 1, this is a rotation in which one part passes through another part. Alternatively, for example, a seal may be provided on the outer surface of the piston and the piston may be moved back and forth as shown in FIG. The design of an integral elastomeric seal spring such as this ring 20 results in gradual back-up pressure on the flat bearing seal member 14 over its entire temperature range, resulting in the causing the dimensional changes experienced by metal parts such as Thus, as such components heat up, substantial dimensional changes occur such that the bearing seal member 14, which is continually squeezed outwardly by the critical dimension ring 20, is forced to move in the circumferential direction. Adjust to make corrections. This is achieved by the variation in the circumference of the bearing and sealing members allowed by the mutual movement of the free ends 18, 19. At the same time, the annular elastic ring 2
An integral resilient seal spring in the form of 0 adjusts the amount of pressure within the groove. It can be seen that the dimensions of this groove also change with temperature changes. These changes are
Dimensional changes are made to the initial structure of the shaft, groove, bearing, and ring itself, all of which are very difficult to compensate for. However, it has been found that rings having dimensions within the limits described herein successfully compensate for these variations when utilizing integrally sealed bearings such as member 14.

When such adjustment becomes necessary, the ring 20
The elastomeric material constituting the ring 20 flows into substantial recesses 21 to 24 on each side of the ring 20. Because this material flows easily but is incompressible, the present invention avoids the problems previously experienced with standard quad rings or O-rings. These rings are exposed to excessive pressure and are subject to severe wear.
These bearings and seals cannot be appropriately adjusted to support them over the temperature range experienced.

It can be seen that the ring 20 provides a complete seal over the bottom of the groove 11 as well as its top. This ring 20 thus functions as a seal and is at the same time sufficiently sensitive to maintain proper temperature control between the two relatively moving parts 10, 12 over the entire temperature range to which such equipment is subjected during operation at various high speeds. It also functions as an elastic spring to ensure the seal together with the bearing 14.

(Effects of the Invention) As is clear from the above description, the present invention provides an integrated elastic seal spring that is disposed in a seal groove to support a self-lubricating split ring type annular bearing, and a cross section of the seal spring. By specifying the shape, the relatively deep recesses formed on the opposing working surfaces and the convexities on the adjacent corners create a soft or slow pressure on the bearing member from the back side, so that the bearing can be easily sealed. Excessive fluctuations in pressure are no longer caused, and the seal spring is effective for high-speed rotation and long-term operation.

[Brief explanation of the drawing]

1 is a longitudinal cross-sectional view of a bearing with one of the integral seals/elastic springs of the present invention provided in the groove of the shaft behind the self-lubricating bearing seal; FIG. 3 is a side view of one of the seals/elastic springs; FIG. 3 is a longitudinal cross-sectional view taken along line 3--3 of FIG. 2; FIG. 4 is an enlarged cross-sectional view of the ring shown in FIGS. 2 and 3; 5 is a free-form side view of the bearing seal shown in FIG. 1; FIG. 6 is a longitudinal cross-sectional view of the bearing seal taken along line 6-6 of FIG. 5;
FIG. 7 is a plan view of the bearing seal shown in FIGS. 5 and 6. FIG. 10... High-speed rotating metal shaft, 11... Annular groove, 12...
Bearing, 14...Split ring type bearing member, 20
...Elastic spring ring, 21, 22, 23, 2
4... Concave side surface, 25, 26, 27, 28... Convex corner lobe.

Claims (1)

