LUBRICATION SYSTEM FOR PORTABLE PIPE THREADER

A portable pipe threader includes a housing, a carriage supported by the housing, at least one pipe threading tool coupled to the carriage and selectively operable to perform work on a pipe, a drive assembly at least partially positioned within the housing including an electric motor operable to provide torque to the pipe, and a lubrication system removably coupled to the housing, the lubrication system including a reservoir for holding a lubricant and a pump supported upon the reservoir and configured to draw the lubricant from the reservoir, the pump being powered by the drive assembly.

FIELD OF THE INVENTION

The present invention relates to pipe threaders, and more particularly to lubrication systems for portable pipe threaders.

BACKGROUND OF THE INVENTION

Portable pipe threaders include a stand and a carriage mounted to the stand having multiple pipe threading tools. These tools are usually a die holder including a die, a pipe cutter, and a pipe reamer. Typically, a motor transmits torque to a chuck. A pipe is clamped within the chuck and as the motor rotates the chuck, the pipe rotates with respect to the tools. The motor is an AC motor that receives power from a remote power source (e.g., via a power cord) and is usually controlled using a pedal, which upon actuation, triggers the motor to begin rotating the chuck and the pipe therein to cut the pipe, thread the pipe, etc. During threading operations, the thread-cutting dies, or other pipe threading tools, require lubrication to minimize friction and prevent excessive heat on the pipe and the tool. Some portable pipe threaders have an onboard lubrication system to lubricate the dies as the threads are being cut on the pipe, while others rely upon the operator to manually lubricate the dies with a hand-operated pump.

SUMMARY OF THE INVENTION

The present invention provides, in one aspect, a portable pipe threader including a housing, a carriage supported by the housing, at least one pipe threading tool coupled to the carriage and selectively operable to perform work on a pipe, a drive assembly at least partially positioned within the housing and including an electric motor operable to provide torque to the pipe, and a lubrication system removably coupled to the housing, the lubrication system including a reservoir for holding a lubricant and a pump supported upon the reservoir and configured to draw the lubricant from the reservoir, the pump being powered by the drive assembly.

The present invention provides, in another aspect, a portable pipe threader including a housing, a carriage supported by the housing, at least one pipe threading tool coupled to the carriage and selectively operable to perform work on a pipe, a drive assembly at least partially positioned within the housing and including an electric motor operable to provide torque to the pipe, and a lubrication system including a reservoir coupled to the housing. The lubrication system further includes a valve positioned within an inlet of the reservoir, and a basin positioned beneath the carriage having an inclined bottom wall for directing lubricant toward the reservoir when the valve is actuated from an open position, in which lubricant may flow through the reservoir inlet and into the reservoir, and a closed position, in which lubricant is prevented from exiting the reservoir through the reservoir inlet, in response to removal of the reservoir from the basin.

The present invention provides, in yet another aspect, a portable pipe threader including a housing, a carriage supported by the housing, at least one pipe threading tool coupled to the carriage and selectively operable to perform work on a pipe, a drive assembly at least partially positioned within the housing and including an electric motor operable to provide torque to the pipe, and a lubrication system removably coupled to the housing, the lubrication system including a reservoir for holding a lubricant and a pump powered by the drive assembly. The portable pipe threader further includes a stand adjustable between a collapsed state and a deployed state, and, when in the collapsed state a longitudinal axis of the housing is maintained at a first oblique angle relative to a horizontal reference plane parallel with a work surface upon which the stand is supported to funnel lubricant toward the reservoir and in the deployed state the longitudinal axis of the housing is maintained at a second oblique angle relative to the horizontal reference plane parallel with the work surface upon which the stand is supported to funnel lubricant away from an end of the pipe on which a working operation is performed.

