Drive system for a machining tool or other machine tool usable with a metal working press or other machine

Abstract

To provide a drive system for a machining tool or other machine tools usable with a metal working press or other machines.SOLUTION: A drive system for a tool used with a metal working press or other machine in which a planetary gear is used and the drive system is configured for use with a particular machine tool, such as a female threading tool, and a complementary system can be configured for use with such a drive system. The drive system allows for enhanced tool output compared to conventional drive mechanisms, while allowing for variable disassembly and configuration of the system with respect to the intended machining operation.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] CROSS-REFERENCE TO RELATED APPLICATIONS This application claims priority to U.S. Provisional Patent Application No. 62 / 739,339, filed September 30, 2018, the teachings of which are incorporated herein by reference.

[0002] FIELD OF THE INVENTION The present invention relates generally to metalworking machines and drive systems used therewith for machining the same, as well as other systems usable with the drive systems. [Background technology]

[0003] Sheet metal and other workpieces can be fabricated into a variety of useful products. Typical fabrication (i.e., manufacturing) processes involve bending, folding, and forming holes in the sheet metal and other workpieces. Equipment used in such processes is diverse, including turret presses and other industrial presses (such as single station presses), Trumpf style machines and other rail-type systems, press brakes, sheet-feed systems, coil-feed systems, and other types of fabrication equipment for punching or pressing sheet material.

[0004] Turret presses are known to include a rotating upper table or "turret" that supports multiple tools (e.g., punches) and a rotating lower table / turret that supports, for example, multiple dies. When the upper and lower tables are rotated to a position where a particular male punch on the upper table aligns with a particular female die on the lower table, the workpiece (e.g., sheet metal) between the two can be machined (punched, bent, etc.) by moving the punch downward into contact with the workpiece so that the punch deforms the workpiece. The downward movement of the punch occurs when the ram impacts the punch from above. The die typically has a recess into which the tip of the punch protrudes during the punching operation. In some cases, a hole is punched during the punch's downward stroke, and the tip of the punch can shear the sheet metal (in the process, it can extend into the central recess of the die). In comparison, a single-station punch does not have a turret but has a single station for pressing the workpiece.

[0005] As is known, in some cases, metalworking presses can be designed for use with tooling fixtures (such as tapping tools) that must rotate for use in machining. For example, tapping tools (as opposed to punch tools) are intended to produce screw threads in a workpiece. Thus, tapping tools (or "taps") are used to cut or form the female portion of a mating pair (e.g., a nut). The use of a tap (again, as opposed to the use of a punch tool) requires radial or rotational movement of the tap as it is driven linearly toward the workpiece (by the downstroke of the press ram). Conversely, when a die is used with such a tap, the die primarily serves as a support for the sheet metal during the tapping process.

[0006] Continuing to focus on conventional female threading tools, using such tools with a press has been problematic. For example, the ram stroke distance for the press may be limited. Therefore, the power output (e.g., amount of rotation) generated for the female threading tool may also be limited. Furthermore, with conventional tool (drive) assemblies, the tap may be subjected to a significant amount of torque and shear stress from the rotational forces generated by the corresponding female threading mechanism. The resulting rotational motion of the mechanism components acts on the tap, causing it to rotate accordingly. Over time, the torque and shear forces may result in the tap deforming (or shearing) along its length during machining, depending on the workpiece material used and the magnitude of the forces generated by the mechanism. Furthermore, it has previously been difficult to effectively transfer the forces generated on the tool for the machining operation to maximize the power output (rotation, in the case of a tap) without the tool experiencing corresponding forces.

[0007] Over the years, many designs have been developed to address the above problems. For example, certain designs use a lead screw that rotates as a result of the descent of the ram, causing the tap to rotate accordingly; the downward displacement of the tap is made possible by both the lead screw and the tap having a threaded connection with the pitch assembly. Other designs are known to include powered means (motors) or to use the automatic indexing feature of the press.

[0008] However, while the above-described designs have been effective, they still impart large forces to the tap and provide a limited amount of corresponding power output (at least in terms of rotation). A need remains for a tap drive system that addresses the above-described problems, as well as others, and in so doing, to provide an effective and efficient system for use with metalworking presses. However, in addressing such needs, it has been found that such a solution is also applicable and extendable to other tooling tools used in conjunction with such presses and other machines, and possibly to other functions for which the presses and machines are intended. Summary of the Invention

[0009] Embodiments of the present invention include drive systems for tools used with metalworking presses or other machines, where the systems use planetary gears. Some embodiments relate to drive systems configured for use with specific machining implements, such as internal thread cutting tools. Further embodiments include complementary systems preferably configured for use with such drive systems. Drive system embodiments allow for enhanced tool power output compared to conventional drive mechanisms. Some embodiments also allow for variable disassembly and configuration of the drive system for the intended machining operation.

