JPH01145471A - Integral type elastic seal spring - Google Patents

Abstract

PURPOSE: To become effective for high speed rotation and a long-hour drive by disposing a unitary elestomeric seal spring to a seal groove in a manner that the unitary elastomeric seal spring supports a split-ring annular bearing with self-lubrication, and by specifying a cross-sectional configuration of the seal spring. CONSTITUTION: A split-ring bearing member 14 has self-lubrication, is cut at a diagonal 17, has free ends 18, 19. When the split-ring bearing member 14 is properly pushed outward by a unitary elastomeric seal spring 20, automatic control for a size variation caused by temperature change can be conducted. Minimum radial dimension of the spring 20 between bottoms of convex sections of side surfaces 21, 22 forming space at two facing radial directions is 65 to 75% of maximum regular dimension (a distance between points 29, 30) between working surfaces. Each convex section of four sides 21 to 24 is 24 to 33% of the maximum regular radial dimension of the ring 20. Thereby variation of a size can be compensated over an entire range of temperature change generated on a part.

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 gearbox they house. It ends up. -If 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.

Advantageously, the seals located between the metal parts in the form of K1 bridges accommodate these high speed relative movements for long periods of time and can be made of recently developed materials with high inherent lubricity. For example, a bearing product sold under the trademark YESPEL, although very expensive and must be machined, performs as a 7-wheel under the conditions described above. However, this is a case where the sealing surface is gently, reliably and continuously acted on without applying excessive pressure, and if excessive pressure is applied, it will cause excessive wear. This indicates that there is no structure so far devised or known that sufficiently provides such a seal. It is a known method of providing 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. That's because there wasn't. There was 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 Besubel are already known and their self-lubricating properties have been recognized, but the inventors believe that a simple annular bearing made of such material can It was found that the difference in the expansion coefficient of As a result, we used a sprung IJ bearing that allows the circumference of the bearing to be changed.

However, it has been found that split ring bearings also do not perform well except under limited circumstances. In this case, despite the fluctuations in the initial dimensions of the installed components and the fluctuations that occur due to the generated heat, even moderate pressure that makes the sealing surface of the highly lubricated bearing act lightly but reliably and uniformly on the sealing surface , creating harmful wear conditions.

Therefore, I considered using a standard O-ring or a Ford (QUAD) IJ ring with standard dimensions and configuration, but
It turned out that none of them worked well. This is because these rings do not initially apply the proper pressure, or the bearings are over-stressed 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 inventors of the present invention have conducted numerous experiments, and have found that the bearing member has a surface speed of 100 feet/ft.
minutes 1c If it is made of a material that has inherent self-lubricating properties at pressure velocity values of 1800 or more and is configured in the form of a split ring so that it can be adjusted in the circumferential direction, and if it is made of an easily flowing material such as rubber. It has been discovered that if a resilient backup ring of appropriate critical dimensions is provided, a long-lasting and effective seal for long-term high speed motion is provided. To obtain such a seal, the cross-section is polygonal, with substantially equal transverse dimensions, convex corner ropes and opposite concave sides, the degree of concavity and convexity and the maximum and minimum radial dimensions are within critical limits. We designed an elastic backup ring with a specified value of . The backup ring is substantially symmetrical in cross-section.

The critical radial distance m between opposite radially spaced working surfaces of two rings is in the range 60-75 inches, preferably 68 inches, of the maximum radial distance of the opposite corners of one side of the rings.

The corner ropes have a convex radius of 14-1/1 inches, preferably 16 inches, with the same maximum radial distance between the corners. The recesses in the two opposing working surfaces are 17 mm apart from the above distance.
-55 inches, preferably 28 inches.

(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. The relatively deep recesses of the rotating working surfaces and the sharp protrusions of the adjacent corners create a soft or slow pressure on the back side of the bearing seal, which can be radially adjusted to reduce the pressure at the seal. Dimensional changes can be made without excessive variation.

In this way, a sufficient seal can be provided without excessive heat or wear. The rubber of the convex corner rope 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 resilient ring continues to apply a gentle pressure on the back side of the bearing cool, similar to the pressure applied during initial installation. The backup ring is approximately 1.9 to 50 bonds/
Because they are designed to provide a gentle, gradual pressure of square inches, and because this pressure is held at a substantially constant level by the rubber flow described above, sealed bearings
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 can be seen, a high speed rotating metal shaft 10 with an annular groove 11 on its outer surface faces a metal bearing member 12 surrounding the shaft 10. At this time, this axis 1
0 rotates at a high speed for a long period of time. Typically, the bearings 12 are of a different coefficient of expansion than the gold maple from which the shaft 10 is made, so that the dimensional changes resulting from high speeds and resulting increases in temperature of each of these metals will be quite different. As a result, some air gap, indicated by 13, provided between the two members j0.12 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 15. are doing. This split ring bearing member is self-adjusting and has a
Made from a self-lubricating material with a pressure velocity greater than 1800 at a face velocity of 0 ft/min. As shown in FIG. 1, it is flat, generally rectangular in cross-section, and includes a tongue 15 that extends axially outwardly and fits into an opening 16 in the shaft 10. This tongue 15 ensures that the bearing member 14 rotates together with the shaft 10 within the bearing 12.