DETAILED DESCRIPTION

With reference toFIG. 1, a portable pipe threader10includes a stand100and a main housing51supported on the stand100, and a carriage42supported on the main housing51having a plurality of pipe threading tools46,50,54supported by the carriage42. The pipe further includes a drive assembly18housed within the main housing51and mounted to the stand100having a motor22(e.g., a brushless direct current electric motor), a gear box26coupled to the motor22having an output gear (not shown), an electronic speed selection switch, such as a pedal30, that selectively controls the drive assembly18, and a plurality of guide rails45configured to support the carriage42. The drive assembly18is powered by a battery pack38supported by the stand100in selective electrical communication with the motor22to provide electrical power to the motor22. In some constructions, the battery pack38and the motor22can be configured as an 18 Volt high power battery pack and motor, such as the 18 Volt high power system disclosed in U.S. patent application Ser. No. 16/045,513 filed on Jul. 25, 2018 (now U.S. Patent Application Publication No. 2019/0044110), the entirety of which is incorporated herein by reference. In other constructions, the battery pack38and the motor22can be configured as an 80 Volt high power battery pack and motor, such as the 80 Volt battery pack and motor disclosed in U.S. patent application Ser. No. 16/025,491 filed on Jul. 2, 2018 (now U.S. Patent Application Publication No. 2019/0006980), the entirety of which is incorporated herein by reference. In such a battery pack38, the battery cells within the battery pack38have a nominal voltage of up to about 80 V. Further, in another embodiment, the battery cells within the battery pack38have a nominal voltage of up to about 120 V. In some embodiments, the battery pack38has a weight of up to about 6 lb. In some embodiments, each of the battery cells has a diameter of up to 21 mm and a length of up to about 71 mm. In some embodiments, the battery cells within the battery pack38are cylindrical battery cells, prismatic battery cells, pouch battery cells, or a combination thereof. In some embodiments, the battery pack38includes up to twenty battery cells. In other embodiments, the battery pack38includes up to thirty battery cells, up to forty battery cells, up to forty-five battery cells, or greater. In some embodiments, the battery cells are disposed in a single pack. In other embodiments, the battery cells are disposed in multiple packs, i.e., two packs, three packs, four packs, etc. In some embodiments, the battery cells are connected in series. In some embodiments, the battery cells are operable to output a sustained operating discharge current of between about 20 A and about 140 A, for example, about 40 A and about 60 A. In some embodiments, each of the battery cells has a capacity of between about 1.7 Ah and about 15.0 Ah. And, in some embodiments of the motor22when used with the 80 Volt battery pack38, the motor22has a power output of at least about 2760 W and a nominal outer diameter (measured at the stator) of up to about 80 mm, up to about 100 mm, up to about 120 mm, up to about 140 mm, or greater.

With reference toFIG. 1, the drive assembly18further includes a drive element34(e.g., a drive tube) coupled to the gear box26and powered by the motor22. The motor22is configured to supply torque to the output gear of the gear box26and rotatably drive the drive element34to rotate a pipe (not shown) or a selected one of the plurality of pipe threading tools. The pedal30is operable to activate the motor22and control a relative speed at which the pipe rotates. In other embodiments, the relative speed at which the pipe rotates can be selected using an electronic speed selection switch other than the pedal30(e.g., dial, keypad, button, etc.; not shown).

With continued reference toFIG. 1, the portable pipe threader10further includes a spindle60in which the pipe is clamped. The drive element34interconnects the spindle60and the output gear of the gear box26. Thus, torque from the motor22is transferred to the spindle60, causing it and the pipe to rotate, via the gear box26and the drive element34. With reference toFIG. 1, the plurality of pipe threading tools46,50,54includes a die holder46having a plurality of dies (not shown) to cut threads on the pipe, a pipe cutter50to trim excess pipe, and a pipe reamer54to deburr, or otherwise smooth, an inner edge of a cut end of a pipe. The plurality of pipe threading tools46,50,54remain stationary on the carriage42while the pipe is rotated by the spindle60. The portable pipe threader10also includes a lubrication system200(FIG. 2) configured to provide lubricant to the pipe during a threading operation using the die holder46and a particular die (not shown) installed therein.

With continued reference toFIG. 1, the stand100includes an upright portion168configured to support the threader10and a stand locking mechanism120for selectively locking the stand100in a deployed state (FIG. 1) and a collapsed state (FIG. 9). The stand100further includes a plurality of first and second support legs110,160pivotably coupled via rotatable joints170(e.g., bolts, screws, etc.), an axle165pivotably coupled to the second support legs160having a plurality of wheels130, a plurality of list-assist springs125for aiding the stand100from moving from the collapsed state to the deployed state, and a handle assembly135integrated with the first support legs110having feet portions140to support the threader10in the deployed state where the threader10is elevated from a work surface105during use. The handle assembly135further includes grip portions150for the user to grasp the stand100during transport of the threader10and loading skis155coupled to the first support legs110for allowing the stand100to travel more easily over difficult surfaces when it is being transported (e.g., being pulled up stairs).

FIG. 2illustrates the lubrication system200for use with the threader10. The lubrication system200is removably couple to, or engaged with, the housing51of the threader10. As shown, the system200includes a catch basin210having a shroud215for collecting the lubricant that is sprayed from the pipe as it is undergoing work from one of the pipe threading tools46,50,54, a plurality of brackets220for selectively mounting the system200to the guide rails44, and a debris shield235(FIG. 1) for allowing lubricant to pass into the basin210while preventing larger debris (i.e., metal chips) from passing through. The system200further includes a reservoir240positioned underneath the basin210for collecting lubricant, a pump assembly300mounted to the basin210via a mounting aperture305in one of the brackets220(FIG. 4), a drain245having a drain cap250positioned at lower portion of the reservoir240, and a seal260positioned between the basin210and the reservoir240to seal the basin210and the reservoir240to prevent leakage. During use of the system200, the basin210is configured to be slightly inclined downward along the guide rails44and away from the main housing51in order to direct the lubricant away from the pipe and into the reservoir240.

With reference toFIGS. 2-4, the pump assembly300includes a pump housing310, a pump drive shaft320extending from the housing310, a positioning spring325surrounding the drive shaft320for guiding the alignment of the shaft320, a plurality of bearings330for supporting the drive shaft320, and a plurality of bearing cups335for housing each of the respective bearings330. The pump assembly300further includes a lip seal350positioned between the drive shaft320and the housing310for sealing the drive shaft320with respect to the pump housing310, a pump intake355for drawing lubricant from the reservoir240, a pump outlet345(FIG. 2) for fluidly coupling a hand-held oiling system or an onboard oiling system integrated with the pipe threader10, and a fastener340for limiting the travel freedom of the housing310to the basin210(via the bracket220).