[0010] The following drawings illustrate certain embodiments of the present invention and therefore do not limit the scope of the invention. The drawings are not necessarily to scale (unless otherwise expressly stated) and are intended for use in conjunction with the description of the detailed description below. Embodiments of the present invention are described below with reference to the accompanying drawings, in which like numbers refer to like elements. [Brief explanation of the drawings]

[0011] [Figure 1] FIG. 1 is a perspective view of a drive unit from an advantageous side in accordance with a particular embodiment of the present invention. [Figure 2] FIG. 2 is an internal view of the drive unit of FIG. 1 from an advantageous top view. [Figure 3] FIG. 3 is an internal view of the drive unit of FIG. 1 from an advantageous side. [Figure 4] FIG. 4 is an exploded view of selected components of the drive unit of FIG. [Figure 5] FIG. 5 is a cross-sectional perspective view of the drive unit of FIG. 1 taken along line VV, the drive unit being configured for and adapted for use with a female threading tool in accordance with certain embodiments of the present invention. [Figure 6] FIG. 6 is an exploded view of the drive unit of FIG. [Figure 7]FIG. 7 is an elevational cross-sectional view of the drive unit of FIG. 5 and a die used therewith in accordance with certain embodiments of the present invention, the cross-section of the drive unit being the same as that shown in FIG. 5, and similarly shown with respect to the die. [Figure 8] FIG. 8 illustrates a drive unit with an alternative layout of corresponding components for the upper and lower portions in accordance with certain embodiments of the present invention. [Figure 9] FIG. 9 is an exploded view of a tool assembly with a preferred drive unit in accordance with certain embodiments of the present invention. [Figure 10] FIG. 10 is a side cross-sectional view of the tool assembly of FIG. 9 assembled in accordance with a specific embodiment of the present invention. [Figure 11] FIG. 11 is an exploded view of selected portions of the tool assembly of FIG. [Figure 12] FIG. 12 is a partial side view of the tool assembly of FIG. 9 in an assembled state, showing an internal view of the top of the unit. [Figure 13] FIG. 13 is another partial side view of the tool assembly of FIG. 9 in an assembled state, showing the top portion of the unit and an internal view of the head. [Figure 14] FIG. 14 is a side view of a helix drive in accordance with a specific embodiment of the present invention. [Figure 15] FIG. 15 is a cross-sectional view of the upper portion of the tool assembly of FIG. 19 taken along line XV-XV in accordance with certain embodiments of the present invention. [Figure 16] 16 is a side view of the transmission assembly of the tool assembly of FIG. 9. FIG. [Figure 17] FIG. 17 is an exploded view of the transmission assembly of FIG. [Figure 18] FIG. 18 is a side view of another design of a helix drive in accordance with a specific embodiment of the present invention. [Figure 19] FIG. 19 is a partial side view of a modified design of the tool assembly of FIG. 9 assembled in accordance with certain embodiments of the present invention, showing an internal view of the top portion of the unit. [Figure 20]FIG. 20 is a partial side view of another modified design of the tool assembly of FIG. 9 assembled in accordance with certain embodiments of the present invention, showing an internal view of the top portion of the unit. [Figure 21] FIG. 21 is a partial side view of a further modified design of the tool assembly of FIG. 9 assembled in accordance with certain embodiments of the present invention, showing an internal view of the upper portion of the unit. [Figure 22] FIG. 22 is a side partial cross-sectional view of a tool assembly using an internally threaded coupling with a threaded helix and head portion in accordance with certain embodiments of the present invention. [Figure 23] FIG. 23 is a side cross-sectional view of a further tool assembly using an internally threaded coupling with a threaded helix and head in accordance with certain embodiments of the present invention. DETAILED DESCRIPTION OF THE INVENTION

[0012] The following detailed description is exemplary in nature and is not intended to limit the scope, application, or configuration of the present invention. Rather, the following description sets forth some practical illustrations for realizing preferred embodiments of the present invention. Examples of construction, materials, dimensions, and manufacturing processes are shown for some selected elements, while other elements employ those known to those skilled in the art of the present invention. Those skilled in the art will recognize that many of the described embodiments have a variety of suitable alternatives.

[0013] FIG. 1 is a perspective view of a drive unit 100 in accordance with certain embodiments of the present invention, where the drive unit 100 is configured to drive a tool loaded therein. As described in further detail herein, such a tool may be, for example, an internal threading tool (“tap”) 101 (shown most clearly in FIGS. 5 and 7 ). As shown, the drive unit 100 is relatively compact in shape through the use of an overall housing 102. In certain embodiments, the housing 102 is formed of multiple interconnected layers, each of which is housed by a separate outer housing structure for holding a corresponding component of the unit 100. The compact shape allows the drive unit 100, in certain embodiments, to be made for use with any of a variety of metalworking presses or other machines, both new and existing, to accommodate the machining operations that can be performed when a tool is loaded into the drive unit 100. One such machine that could potentially be retrofitted with drive unit 100 includes a turret press, into which unit 100 simply slides (e.g., into a hole in the upper table), although in the case of presses, the unit's design can be used with any of a variety of industrial press types, including single station, Trumpf-type machines and other rail-type systems, press brakes, sheet-fed systems, coil-fed systems, and other types of processing equipment for punching or pressing sheet material.

