JPH0461968B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to an effective bearing assembly for a metal shaft rotating at very high speeds while being lubricated within a metal bushing.

Disclosure of the Invention The bearing is formed of a self-lubricating material having a pressure rate value of at least 1800 psi at a surface velocity of 100 feet per minute to adequately lubricate the wear surfaces between the bearing and the shaft. Also, to minimize cost, such materials must be moldable.

The bearing is discontinuous or split to compensate for changes in shaft diameter caused by temperature changes caused by high speed rotation.

This bearing is pressed into constant contact with the shaft by a sealing ring. This seal ring design is sensitive to and highly tolerant of pressure changes. The sealing ring is thus able to compensate for the normally large manufacturing tolerances of the groove in which it is mounted and for variations in the diameter of the shaft.

Embodiment One preferred embodiment of the invention is shown in FIGS. 1-7. The bearing assembly has a self-lubricating annular bearing member comprised of a molded, discontinuous split ring. It serves as a bearing surface for the shaft and also functions as a double bearing in that it compensates for the difference in expansion coefficients of steel and brass and eliminates excessive wear of the sealing members. The seal ring acts as an elastomeric spring.

The bearing member is preferably formed from a thermoplastic material, although thermosetting materials may also be used. Examples include unmodified polycarbonate and polystyrene. These two materials work well at low speeds and pressures. For cost reasons, the bearing must be moldable. That means that it must be injection moldable or moldable via transfer molding. To be cost effective, 6/10 nylon with modifiers would be most desirable for long run use. Others, polyethylene,
Materials such as polypropylene, styrene and polyvinylchlorene can also be used. Importantly, the material is moldable and pressure-free.
If the velocity value is a surface velocity of 100 feet per minute,
Must be over 1800psi.

Figures 1-7 show this bearing assembly with the shaft 15 rotating about its axis at high speed within the bronze bushing 16. The upper end of the shaft and bushing terminates in a gearbox (not shown) containing lubricant to lubricate the shaft. axis 1
5, a spindle collar 17 is press-fitted and abuts against the upper end of the bushing 16. steel nut 18
extends around the spindle collar 17, which is typical in batting machines.

The bearing member 20 has a generally L-shaped cross section. Portion 21 has a radial outer circumferential dimension that is substantially equal to the depth of groove 19, and portion 22 has a smaller radial dimension. The bearing member 20 has a sealing surface 20a on its inner diameter, thereby completing a seal around the shaft 15. The axial width of the bearing member 20 is slightly smaller than the axial width of the groove 19 .

To prevent the bearing member 20 from rotating with the shaft 15, a tongue member 23 extends axially into an opening 24 formed in the bearing 16. two parts 21,
22 forms a second groove 24 and includes a seal ring 25 therein.

Bearing member 20 is otherwise uniform in cross-sectional shape and has an axial length of approximately . It is 140 inches (3.556mm). The radial thickness dimension of portion 22 is approximately. 030 inches, and the radial thickness dimension of portion 21 is approximately .030 inches. 059〜． 065 inches.

The inner diameter of the seal is. It is 488 inches. Tongue piece 23
The outer width of the bearing member portion 22, which has a smaller radial dimension, has an outer width of approximately . It is located at 100 inches. The axial dimension of portion 22 is approximately. It is 070 inches.

Bearing member 20 comprises a split ring, the split being indicated at 26 in FIG.
The edges can thus be adjusted.

Seal ring 25 is made of a uniformly resilient flowable rubber-like material, which is typically an elastomer. The ring 25 has a rectangular polygonal cross section and has equal radial and axial dimensions. It is symmetrical and perfectly even.
Each side is concave and each corner has a rounded protrusion 2
It has become 7. The recess between the two protrusions has a radius of curvature that is approximately 28% of the largest dimension of the cross-section of the ring. The depression 28 is a rounded protrusion 27
and are tangentially connected.

The maximum radial thickness of the ring 25, when combined with the radial thickness of the bearing member portion 22, is slightly larger than the radial depth of the second groove 24. Thus, the bearing member 20 is the ring 25
is slightly compressed in the radial direction.