The split ring bearing member 14 is shown in detail in FIGS. 5-7. As best shown in FIG. 7, it is cut at a diagonal 17 and has free ends 1B, 19 which are circumferentially and axially movable relative to each other. This provides automatic adjustment to dimensional changes due to temperature changes when properly pushed outward by the integral elastic seal spring of the present invention shown between the bearing 14 and the bottom of the groove 11. 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.

Disposed within the groove 11 in supporting relationship with the bearing seal 14 is one of the integral resilient seal springs of the present invention, commonly designated by the number 20. The seal spring consists of an integral annular body, usually of right-angled polygonal configuration in cross-section, and is made of a flowable 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 opposite concave sides 21,22 which are active surfaces and are radially spaced. The ring also has a pair of axially spaced concave sides 25,24. These concave sides meet in a generally normal line with the convex corner ropes of the ring identified by numbers 25-28.

A side surface 21 forming a space between two opposing radial directions.
The minimum radial dimension of ring 20, measured between the bottoms of the 22 recesses, is 60-75% of the maximum normal radial dimension between the working surfaces. This maximum radial dimension is the maximum distance between two opposite corners of the sides of the ring, for example number 2 in Figure 4.
The distance between points expressed at 9°50 is measured. The preferred range for this minimum radial dimension is 65-70% of the maximum radial dimension, with the ideal minimum radial dimension at the bottoms of opposing recesses being 68 inches of the maximum radial dimension.

The corner ropes 25 to 28 have a convexity of 14-16% of the maximum radial distance between the active surfaces 21 and 22. The preferred convexity is 16% of this maximum radial dimension. The concavity of each of the four sides 21-24 is substantial. These recesses are K IJ as already defined.
ranges from 17 to 33 inches of the maximum normal radial dimension of the ring.

The preferred range is 24-30% of the dimension, and the ideal range is 27-29% of the dimension. The preferred single dimension is 28 inches, the largest 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 performed as shown in Figure 1.
A rotation in which one part passes through another. or,
For example, an integral resilient seal spring design such as this ring 20, where the seal is on the outer surface of the piston and may be reciprocating as shown in FIG. A large back-up pressure is applied, resulting in the dimensional changes experienced by metal parts such as those described above when operated at high speeds over long periods of time. As such 1 heats up, a substantial dimensional change occurs, so that the bearing sealing member 14, which is continuously squeezed outwardly by the critical dimension ring 20, adjusts circumferentially. and 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, an integral elastic sealing spring in the form of an annular elastic ring 20 regulates the amount of pressure within the groove.

It can be seen that the dimensions of this groove also change with temperature changes.

These changes include all changes that add dimensional changes 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 is required, the elastomeric material constituting the ring 20 flows into substantial recesses 21 to 24 on each side of the ring 20;
Because it flows easily but is incompressible, the present invention avoids the problems previously experienced with standard Ford rings or O-rings. These rings are subject to excessive pressure and consequent severe wear and cannot be properly adjusted to support these bearings and seal members over the range of temperatures experienced.

It can be seen that the ring 20 also provides a complete seal over the bottom of the groove 11 as well as its top. This ring 20 thus acts as a seal while being sufficiently sensitive to keep two relatively moving parts 1 over the entire temperature range experienced by such equipment during operation at various high speeds.
It also functions as an elastic spring ensuring a proper seal with the bearing 14 between 0.12 and 0.12.