[0014] 1 , drive unit 100 is shown in the same orientation as when used within a metalworking machine. For example, upper portion 104 of unit 100 is configured to be driven vertically downward (by drive force A, e.g., a ram stroke), and lower portion 106 of unit 100 is correspondingly driven vertically downward to contact an underlying structure, such as material 103 to be processed (e.g., sheet metal 103, FIG. 7 ). As described later herein, lower portion 106 is operably coupled to upper portion 104 such that it is vertically movable relative to upper portion 104. Thus, upon contact with the underlying structure, lower portion 106 is internally driven vertically upward (again relative to lower portion 104) to trigger the ejection of a tool from unit 100, which is simultaneously rotated by unit 100 for its machining function. Thus, in certain embodiments, the lower portion 106 can be referred to as the drive portion of the unit 100 because of the upward linear drive force relative to the upper portion 104. As will be further explained, the drive unit 100 is configured to function to convert this linear force (e.g., resulting from the downward movement of the unit 100 relative to an underlying structure, such as a material originally being machined) into a rotational force (to rotate a tool disposed on the unit 100).

[0015] Turning now to the specific tool types that drive unit 100 may typically be configured to employ, taps (as described above) are conventionally known to withstand significant amounts of torque and shear stress from rotational forces imparted by the internal threading mechanism. As further detailed herein, the rotational forces traditionally experienced by taps by the internal threading mechanism can be distributed and balanced by drive unit 100, thereby increasing the strength of the assembly and reducing the potential for adverse effects on the tap, while correspondingly increasing the amount of power derived from the tool, at least in terms of rotation. One way to accomplish this is to use interconnected gear sets within drive unit 100 to transmit power to a tool loaded therein. Referring to FIG. 2 , which shows an internal view of unit 100, in certain embodiments, a gearing arrangement including multiple gear sets may be located in the upper portion of unit 100 and used in connection with transmitting power to a tool used therewith. In certain embodiments, a gearing arrangement of interconnected gears forms a planetary gearing for use with drive unit 100. Thus, as explained further below, the planetary gearing of drive unit 100 is generally configured to operate after application of drive force A and concurrent with use of a tool loaded within unit 100.

[0016] To further elaborate on the fundamentals of planetary gearing, typically three sets of gears are required, each with a different degree of freedom. Specifically, at least three planet gears are configured to rotate about axes that revolve around a central sun gear that spins in place, and a ring gear is used to connect the planet gears to the outer surface. Returning to FIG. 2 (and with reference to FIGS. 3 and 4, as explained below), the ring gear is designated 110 and the sun gear is designated 112. Between the ring gear 110 and the sun gear 112, two groups of planet gears 114 and 116 are used. However, the present invention is not limited to this design, as different designs for the drive unit 100 can utilize one group as well as more than two groups of planet gears. Notably, benefits of utilizing more planet gear groups include a corresponding increase in rotation of the central sun gear 112, although increasing the number requires a larger storage capacity for the drive unit 100.

[0017] With respect to the use of such a planetary gear arrangement in drive unit 100, reference is again made to FIG. 3 , which shows an internal view of unit 100 from a side vantage point, and FIG. 4 , which shows an exploded view of unit 100 with selected components thereof. Upward vertical linear movement of the unit's lower portion 106 correspondingly induces rotation of ring gear 110, which drives a first set of planetary gears 114, which in turn drive a second set of planetary gears 116, which in turn drive central sun gear 112. In certain embodiments, with respect to ring gear 110, gear 110 is operably secured to helix drive 120. In the particular embodiment shown, ring gear 110 is located within a casing 118 that extends from helix drive 120, such that gear 110 (as operably secured to helix drive 120) rotates as a result of upward vertical linear movement of the unit's lower portion 106.

[0018] In certain embodiments, helix drive 120 defines a plurality of upwardly curved grooves 122 along its longitudinal length h, along which a corresponding number of bearings 124 are configured to travel. In the particular embodiment shown, bearings 124 are rigidly secured to and protrude from internal recesses 126 formed in lower portion 106. Recesses 126 are sized to receive helix drive 120 such that grooves 122 receive corresponding bearings 124. Because of this assembly between lower portion 106 and helix drive 120, when lower portion 106 linearly moves upward (in contact with an underlying structure, e.g., a material being machined), a corresponding linear upward force is exerted on bearings 124. However, given that bearings 124 are rigidly secured to lower portion 106 and that lower portion 106 is generally prevented from rotating by contact with the underlying structure, the linear upward force on bearings 124 results in upward movement along corresponding grooves 122 in helix drive 120. Because the lower portion 106 (and bearings 124) are held stationary (non-rotating), movement of the bearings 124 within the grooves 122 actually involves the grooves 122 sliding downward relative to the bearings 124 and a corresponding rotation of the helix drive 120 relative to the lower portion 106 and bearings 124. In certain embodiments, as shown, the bearings 124 are positioned equidistant from one another around the recess 126 of the lower portion 106. For example, in the particular embodiment shown, three bearings 124 are employed with respect to the lower portion 106. With these bearings 124 positioned equidistant from one another, the spacing of the bearings 124 around the lower portion 106 is 120°. Due to the fixation of the ring gear 110 to the helix drive 120 (by the casing 118 internally coupling to the ring gear 110), rotation of the helix drive 120 results in a corresponding rotation of the ring gear 110.

