Dual splined shaft

Abstract

The present disclosure provides a lubricating system for a dual splined hollow shaft. A fluid dam is formed circumferentially within the hollow shaft to control the lubrication of the dual splines. The fluid dam includes a pair of sidewalls extending radially inward from the inner wall of the hollow shaft to a height defined by a top wall. A channel formed through the pair of sidewalls permits the movement of lubricant between splines of the hollow shaft. An egress port extends from the top wall of the dam through the outer wall of the hollow shaft to permit lubricant to exit the hollow shaft.

Description

FIELD OF THE INVENTION

The present invention relates to a dual splined shaft and more particularly to a lubrication system for the same.

BACKGROUND

Rotatable shafts can be coupled to gears or other shafts via a spline interface. The spline interface must be lubricated appropriately to prevent wear or galling due to fretting, vibratory loading, or other loading causing wear on the spline teeth. It is desirable to deliver enough lubrication to adequately protect the spline interface, but prevent excessive lubrication. Over lubrication requires additional pumping and storage capacity in the lubricant system, which increases system cost, creates weight penalties, and causes additional space claim requirements.

Dual splined shafts create additional challenges over single spline shafts. Because each spline must be lubricated, the splines must either have separate lubrication delivery systems or a single system must be able to deliver adequate lubrication to both ends of the shaft. Dual lubrication systems are expensive due to the redundancy and single systems tend to either over or under lubricate at least one of the splines.

One method of single source lubrication is to provide an opening in the wall of a partially hollow shaft and spray lubricating fluid toward the opening. One drawback to this type of system is that a significant amount of the lubrication will not pass through the opening because the shaft is rotating. The bigger the opening the more likely the lubricant will enter the hollow shaft, but the large opening makes it more likely that the lubricant will exit back out of the hollow shaft before moving to lubricate either of the splines. Furthermore the size of the opening is limited by the geometry of the shaft and the associated mechanical stress induced in a load bearing wall because of the large opening. If the opening is too small more lubricant is “wasted” as it hits the outer wall of the shaft and fails to enter through the opening as the shaft rotates. The present inventions provide novel and non-obvious, innovation needed in this field of technology.

SUMMARY

The present invention includes an apparatus and method for lubricating a dual splined shaft. Further embodiments, forms, features, aspects, benefits, and advantages shall become apparent from the description and figures provided herewith.

BRIEF DESCRIPTION OF THE DRAWINGS

The description herein makes reference to the accompanying drawings wherein like reference numerals refer to like features throughout the several views, and wherein:

FIG. 1 is schematic top view of a gear box having a plurality of splined shafts projecting therefrom;

FIG. 2 is a cutaway of the gear box of FIG. 1 showing a cross section of a shaft having dual spline couplings;

FIG. 3 is an enlarged perspective view of one end of the dual splined shaft with an input/output shaft engaged therewith and a lubrication nozzle spraying lubrication under a spline coupling; and

FIG. 4 is a cross sectional view of the splined coupling shown in FIG. 3.

DETAILED DESCRIPTION

For purposes of promoting an understanding of the principles of the invention, reference will now be made to the embodiments illustrated in the drawings and specific language will be used to describe the same. It will nevertheless be understood that no limitation of the scope of the invention is thereby intended, such alterations and further modifications in the illustrated device, and such further applications of the principles of the invention as illustrated therein being contemplated as would normally occur to one skilled in the art to which the invention relates.

The inventions disclosed herein includes means for lubricating a dual splined shaft i.e. a shaft having splines on opposing ends thereof. The dual splined shaft can be coupled to input/output shafts or other rotating components having mating spline connections. While the disclosed embodiment depicts female couplings or internal splined couplings on the dual splined shaft, it should be readily understood by one skilled in the art that male couplings or external splined couplings could be implemented on the dual splined shaft. Furthermore the dual splined shaft may have a combination of both a male spline and a female spline. The lubrication system including any nozzles and spray geometry may be modified to utilize a dual splined shaft with a male coupling without departing from the teachings of the present invention.