(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 so as to support a self-lubricating split-ring type annular bearing, and a cross-sectional shape of the seal spring. By specifying the This eliminates the occurrence of excessive fluctuations in the sealing spring, making it possible to provide a seal spring that 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. sticker/
3 is a longitudinal sectional view taken along line 3-3 in FIG. 2; FIG. 4 is an enlarged sectional view of the ring shown in FIGS. 2 and 3; FIG. 5 is a side view of one of the elastic springs; is a free-form side view of the bearing seal according to FIG. 1; FIG. 6 is a longitudinal cross-sectional view of the bearing seal along line 6-6 of FIG. 5; FIG. 3 is a plan view of the bearing seal shown in FIG. 10... High speed rotating metal shaft 11... Annular groove 12.
... Bearing 14 ... Split ring type bearing member 20 ... Elastic spring ring

Claims (22)

[Claims] (1) (a) made of a uniformly elastic and fluid 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, and has a pair of concave surfaces forming a space in the radial direction and a pair of concave surfaces forming a space in the axial direction. (c) the annular body has a convexly curved corner substantially tangentially merging with a recess in each of said surfaces; and (d) said pair of one of the surfaces defines a free-form working surface having a recess radius of about 24-33% of the maximum normal cross-sectional dimension between the pair of surfaces; An integrated elastic seal spring for use in a self-lubricating bearing and support relationship, characterized in that the cross-sectional dimension is 65-75% or less of the maximum normal cross-sectional dimension between the working surfaces. (2) (a) made of a uniformly elastic, flowable rubber-like material and configured to fit 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 forms a space in the axial direction with a pair of concave surfaces that form a space in the radial direction; (c) the annular body has a convexly curved corner substantially tangentially merging the recess in each said surface; (d) One of said pair of surfaces constitutes a working surface, the minimum dimension between said working surfaces being 65-70% of its maximum normal dimension.
An integral elastic seal spring for use in a supporting relationship with a self-lubricating bearing, characterized by: (3) (a) made of a uniformly elastic, flowable rubber-like material and configured to fit 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 forms a space in the axial direction with a pair of concave surfaces that form a space in the radial direction. (c) the annular body has a convexly curved corner substantially tangentially merging the recess in each said surface; (d) One of the pair of surfaces constitutes a working surface, 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. Integrated elastic seal spring for use in self-lubricating bearings and support relationships. (4) The seal spring according to claim 3, wherein the annular body has a substantially symmetrical cross-sectional shape. 5. The seal spring of claim 3, wherein 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 radius of each recess of the working surfaces is approximately 28% of the maximum normal cross-sectional dimension between the working surfaces,
The seal spring according to claim 3. (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 5, 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 radius of the convex portion of the corner portion is 14-16% of the maximum normal cross-sectional dimension between the working surfaces,
The seal spring according to claim 3. (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 has a free shape. (11) The seal spring according to claim 3, wherein each of the recesses of the free-form working surface has the same radius. (12) The seal spring according to claim 3, wherein the minimum cross-sectional dimension between the concave working surfaces is approximately 60-75% of the maximum normal cross-sectional dimension between the working surfaces. (13) The seal spring according to claim 3, wherein the minimum cross-sectional dimension between the concave working surfaces is 68% of the maximum normal cross-sectional dimension between the concave working surfaces. (14) (e) a support structure provided with an annular groove; (f) an annular split ring type bearing member supported by the support structure and provided within the groove; (g) this bearing member
is self-lubricating with a pressure velocity value of 1800 or greater at a surface velocity of 0 ft/min; and (h) the annular body supports the bearing member with one working surface compressing the bearing member. , the other working surface is disposed within the annular groove, pressing against the bottom of the groove, (i) the width of the groove is slightly larger than the maximum dimension between the pair of surfaces defining the space in the axial direction; The depth of the groove 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. The seal spring according to claim 3. (15) (e) a pair of metal members provided for high-speed relative motion and having annular mating bearing surfaces on which said motion occurs; (f)
(g) an annular body is provided in said groove at the bottom thereof; and (h) a split ring type bearing member is provided with a pressure velocity value of 1800 or more at a surface velocity of 100 feet per minute. (i) the bearing member is disposed within the groove in a supporting relationship with respect to the annular body and is movable relative to the other relative to the groove; (j) the total radial dimension of the annular body and the bearing member is slightly larger than the depth of the groove; (k) the axial width of the annular body is smaller than the width of the groove; l)
A seal according to claim 3, characterized in that the minimum cross-sectional dimension between the concave surfaces defining the radial space is approximately 60-75% of the maximum normal cross-sectional dimension between the radially spaced surfaces. spring. 16. The seal spring of claim 15, wherein the bearing member has adjacent free ends that are movable radially and axially relative to each other. (17) The seal spring according to claim 15, wherein the annular body has a 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 working surfaces. 19. The seal spring of claim 15, wherein 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 according to 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 seal spring according to claim 15, wherein the convexly curved corner portion of the annular body has a radius of curvature of approximately 16% of the maximum normal radial distance between the radial spatial surfaces. (22) The convex curved corner portion of the annular body is approximately 14-16 of the maximum normal radial distance between the radial spatial surfaces.
16. Seal spring according to claim 15, characterized in that it has a radius of curvature of %.