[0019] Returning to the planetary gear set used with drive unit 100, as previously described, moving from a rotation of ring gear 110 to a corresponding rotation of first set of planetary gears 114 to a corresponding rotation of second set of planetary gears 116 to a rotation of sun gear 112, the amount of rotation of each successive gear increases with respect to the planetary gear set. This attribute of the planetary gear set should be understood as each subsequent gear (or gear set) being positioned closer to the center than the preceding gear (or gear set), such that the gear closer to the center has a greater amount of rotation. Using the preferred gear configuration, one-third of a rotation of ring gear 110 (corresponding to a rotation of helix drive 120) corresponds to seven rotations of sun gear 112.

[0020] While the above description focuses on an embodiment for the drive unit 100 in which the helix drive 120 is below the gearing arrangement, e.g., the planetary gearing, for the unit 100, the present invention should not be limited to such an embodiment. For example, as shown in FIG. 8 , the drive unit can have the exact opposite arrangement of the helix drive 120 and gearing arrangement, with the helix drive 120 located above the gearing arrangement. With the above embodiment in mind, it will be clear how other arrangements of such a drive unit would operate. For example, when a downward normal force is applied to the upper portion (surrounding the stem of the helix drive 120), the lower portion (containing the gearing arrangement) is directed toward and contacts the surface (the material to be machined). Furthermore, the lower portion (with the gearing arrangement) is directed upward perpendicular to the upper portion (surrounding the stem of the helix drive 120). In certain embodiments, a first portion of the lower portion, which holds the gearing arrangement, is rotatably held by a second portion of the lower portion, which contacts the material to be machined. Additionally, the upper section is locked against rotation by one or more upper extensions (e.g., extensions that are keys that align with vertical slots in the turret bores) that protrude from the upper section. As the lower section moves vertically upward, the lower section (gearing arrangement) rises relative to the upper section (helix drive 120). However, due to the rotatable coupling between the first section (the section that machines and contacts the material) and the second section (gearing arrangement) of the lower section, and the locking (against rotation) of the upper section (which surrounds the stem of helix drive 120), the upward movement of the lower section relative to the upper section results in the second section of the lower housing (gearing arrangement) rising relative to the upper section. The stem of helix drive 120 is configured to rotate around the fixed upper section (by virtue of the upper section's bearing 124 moving downward within the curved groove 122 of the helix drive stem). This rotation of helix drive 120 correspondingly rotates the gears of the gearing arrangement, as previously described.The advantage of this alternative arrangement of the drive unit is that the gearing arrangement is positioned closer to the tap, whereby the sun gear or output gear has no reason to exist as long as the extension or insert 130 connects said gear to the tool.

[0021] FIG. 5 is a perspective cross-sectional view of a drive unit 100′ (similar to drive unit 100 and configured to employ a female thread-cutting tool 101 (“tap”)) in accordance with certain embodiments of the present invention. The drive unit 100′ is configured such that its sun gear 112 is operatively coupled to the tap 101. Thus, rotation of the sun gear 112 is likewise imparted to the tap 101. Thus, as noted above, it can be seen that when the sun gear 112 rotates seven times, the tap 101 also rotates seven times. The sun gear 112 is operatively coupled to the tap 101. In certain embodiments, as shown, such operative coupling is provided through the use of an insert 130, one end 130a of which is configured to couple with the extension 112a of the sun gear 112. One preferred coupling configuration may include the insert 130, or at least both ends 130a, 130b thereof may be hollow. To that end, in certain embodiments (shown as preferred in FIG. 4 ), the sun gear extension 112a can be formed with a particular shape (e.g., square), and the insert end 130a can be formed with a corresponding internal shape (e.g., square profile) to snugly receive the sun gear extension 112a. Thus, with this connection, rotation of the sun gear 112 corresponds to the same rotation of the insert 130. Similarly, in certain embodiments, the opposite end 130b of the insert 130 can be formed with a corresponding internal shape (e.g., square profile) to snugly receive the correspondingly shaped (e.g., square) end 101a of the tap 101. In certain embodiments, one or more ball bearings 130c can be positioned within the insert end 130b so as to partially protrude from the square internal profile and contact (and more snugly hold) the outer surface of the square tap end 101a. Thus, with this connection, rotation of the insert 130 corresponds to the same rotation of the tap 101. Of course, there are many different ways of connecting the insert 130 (e.g., both ends thereof) and the sun gear extension 112a (e.g., corresponding ends thereof) and the tap 101, and one such example will be detailed, but the invention is not limited thereto.