Ring 25 is continuous and has a perfectly uniform cross section. Projection 27 with rounded corners
The radius of is approximately 16% of the maximum radial dimension of the ring
It is. The inner diameter is approx. Rings such as those that are 0.048 inches work very satisfactorily. The minimum radial thickness dimension between opposing recessed surfaces 28 of such a ring is approximately . 036 inches. The radius of curvature of the recessed portion 28 is approximately. The radius of curvature of the rounded protrusion 27 is approximately .016 inch. 008 inches.

The ring 25 does not necessarily have to have a square cross section. Alternatively, the groove can be made axially longer and the ring can be longer axially, such as shown at 30 in FIG. The radial thickness of the ring 30 and the radial thickness of the bearing member portion with which it comes into contact are slightly larger than the radial depth of the groove.

The axial width of the ring 30 is slightly less than the axial width of the groove when adding the axial dimension of the bearing member portion extending therealong.

Figures 9-12 show the same bearing as in the previous example, except that it is configured to provide a complete seal on the outer diameter of the bearing. Therefore, as shown in FIGS. 9 and 10, it is the outer periphery that has the largest axial dimension. A portion with a small thickness in the radial direction is indicated by the reference numeral 32, and a portion with a large thickness in the radial direction is indicated by a reference numeral 33.
Indicated by Thus, portion 32 has a smaller radial thickness and a larger axial width than portion 33. The seal is not on the inner diameter of member 31, but on the outer diameter. It is otherwise the same as the previous example except that its bearing rotates with the shaft 34.

A groove 35 is formed in the shaft that rotates within the bushing 36. The bearing 31 is located within the groove,
Portion 32 completes the seal at 38 to bearing 36.

The seal ring 39 has the same dimensions and the same relationship as the second groove 40 as the inner diameter seal of FIG.
The sealing ring 39 has a radial dimension that holds the portion 32 in compression with the inner surface of the bushing 36. Reference numeral 40 indicates a collar and 41 indicates a steel nut.

Bearing member 31 is split-shaped, as shown at 42 in FIG. The ring 39 is the bearing member 31
The bearing is held in compression against the inner surface of the bushing 36 to ensure a complete seal between the bushing 36 and the bushing 36. It also has a smaller axial dimension than the groove 37 and abuts the portion 33.

During operation, the elastomeric spring members 25, 31
holds the bearing member in compression against the surface to which the seal is to be made. This is the bearing surface with the longer axial dimension. By using bearings such as those described here, lubricant losses are greatly reduced, and wear is also greatly reduced, resulting in less downtime and much less part replacement. be able to. The lubricant is contained within the gearbox and the bushing retains lubrication for a longer period of time than in the past. Since the rings 25, 39 maintain a slight pressure on the bearing member at all times, their inherent self-lubricating properties provide maximum effectiveness. This creates an effective seal that reduces wear and prevents lubricant from leaking.

The rings 25, 39 are very flexible and easily compensate for dimensional changes caused by temperature changes in the rotating parts. The assembly of the invention greatly extends the useful life of machines already in use in this field.
In the future, structures similar to this will be utilized by the manufacturer of this original device to greatly improve such machines while extending their useful life.

[Brief explanation of drawings]

1 is a partial vertical sectional view of the bearing assembly of the present invention, FIG. 2 is a vertical sectional view taken along line 2-2 in FIG. 3, FIG. 3 is an end view of FIG. 2, and FIG. The figure is the third
5 is a vertical sectional view taken along line 5-5 in FIG. 6, FIG. 6 is an end view of the seal ring at the rear of the bearing, and FIG. 7 is shown in FIG. 5. 8 is a vertical sectional view of a seal ring with a modified cross section; FIG. 9 is a partial vertical sectional view of a different but similar bearing assembly; FIG. 10 is a vertical sectional view of a different but similar bearing assembly; 11 is an end view of the bearing member shown in FIG. 10, and FIG. 12 is a plan view of the bearing member shown in FIGS. 10 and 11. 15,34...Shaft, 16,36...Butching, 17,40...Spindle collar, 18,4
1... Steel nut, 19... Groove, 20... Bearing member, 21, 22, 32, 33... Bearing member part,
23... tongue piece member, 24, 40... second groove, 2
5, 30, 39... Seal ring, 26, 42...
...Split, 27...Rounded corner protrusion, 28...Indentation, 35...Shaft groove.