The dual splined shaft of the present invention is substantially hollow to permit lubrication fluid or lubricant to move freely between opposing ends of the shaft. One aspect provides for a shaft design with desired lubrication at the opposing coupling ends while minimizing the volume and dwell time of the lubricant within the hollow shaft. If the volume or dwell time of the lubricant in the dual splined shaft is more than the required amount then the lubrication system will not be optimized. This non-optimization requires larger volume oil sumps and higher capacity pumps which in turn leads to space claim and weight penalties—all which translates into higher system costs. The present invention ensures that both splines are adequately lubricated and that lubricant is expelled at a desired rate to prevent excess lubricant from building up within the hollow shaft.

For purposes of this disclosure lubricating fluid can include any common or non-common lubricant known to those skilled in the art. In one example the fluid can be a carbon based mineral oil, in another example the fluid can be a synthetically produced lubricant, and in other examples the fluid can combinations of natural made lubricants and man made lubricants.

Referring to FIG. 1, a schematic representation of a gear housing 10 having a plurality of shafts 12, 13, and 15 extending therefrom is illustrated. Each of the shafts 12, 13, 15 can include a spline coupling 14 on the ends thereof. While a gear housing is illustrated in the example embodiment, it should be understood that the present invention can be utilized with any shafting or gear configuration in which it would be advantageous to use a dual splined shaft. Material selection for the shafts, gears, splines and other rotating components disclosed herein are generally known to those skilled in the art. Materials may include, but are not limited to metals, ceramics, composites, plastics and any combination thereof.

Referring now to FIG. 2, the gear housing 10 can have a dual splined shaft 16 operable to transmit rotation or torque between the pair of splined shafts 12, 13. The splined shafts 12, 13 can be input shafts, output shafts or any other rotating component such as gears and the like. The dual splined shaft 16 includes a first end 18 having a first splined coupling 20 and a second end 22 having a second splined coupling 24. The dual splined shaft 16 has a substantially hollow core 26 to permit lubricating fluid to internally travel along the length of the shaft 16 between the first and second spline couplings 20, 24.

The shaft 16 includes a fluid dam 28 protruding radially inward from an inner wall 30. The fluid dam 28 can extend circumferentially around the entire inner wall 30. The fluid dam 28 includes a pair of sidewalls 27, 29 extending radially inward toward a top wall 36. At least one channel 32 extends through the sidewalls 27, 29 and can be positioned at a sufficient depth such that lubricating fluid can flow past the fluid dam 28 through the at least one channel 32. In one form the depth of the channel 32 is substantially flush with the inner wall 30 of the hollow shaft 16. At least one fluid egress port 34 extends from the top wall 36 of the dam 28 through an outer wall 38 of the shaft 16 to permit lubricating fluid to egress out of the dual splined shaft 16.

First and second seal assemblies 42, 43 are positioned adjacent the first and second ends 18, 22, respectively of the shaft 16. The seal assemblies 42, 43 restrict lubrication fluid from exiting the dual splined shaft 16 through the ends thereof. The seal assemblies 42, 43 can include a fluid seal 45 such as an o-ring or the like to seal an interface portion of the inner wall 30 of the dual splined shaft 16 with the coupled shafts 12, 13. The seal assemblies 42, 43 are preferably a single continuous component mounted on the coupled shafts 12, 13 prior to installation, but alternatively embodiments can include multi-piece construction that can be installed after the shafts 12 and 13 are coupled with the dual splined shaft 16 as one skilled in the art would readily understand. The first seal assembly 42 includes at least one ingress port 40 for permitting lubricating fluid to enter into the shaft 16 and lubricate the splined couplings 20, 24. In one non-limiting embodiment the ingress port 40 includes a plurality of elongated slotted apertures formed under the O-ring or seal portion 45 of the seal assembly 42 (best seen in FIG. 3). Because of the centripetal acceleration force due to high speed rotation of the shaft 16, the lubricating fluid will move radially outward toward the inner wall 30 of the shaft 16 and will be restricted from flowing past the seals 45 of the seal assemblies 42, 43.