[0022] FIG. 6 is a fully exploded view of a drive unit 100′, excluding the tap 101, in accordance with certain embodiments of the present invention. The drive unit 100′ is shown from right to left with respect to its components and housing structure, from the upper portion 104 to the lower portion 106′ (the lower portion is numbered differently from the lower portion 106 previously referenced in FIGS. 1 and 3 because it includes an insert 130 for the tap 101). Therefore, this view more clearly illustrates the components and their structure. FIG. 7 is an elevational cross-sectional view (similar to FIG. 5) of the drive unit 100′ and a die 140 used therewith, in accordance with certain embodiments of the present invention. Shifting focus to the tap 101 of the drive unit 100′, and particularly to the protrusion of the tap 101 from the unit 100′ to perform a female threading operation on a corresponding material (e.g., sheet metal 103), the tap 101 does not move upward, in comparison, because the lower portion 106 moves vertically upward upon contact with the material. Instead, the upward movement of the lower portion 106 causes the tap 101 to essentially descend into contact with the material and then perform the internal threading operation thereon, and the tap 101 rotates for operation corresponding to the rotation of the sun gear 112.

[0023] 7 is configured to serve as a lubrication system for the tap 101 during the internal threading operation. When the lower portion 106' of the drive system 100' contacts the material (e.g., sheet metal 103), this corresponds to another contact between the material and the upper surface of the die 140. In certain embodiments, such contact induces a lubricant (e.g., oil) to be directed upward from the die 140 onto the overlying portion of the material. In the particular embodiment shown, the upper surface of the die includes a vertically protruding pad portion 142 of the die 140, such that depression of the pad 142 (by contact with the material, e.g., sheet metal 103) induces a pump piston 144 positioned below the pad 142 within the die 140 to force lubricant from a tapping reservoir 146. To that end, in certain embodiments, piston 144 acts on first valve 148 to direct lubricant from reservoir 146 through the valve and onto the area of ​​the material being machined by tap 101. In so doing, it is seen that the lubricant coats the material area defined below, above, and within the pre-drilled hole (before it is threaded by tap 101 of drive unit 100′) by virtue of the lubricant being released onto the material and below drive unit 100.

[0024] 7, when the lower portion 106' of the drive unit 100' is removed from the material being machined (e.g., sheet metal 103), the piston 144 correspondingly retracts to a raised position within the die 140 such that a vacuum is created in the reservoir 146, drawing additional lubricant into the reservoir. In certain embodiments, such refilling of the reservoir 146 with lubricant is accomplished by operation of a second valve 150 in communication with the reservoir 146 at one end and with an additional lubricant supply reservoir 152 at the other end of the valve 150. Additionally, to prevent excessive accumulation of lubricant in the tapping reservoir 146, one or more grooves 154 can be formed in the die 140 extending from an upper opening 146a of the reservoir 146 toward a teardrop hole 156 formed in the die 140.

[0025] To date, the designs described herein have focused on configurations to enhance the effectiveness and efficiency of force transmission by the implemented drive unit. For example, the conversion of linear to rotational forces, from the ram stroke to the drive of the tool (e.g., tap), is better distributed / balanced using the drive unit, thereby increasing the strength of the assembly, reducing adverse effects on the tool during use, and correspondingly increasing the amount of power derived from the tool, at least rotationally. Continuing this emphasis, further designs will be illustrated. Beginning with FIG. 9, an exploded view of a tool assembly 200 is shown. The assembly 200 includes a drive unit 202 formed by a transmission assembly 204 and a helix drive 206. As explained in more detail below, the drive unit 202 functions similarly to the drive units illustrated herein (in terms of transmitting force), and the transmission assembly 204 includes a gearing stage or configuration, such as a planetary gearing, for enhancing output (increasing rotation), and a helix drive 206 for converting input linear force into rotational force to operate the transmission assembly 204. Because the generally available ram distance (stroke) in a press is therefore limited (as already mentioned above), the combined use of a staged gearing configuration (e.g., the transmission assembly 204) and an inclined helix (e.g., the drive 206) provides a compact solution for working with a limited ram stroke and maximizing output rotation. This greatly expands the application possibilities of the female threading tool in terms of material thickness and desired thread pitch. In contrast, conventional female threading units are known to include a single rotary element / linear drive.