Claims (1)

[Scope of Claims] 1 (a) a shaft configured and arranged to rotate at a high speed about its axis; and (b) supported by and secured in a sealing relationship surrounding said shaft. (c) a bushing rotatably supporting said shaft for rotation about said axis and terminating in proximate but spaced relation to said collar; (d) a bushing rotatably supporting said shaft for rotation about said axis; (e) a housing enclosing and supporting a bushing and cooperating with the collar and one end of the bushing to form an annular groove about the shaft, extending beyond the bushing into close contact with the collar; At least at a surface speed of 100 feet per minute
a molded discontinuous split ring self-lubricating annular bearing member formed of a moldable self-lubricating material having a pressure velocity value equal to 1800 psi; (f) said bearing member having a generally L-shaped transverse shape; having the shape of a surface, a portion thereof having a smaller radial thickness dimension than the remainder thereof, and an axial width dimension substantially equal to the width dimension of the groove, and being located within the groove; (g) a seal ring made of a uniform elastic-flowable rubber-like member mounted in the groove in surrounding relation to the portion of the bearing member having a smaller thickness dimension; (i) the inner circumference is substantially equal to the outer circumference of the bearing member portion having the smaller thickness, and (i) the axial width of the bearing member portion having the greater thickness and the seal ring; (j) the thickness of the bearing member with the smaller thickness and the seal ring in a free form without being constrained; The combination of the thickness dimension slightly exceeds the depth dimension of the groove, so that the seal ring and the smaller thickness dimension exert a slight radial compression around the axis. a bearing assembly comprising: a bearing assembly; 2 (a) at least at a surface velocity of 100 feet per minute.
(b) a formed discontinuous split ring self-lubricating bearing member formed of a formable self-lubricating material having a pressure velocity value equal to 1800 psi; (b) said bearing member having a general cross-sectional shape; (c) being substantially uniformly generally L-shaped throughout, one axial portion thereof having a radial thickness less than the remaining portion thereof, and having an annular seal ring engagement surface; It is made of a uniform elastic-flowable rubber-like member, is attached to form an engaging relationship with the seal ring engagement surface of the bearing member, and extends entirely along the surface, and furthermore, one part of the outer circumferential surface thereof. (d) said seal ring has a radial thickness equal to one of the outer circumferential surfaces of said bearing member portion when said bearing member portion is in an unrestrained free form; (e) said sealing ring has a substantially right-angled polygonal cross-sectional shape and includes a pair of opposed radially spaced recessed working surfaces and a pair of axially spaced recessed working surfaces; (f) said sealing ring, when in its unconstrained free form, has a convexly curved surface that connects in a continuous arc with the indentation of said surface; (g) a support structure including a pair of opposing surfaces, one of the surfaces configured and arranged to move rapidly relative to the other; (h) forming a first annular groove in one of the surfaces surrounding the bearing member and the seal ring, through which the bearing member and the seal ring extend; The sum of the axial width of the seal ring and the axial width of the thick portion of the bearing member is shorter than the width of the groove; The dimension of the radial cross section is the maximum when in a free form, and that dimension, when added to the thickness dimension of the thinned part of the bearing member, slightly exceeds the depth dimension of the groove. , when they are placed in the grooves, they are in a slightly radially compressed state; and (j) said bearing member has an axially extending sealing surface, said sealing surface being in said compressed state. being gently pressed radially within said groove toward its opposing surface by a seal ring located in said groove to complete a seal across said groove. 3(k) further comprising a locking device supported by the bearing and extending axially therefrom to lock the bearing against movement relative to the support structure; A bearing assembly according to claim 2. 4. The bearing assembly of claim 2, wherein the width dimension of the seal ring is greater than its radial wall thickness dimension when it is in its unconstrained free form. 5. The bearing member and the support structure cooperate to form a second annular groove, the width of which is longer than the depth thereof, and the seal ring is disposed within the groove. 3. The bearing assembly of claim 2. 6 (a) At least at a surface velocity of 100 feet per minute.