[Scope of Claims] 1 (a) Comprised of a uniformly elastic and flowable rubber-like material, which fits into a sealing groove of a ring-shaped configuration in supporting relationship with an annular split-ring type bearing member having inherent self-lubricating properties; (b) The annular body has a substantially right-angled polygonal cross-sectional shape, and has a pair of concave surfaces forming a space in the radial direction and a space in the axial direction. (c) the annular body has a convexly curved corner portion substantially tangentially merging with the recess in each said surface; d) one of said pair of surfaces defines a free-form working surface having a recess radius of about 24-33% of the maximum normal cross-sectional dimension between said pair of surfaces; An integrated elastic seal spring used in conjunction with a self-lubricating bearing, characterized in that the minimum cross-sectional dimension between the working surfaces is 65-75% or less of the maximum normal cross-sectional dimension between the working surfaces. 2 (a) constructed of a uniformly elastic, flowable rubber-like material and configured to fit in a sealing groove of a ring-shaped configuration in supporting relationship with an annular split-ring type bearing member having inherent self-lubricating properties; (b) the annular body has a substantially right-angled polygonal cross-sectional shape;
(c) the annular body has a pair of concave surfaces defining a radial space and a pair of concave surfaces defining an axial space; (d) one of said pair of surfaces constitutes a working surface;
The minimum dimension between its working surfaces is its maximum normal dimension.
An integral elastic seal spring for use in a self-lubricating bearing and support relationship, characterized by a 65-70% 3 (a) constructed of a uniformly elastic, flowable rubber-like material and configured to fit in a sealing groove of a ring-shaped configuration in supporting relationship with an annular split-ring type bearing member having inherent self-lubricating properties; (b) the annular body has a substantially right-angled polygonal cross-sectional shape;
(c) the annular body has a pair of concave surfaces defining a radial space and a pair of concave surfaces defining an axial space; (d) one of said pair of surfaces constitutes a working surface;
Integral elastic bearings for use in a supporting relationship with self-lubricating bearings, each having a concave radius of approximately 17-33% of the maximum normal dimension between the working surfaces, when the working surfaces are free-form. seal spring. 4. Seal spring according to claim 3, characterized in that the annular body has a substantially symmetrical cross-sectional shape. 5. A seal spring as claimed in claim 3, characterized in that the recess radius of each of said working surfaces is 27-29% of the maximum normal cross-sectional dimension between said working surfaces. 6. The seal spring of claim 3, wherein the radius of each recess in said working surfaces is approximately 28% of the maximum normal cross-sectional dimension between said working surfaces. 7. The seal spring according to claim 3, wherein the radius of the convex portion of the corner portion is approximately 16% of the maximum normal cross-sectional dimension between the working surfaces. 8. The seal spring according to claim 3, wherein the radius of the convex portion of the corner portion is approximately half the radius of the concave portion of the working surface. 9. The seal spring according to claim 3, wherein the radius of the convex portion of the corner portion is 14-16% of the maximum normal cross-sectional dimension between the working surfaces. 10. The seal spring according to claim 3, wherein the maximum axial dimension of the annular body is equal to the maximum radial dimension when the annular body is free-form. 11. Seal spring according to claim 3, characterized in that each recess of the free-form working surface has the same radius. 12 The minimum cross-sectional dimension between the concave working surfaces is:
4. A seal spring according to claim 3, wherein the seal spring is approximately 60-75% of the maximum normal cross-sectional dimension between said active surfaces. 13 The minimum cross-sectional dimension between the concave working surfaces is:
4. A seal spring as claimed in claim 3, characterized in that it is 68% of the maximum normal cross-sectional dimension between said active surfaces. (e) a support structure having an annular groove; (f) an annular split-ring bearing member supported by the support structure and disposed within the groove; (g) the bearing member having a 100-ft. is self-lubricating, with a pressure velocity value of 1800 or more at a surface velocity of /min; is provided within said annular groove, pressing against the bottom of said groove, (i) the width of said groove is slightly greater than the maximum dimension between a pair of surfaces forming an axial space; is slightly smaller than the overall radial dimension of the bearing member and the maximum normal cross-sectional dimension of the annular body, and the annular body and the bearing member are held under slight pressure. Seal spring according to item 3. 15 (e) a pair of metal members having annular mating bearing surfaces provided for high-speed relative movement and on which said movement occurs; (f) an annular groove provided in one of said surfaces; (g) an annular body having a bottom thereof; (h) a split ring type bearing member is comprised of a plastic material having inherent self-lubricating properties with a pressure velocity value of 1800 or more at a surface velocity of 100 feet per minute; (i) said bearing; a member is disposed within the groove in a supporting relationship with respect to the annular body and compresses another metal member moving relative to the groove; (j) the sum of the annular body and the bearing member; (k) the axial width of the annular body is less than the width of the groove; and (l) the minimum cross-sectional dimension between concave surfaces defining a radial space is , approximately 60-75% of the maximum normal cross-sectional dimension between said radial space surfaces. 16. A seal spring according to claim 15, characterized in that the bearing member has adjacent free ends that are movable radially and axially relative to each other. 17. The seal spring of claim 15, wherein the annular body is of substantially symmetrical cross-sectional configuration. 18. The seal spring of claim 15, wherein the radially spaced surface of the annular body has a recess radius of approximately 28% of the minimum normal radial dimension between the active surfaces. 19. Seal spring according to claim 15, characterized in that the minimum radial distance between the radial spatial surfaces of the annular body is approximately 68% of the maximum normal radial distance therebetween. 20. The seal spring of claim 15, wherein the maximum axial dimension of the seal member is essentially the same as the maximum radius of the seal member. 21 The convex curved corner portion of the annular body is
16. The seal spring of claim 15, having a radius of curvature of approximately 16% of the maximum normal radial distance between said radial space surfaces. 22 The convex curved corner of the annular body is approximately the maximum normal radial distance between the radial spatial surfaces.
characterized by having a radius of curvature of 14−16%,
The seal spring according to claim 15.