[0026] 9 and continuing with drive unit 202 of assembly 200, transmission assembly 204 is formed as a modular unit. In certain embodiments, as shown, assembly 204 can be operatively coupled to helix drive 206 (e.g., by dowel pin 208), and with reference to FIG. 10 (showing a cross-sectional view of assembled tool assembly 200 of FIG. 9 along line XX), drive unit 202 is configured to be housed within tool assembly 200. In the particular embodiment shown, tool assembly 200 can be configured to be disassembled by the user so that transmission assembly 204 and / or helix drive 206 can be retrofitted or replaced from tool assembly 200 in the field as needed or desired. Furthermore, as will be described with reference to FIG. 11 (a partially exploded view of selected portions of tool assembly 200), transmission assembly 204 is modular and therefore user configurable, e.g., one transmission assembly 204 can be replaced with another, allowing drive unit 202 to be configured to best suit the intended use / application based on the tooling used in tool assembly 200 and the material to be machined.

[0027] As can be seen from the above, to enable and facilitate retrofitting / configuration of drive unit 202 based on the intended use, tool assembly 200 is configured for easy disassembly by the user in the field. Referring to FIG. 10 (and FIGS. 9 and 11 ), tool assembly 200 is relatively compact and simplified in shape by using similarly shaped upper and lower housings 210, 212 to house and / or support the corresponding components of assembly 200, including drive unit 202. With such a compact and simplified shape, tool assembly 200, in certain embodiments, can be used with any of a variety of metalworking presses or other machines (and the associated tooling required for driving and rotating). One such machine that is easy to retrofit with tool assembly 200 is a turret press, into which assembly 200 can simply be placed (e.g., into a hole in its upper table). However, in the case of presses, the assembly design can be utilized for a variety of industrial press types, including single station, Trumpf type machines and other rail type systems, press brakes, sheet fed systems, coil fed systems, and other types of processing equipment for punching or pressing sheet material.

[0028] Returning to the concept of user disassembly and beginning with FIG. 9 (and with reference to FIG. 10 ), the upper and lower housings 210, 212 can be configured with mating threads on corresponding ends thereof in certain embodiments. For example, the illustrated tool assembly 200 has external threads 212a on the upper end of the lower housing 212 that mate with internal threads 210a on the lower end of the upper housing 210. However, the invention should not be so limited, and other couplings or alternative threaded configurations for the housings 210, 212 can be used. Further, as illustrated, a keyed fastener can be used to subsequently lock the housings 210, 212 together. In certain embodiments, this fastener can take the form of an insert 114a and / or a corresponding fastener 114b for retaining the insert 114a. However, the keyed fastener can be any of a variety of other fastener types and function similarly. For disassembly (e.g., using threaded housings and interlocking keyed fasteners), fasteners 114b / inserts 114a are unscrewed / removed and upper housing 210 is then rotated relative to lower housing 212 to disengage the lower housing, thereby providing access to drive unit 202 ( FIG. 11 ) and other internal components. For assembly (or reassembly), after any desired retrofit or replacement of drive unit 202, upper housing 210 is threadedly connected to lower housing 212 and inserts 114a / fasteners 114b are then added / threaded to hold and lock the housings together.

[0029] While the foregoing serves as an introduction to some of the features of tool assembly 200, it should be appreciated that other features are inherently preferred. For example, while the configuration of drive unit 202 includes helix drive 206 positioned above transmission assembly 204, it should be appreciated that the above-described configuration is also applicable to tool assemblies having the reverse configuration (e.g., see the previous discussion of drive unit 100 in FIG. 1 ). The versatility and guaranteed configuration of drive unit 202 described above for tool assembly 200, e.g., with respect to user disassembly, is generally not considered for conventional drive mechanisms for internally threaded tools. This is primarily due to the fact that conventional designs are inherently highly complex, particularly those configured such that any disassembly poses the risk of adversely affecting functionality. Thus, conventional mechanisms, as described herein, are not easily configurable in the field based on the intended use / application, and are generally configured as structures that are completely replaceable without field modification.

[0030] Continuing with the conventional design, in certain embodiments, the tool assembly 200 is configured with a dynamic biasing member 216 (e.g., gas, e.g., nitrogen, spring, etc.) rather than a mechanical (e.g., coil spring type). As described further below, in certain embodiments, the tool assembly 200 is designed such that the biasing member 216 is more dynamic than mechanical. In particular, because the transmission assembly 204 and / or helix drive 206 of the tool assembly 200 are designed to be reconfigured / retrofitted in the field, the required recoil force / distance may vary accordingly and can be more variably accommodated by the use of a gas spring. For example, in certain embodiments, the gas spring may be configured to provide a recoil force of 800 lbs with a travel distance of 1.5" to 3.5". The use of a gas spring for the biasing member 216 allows the reaction parameters to be tailored to a variety of transmission assembly 204 / helix drive 206 combinations while at the same time providing user friendliness when configuring the tool assembly 200 in the field.