Referring now to FIGS. 3 and 4, the first end 18 of the shaft 16 is illustrated with a nozzle 48 directing a spray 49 of lubricating fluid toward the ingress port 40. The nozzle 48 can spray lubricating fluid substantially in the direction along the axis of rotation X. The lubricating fluid enters through the ingress ports 40 as the dual splined shaft 16 is rotating. The port 40 permits lubricating fluid to pass under the seal 45 of the seal assembly 42 and into the spline coupling 20. The seal 45 of the seal assembly 42 substantially restricts the lubricating fluid from escaping back out through the first end 18 of the shaft 16. The lubricating fluid then flows through the splined coupling 20 connecting the coupled shafts 16 and 12 to one another. After the lubricating fluid passes through and lubricates the splined coupling 20, the lubricating fluid traverses into the hollow portion of the shaft 16.

As described above, because the dual splined shaft 16 rotates at a relatively high speed the lubricating fluid in the hollow portion will move toward the surface of the inner wall 30 (best seen in FIG. 2). As the lubricating fluid continues to flow into the hollow portion of the shaft, the fluid will pass across the dam 28 via the at least one channel 32. When the hollow shaft 16 is partially filled with lubricating fluid, the fluid will move to the second end 22 and lubricate the second splined coupling 24. The lubricating fluid is prevented from escaping past the coupling 24 at the second end 22 because the seal 45 of the second seal assembly 43 (see FIG. 2) forms a fluid tight connection between dual splined shaft 16 and the coupled shaft 13. The lubricating fluid will continue to build up along the inner wall 30 of the rotating shaft until it rises above the top wall 36 of the dam 28. After the lubricating fluid reaches the height of the top wall 36, any additional fluid entering the hollow shaft 16 will cause the lubricating fluid to exit through the egress ports 34 and flow back to a fluid sump (not shown). During operation, the height of the dam 28 will control the amount of lubricating fluid retained in the hollow shaft 16 and the number and size of the egress ports 34 will control how fast the lubricating fluid is expelled from the hollow shaft 16. At shutdown, lubricating fluid can egress through the inlet ports 40 because the centripetal force has been removed. In this manner both spline couplings 20, 24 of the dual splined shaft 16 will be adequately lubricated and the quantity of lubricating fluid disposed within the hollow shaft 16 is controlled by the dam 28 during operation.

While the invention has been described in connection with what is presently considered to be the most practical and preferred embodiment, it is to be understood that the invention is not to be limited to the disclosed embodiment(s), but on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims, which scope is to be accorded the broadest interpretation so as to encompass all such modifications and equivalent structures as permitted under the law. Furthermore it should be understood that while the use of the word preferable, preferably, or preferred in the description above indicates that feature so described may be more desirable, it nonetheless may not be necessary and any embodiment lacking the same may be contemplated as within the scope of the invention, that scope being defined by the claims that follow. In reading the claims it is intended that when words such as “a, an,” “at least one” and “at least a portion” are used, there is no intention to limit the claim to only one item unless specifically stated to the contrary in the claim. Further, when the language “at least a portion” and/or “a portion” is used the item may include a portion and/or the entire item unless specifically stated to the contrary.

Claims

1. An apparatus comprising: a hollow rotatable shaft having an inner wall and an outer wall; first and second splines associated with opposing ends of the shaft; a fluid dam formed within the hollow shaft, the fluid dam having a pair of sidewalls extending radially inward from the inner wall of the hollow shaft to a height defined by a top wall connecting the sidewalls; at least one channel formed through the pair of sidewalls; and at least one egress port extending from the top wall of the dam through the outer wall of the hollow shaft, wherein the bottom of the channel is substantially flush with the inner wall of the hollow shaft.