When the lubrication system200is mounted to the guide rails44, the positioning spring325is configured to facilitate the alignment of the pump drive shaft320with a gearbox output27for rotatably driving the pump315. The gearbox output27is configured to be selectively rotatably driven by the gearbox26in order to let the user cycle between powering just the pump assembly300, just the threader10, or both the pump assembly300and the threader10simultaneously. To further aid in the alignment of the drive shaft320with the gearbox output27, the positioning spring325allows the assembly300to rotate in any direction within the mounting aperture305. Furthermore, sufficient clearance exists (e.g., 2 mm) between the mounting aperture305and the bearing cup335to permit the pump housing310to translate in one or more directions relative to the bracket220to easily pilot the drive shaft320into the gearbox output27.

FIG. 3Billustrates a flexible guide shaft323that can replace the rigid drive shaft320in some embodiments of the pump assembly300. The flexible drive shaft323is configured to ensure proper alignment with the gearbox output27when the system300is mounted to the guide rails44. Additionally, the flexible drive shaft323can reduce the stresses that could be transmitted from the shaft323to the pump assembly300due to poor alignment with the gearbox output27. The flexible drive shaft323is formed from a wire wound into a helix and this configuration allows the flexible drive shaft323to be bendable in all directions, as indicated by arrows326a,326brelative to a center axis324of the flexible drive shaft323in its relaxed, straight configuration. For example, the free end323aof the flexible drive shaft323is bendable up to and including ninety degrees (90°) relative to the fixed end323bof the flexible drive shaft323in any direction from the center axis324.

With continued reference toFIGS. 2-4, the lubrication system200is configured to be completely modular, meaning that the entire system200is selectively mountable to the guide rails44such that when the system200is removed, the system200becomes a closed system, effectively sealing off both the pump assembly300and the gearbox output27, thereby preventing any oil leak paths from the system200or to the gear box26. Since the system200is removable, this gives the user the option to remove the system200when the application of lubricant to the pipe is unnecessary. Also, this allows the user to selectively reduce the weight of the threader10during transport or when the user is adjusting the threader10between the collapsed and deployed states. Additionally, the lubrication system200is only operable while the system200is mounted to the threader10and the drive shaft320receives torque from the gearbox output27, which reduces unnecessary wear on the pump315and the gearbox26.

FIGS. 5-8illustrate a lubrication system400for use with another embodiment of the threader10. The lubrication system400is configured as an integrated system being partially housed within the housing51of the threader10. The system400includes a basin410having a plurality of mounting brackets430for mounting the basin410to the guide rails44, a shroud portion415movable relative to the basin410along guide grooves412for collecting the lubricant that is sprayed from the pipe as it is undergoing work from one of the pipe threading tools46,50,54, and a debris shield435(FIG. 6) for collecting larger debris (i.e., metal chips) and preventing such debris from flowing into a drain440located at a lower portion of the basin410.

The lubrication system400further includes a valve assembly500for fluidly coupling the drain440to a reservoir420housed within the housing51of the threader10. The valve assembly500is also configured to seal the reservoir420when the reservoir420is removed, or otherwise disengaged, from the basin410and removed from the threader10. The valve assembly500includes a housing503, a valve510located within the housing503, a compression spring515for biasing the valve510toward a seat defining an inlet504to the reservoir420, and a tube445extending into the reservoir420for depositing the lubricant flowing from the basin410into the reservoir420. To couple the basin410to the reservoir420, the user mounts the basin410onto the guide rails44and inserts the drain440into the inlet504, which biases the valve510rearward against the bias of the spring515, thereby allowing lubricant to flow freely between the basin410and the reservoir420. If the user wishes to empty the reservoir420, the reservoir420has an end cap422that can be removed to drain the lubricant.

FIG. 9illustrates an embodiment of the threader10using the integrated lubrication system400in the collapsed state where the stand100and threader10are oriented adjacent the work surface105. In this state, the threader10is supported on the stand100via a plurality of brackets107(FIG. 10) located on the upright168configured to incline the main housing51slightly rearward along a spindle axis600at a first oblique angle A1with respect to a reference plane P1, with the pipe threading tools46,50,54being at a higher elevation than the spindle60, to promote drainage of the lubricant from the basin410into the reservoir420. In some embodiments, the first oblique angle A1is between, and including one to two degrees (1°-2°) above a horizontal line. Alternatively, in the deployed state (FIG. 10), the main housing51is angled slightly forward along the spindle axis600at a second angle A2with respect to the reference plane P1, with the pipe threading tools46,50,54being at a lower elevation than the spindle60, to permit lubricant to flow away from the pipe as work is being performed. In some embodiments, the second oblique angle A2is between, and including, one to two degrees (1°-2°) below the horizontal reference plane P1.