[0031] Returning to FIG. 10 , the illustrated tool assembly 200 is oriented similarly to when used within a metalworking machine. When selected for use in a metalworking machine, the assembly 200 is moved to vertically align with and impact the machine's ram. When driven vertically downward (by a driving force A′, e.g., a ram stroke), the head portion 218 of the assembly 200 moves relative to the upper housing 210, since the head portion 218 and housing 210 are operatively coupled. For example, in certain embodiments (and as can be seen in FIGS. 12 and 13 ), a plurality of grooves 222 are formed along the longitudinal length h′ of the head portion 218, with a corresponding number of bearings 224 configured to move along these grooves. In the particular embodiment shown, the bearings 224 are rigidly secured to and protrude from an internal bore 226 formed in the upper housing 210. As can be seen in FIG. 10 , the upper housing 210 is formed with an internal recess 228 sized to receive the head portion 218, such that the grooves 222 receive the corresponding bearings 224. With such a connection between the upper housing 210 and the head portion 218 (FIGS. 12 and 13), when the machine ram strikes, the entire tool assembly 200 is driven downward until the opposite tool end contacts the workpiece, at which point the head portion 218 moves downward perpendicular to the upper housing 210, causing the groove 222 to correspondingly move downward about the bearing 224.

[0032] Similar to head portion 218 and upper housing 210, head portion 218 and helix drive 206 are also operatively coupled. Looking to FIG. 14 (and with continued reference to FIGS. 12 and 13), in certain embodiments, a plurality of upwardly curved grooves 222' are formed along length h" of helix drive 206, with a corresponding number of bearings 224' configured to travel along these grooves. Referring to FIGS. 10 and 13, in certain embodiments, bearings 224' are rigidly secured to and project from corresponding internal bores 226' formed in head portion 218. As can be seen in FIG. 10, upper housing 210 is formed with an internal recess 228' sized to receive helix drive 206, such that grooves 222' receive corresponding bearings 224'. As can be seen in FIG. 13, with this coupling between head portion 218 and helix drive 206, head portion 218 is operatively coupled to helix drive 206. 18 moves linearly downward, a corresponding linear downward force is applied to bearing 224'. However, considering that bearing 224' is rigidly fixed to head portion 218 and is generally prevented from rotating by its connection to upper housing 210, which locks head portion 218 into the machine (e.g., turret table bore) (as discussed above), the downward linear force on bearing 224' results in downward movement along corresponding grooves 222' of helix drive 206. Again, if head portion 218 and therefore its bearings 224' are held stationary (so as not to rotate), movement of bearing 224' within grooves 222' (and the downward force on bearing 224' applied to the bottom surface of the corresponding grooves 222') results in corresponding rotation of helix drive 206.

[0033] 15, the bearings 224 of the upper housing 210 and the bearings 224' of the head portion 218 are equidistantly spaced about the interior recesses 226, 226' thereof. For example, in the particular embodiment shown, three bearings 224 are employed for the upper housing 210 and three bearings 224' are employed for the head portion 218. With each of these bearing sets 224, 224' equidistantly spaced 120° apart from one another and each extending from or to the head portion 218, the 120° distribution of each triplet of bearings 224, 224' are offset from one another on the head portion 218. As will be explained below, the head portion 218 can be configured with additional sets of grooves 222a, 222b therein adjacent to the initial set of vertically oriented grooves 222 in the particular embodiment shown.

[0034] Returning to the use of tool assembly 200, reference is made to FIG. 10 and FIGS. 16 and 17, which show a side view and an exploded view of transmission assembly 204, respectively, to describe the rotation of helix drive 206. As mentioned above, in forming drive unit 202 for tool assembly 200, helix drive 206 can be operatively coupled to transmission assembly 204, for example, by dowel pin 208. Through this coupling, the rotation of helix drive 206 forms an input to transmission assembly 204 and the gearing arrangement housed therein, such as a planetary gear arrangement. As previously illustrated herein, planetary gear arrangements can be effectively used to enhance the output (increase the rotation) of the tool being driven and rotated (e.g., a tap). By using a ring gear, multiple sets of planet gears, and a sun gear, and depending on the number of planetary gear stages, the output rotation of transmission assembly 204 can be a multiple of the input rotation. 17, rotation of the coupling stem 230 causes corresponding rotation of the first set of planetary gears 232, which is followed by corresponding rotation of the second set of planetary gears 238 by way of the first sun gear 234, which is followed by corresponding rotation of the second sun gear 240, which is operably coupled to an insert 240 for a tool (e.g., a tap). As previously explained, the gears closer to the center have a correspondingly greater amount of rotation, and therefore the tool (e.g., a tap) rotates accordingly due to the external rotating contact of the planetary gears 232 and 238 with the central ring gear 236.

[0035] Thus far, various drive unit designs and tool assembly designs comprising drive unit designs have been illustrated. With respect to these embodiments, the focus has been on using planetary gearing within the drive unit 100, 202 to not only increase power output in terms of rotational mass, but also to enhance its magnitude (increase rotation) while providing better distribution / balancing of the output rotational force. Furthermore, by providing the drive unit as a modular component (e.g., completely or one or more of its separable parts, i.e., the transmission assembly and / or the helix drive), a user can retrofit and configure the tool assembly with, for example, a pop-in transmission assembly that is more desirable for the application. To categorize the same concept, additional designs are next illustrated, again focusing on one or more of the system's effectiveness, efficiency, and versatility. In certain embodiments, one or more other components can be further modified, such as the helix drive of the drive unit and / or the head portion of the tool assembly.