a shaped discontinuous split ring self-lubricating bearing member formed of a moldable self-lubricating material having a pressure velocity value equal to 1800 psi; (b) said bearing member having a generally L-shaped transverse shape; (c) formed of a uniform elastic-flowable rubber-like member, a portion of which has a smaller thickness than the remainder of the bearing member; (d) a seal ring mounted in radially pressing relationship with the seal ring, one of the radial thickness dimensions of which is substantially equal to the dimension of the surface of the bearing member portion abutting the seal ring; the seal ring has a substantially right-angled polygonal seal ring, further having a pair of radially spaced recessed actuating surfaces and a pair of axially spaced recessed surfaces; (e) the seal ring, when in its unconstrained free form, has a convexly curved corner portion that connects in a continuous arc with the recess of the recessed surface; (f) the bearing member; and the seal ring, forming a first annular groove within which the bearing member and the seal ring extend; (g) the bearing member and the groove have axial dimensions; (h) the radial depth of the groove is substantially equal to the maximum radial dimension of the cross-section of the bearing member; and (i) the axial width of the groove; (j) is slightly larger than the sum of the maximum width in the axial direction of the cross section of the seal ring in its unconstrained form and the width of the bearing member having the larger thickness; The seal ring, when in its unrestrained free form, has a maximum thickness dimension in the cross section, which dimension when combined with a thickness dimension of the bearing member portion having a smaller radial dimension; a bearing assembly that is slightly larger than a depth dimension of the groove and that is subjected to a slight compressive force in a radial direction when placed within the groove. 7. Claim 6, wherein the seal ring surrounds the outer periphery of the bearing member portion having a small thickness dimension and has an inner diameter slightly smaller than the outer periphery.
Bearing assembly as described in . 8. the bearing member and the support structure cooperate to form a second annular groove therebetween, and the seal ring extends within the second groove and defines a cross-sectional area in an unconstrained manner of the seal ring. 7. The bearing assembly of claim 6, wherein a maximum radial thickness dimension of the second groove is slightly greater than a depth dimension of the second groove. 9 the bearing member and the support structure cooperate to define a second annular groove therebetween, the sealing ring extending within the second groove; The maximum thickness dimension in the radial direction of the cross section is slightly larger than the depth dimension of the second groove, and the maximum width dimension in the axial direction of the seal ring in an unrestrained state is less than the width dimension of the second groove. Bearing assembly according to claim 6, characterized in that it is small. 10 The bearing member portion having a small radial thickness dimension is about. 030~. 060 inch (0.762~1.524
7. A bearing assembly according to claim 6, characterized in that it has a thickness dimension of cm). 11 (a) a shaft member configured and arranged to rotate at a high speed around its axis; and (b) a lubricating fluid surrounding said shaft and surrounding and lubricating said shaft member during rotation of said shaft. (c) the housing member and the shaft member are configured and arranged to cooperate to form an annular groove therebetween; (d) At least at a surface velocity of 100 feet per minute
a molded discontinuous split ring self-lubricating annular bearing member formed of a moldable self-lubricating material having a pressure velocity value equal to 1800 psi; (e) said bearing disposed within said annular groove; (f) having a portion having a maximum width dimension substantially equal to the width dimension of the groove and extending in surrounding relation to the shaft member and in sealing contact with one of the members; (f) the bearing; has a greater radial thickness in one axial portion than the other portion and a substantially uniform cross-sectional shape throughout; (g) a flowable rubber-like material of uniform elasticity; axially facing and abutting the bearing portion formed of a member and having a reduced radial thickness and mounted in the groove, cooperating therewith to form a seal between the shaft member and the housing member; (h) the seal ring extends within the groove along the side of the radially thickened portion of the bearing; (i) the width dimension of the seal ring is , when the axial dimension of the thick walled portion of the bearing is added, it is smaller than the width dimension of the groove; (j) the thickness dimension of the thin walled portion of the bearing and the seal ring in an unrestrained state; plus the radial thickness dimension is slightly larger than the depth dimension of the groove, so the seal ring and the thin walled portion are subjected to a slight radial compressive force within the groove. a bearing assembly, wherein the seal between the housing member and the shaft member is thereby completed and maintained.