[0036] Starting with the helix drive 206 of the tool assembly 200 (as seen in FIG. 14), other helix designs are possible, as illustrated by the helix drive 206' in FIG. 18. Before discussing the differences between the two drives 206 and 206', it must be understood that the helix drive plays a key role in converting the input from linear to rotational. From an analysis of this conversion, it can be seen that the opening and closing cycle or working periods of the helix drive are the most stressful in terms of forces. In particular, with regard to the opening period, the helix drive rotates from rest, and in the closing period, the helix drive reverses, so that the drive is stopped and driven to rotate in the reverse rotational direction as well. In certain embodiments, as illustrated in drive 206' of FIG. 18, the area between grooves 222" deviates from uniform. For example, in the particular embodiment shown, the area between grooves 222" at its ends is narrow, while this area increases as grooves 222" extend toward the end of the helix drive. The effect of this change in design is a reduction in the angle of the grooves (relative to the length of the drive). In particular, canting the threads of groove 222" to be at a smaller angle relative to the direction the helix drive is traveling from the downstroke of the machine ram reduces stresses associated with starting and ending cycles or working periods of the helix drive.

[0037] Furthermore, the total output rotations from a given ram stroke force, at least up to this point, depends on the design parameters of the transmission assembly 204 and the helix drive 206. For example, in certain embodiments, the design parameters include the groove configuration and angle setting of the helix drive 206 and the rotational output ratio through the transmission assembly 204. By way of example only, in certain embodiments, the gearing stages of the transmission assembly 204 are configured for a 20:1 ratio, resulting in a total output of 8 rotations for every 0.4 rotations of the helix drive 206. This is roughly what is required for a tap drive unit used for the Press C station size. Alternatively, in certain embodiments, modifying the transmission assembly 204 so that its gearing stages have a 25:1 ratio and adding an angled helix drive 206' can result in a total output of at least 12 rotations for every 0.5 rotations of the drive 206'.

[0038] Shifting focus to the head portion 218 of the tool assembly 200, reference is now made to FIGS. 19-21. As previously described, the grooves 222 formed in the head portion 218 were oriented vertically, so as to be generally in the same direction as (or generally parallel to) the direction of the ram stroke from the metalworking machine. Thus, when used with corresponding bearings 224 to operably couple the head portion 218 to the upper housing 210, the grooves 222 primarily define the length over which the ram can drive the head portion 218 downward, and thus the length over which the helix drive can rotate. Based on the layout of the grooves 222′ formed in the helix drive 206′ as shown, the drive 206′ rotates clockwise when the ram stroke impacts the head portion 218. However, as suggested with respect to FIG. 15, in certain embodiments, the head portion 218 can be formed with additional groove sets at different inclinations relative to the direction of the ram stroke to affect the rate of force transmission, thereby producing acceleration or deceleration.

[0039] For example, beginning with FIG. 19, two other groove sets 222a and 222b are formed in head portion 218a in addition to vertically oriented groove 222. As shown, these additional groove sets 222a, 222b each extend transversely relative to groove 222" of helix drive 206'. When installed in either selected groove set 222a or 222b, bearing 224 is guided upward within the groove upon receiving a ram stroke on head portion 218a to rotate head portion 218a clockwise. Thus, when grooves 222a and 222b are used, the clockwise rotation of head portion 218a contributes to / reinforces the clockwise rotation of helix drive 206', thereby helping to increase the rotational speed of helix drive 206' from a ram stroke. It should be appreciated that groove set 222b, which has a greater slope than groove set 222a, provides a correspondingly greater increase in rotational speed to helix drive 206'.

[0040] Conversely, looking at FIG. 20 , the other two groove sets 222a' and 222b' are formed in head portion 218b to better align with grooves 222' of helix drive 206'. When installed in either selected groove 222a' or 222b', bearing 224 is guided upward in the groove upon receiving a ram stroke to head portion 218b to rotate head portion 218b counterclockwise. Thus, when grooves 222a' and 222b' are used, counterclockwise rotation of head portion 218b counteracts / opposes clockwise rotation of helix drive 206', thereby helping to reduce the rotational speed of helix drive 206' from the ram stroke. It should be appreciated that groove set 222b', which has a greater slope than groove set 222a', correspondingly provides greater rotational reduction to helix drive 206'.

[0041] 19 and 20, it may be desirable to increase the rotational speed of helix drive 206' to speed up the overall operation, for example, unless the material being machined would be damaging to the tool at such a speed, or it may be preferable to decrease the rotational speed of drive 206', for example, if the material being machined is hard, whereby standard or fast speeds would damage the tool. Turning to FIG. 21, head portion 218c is formed with groove sets 222a and 222a' (the groove sets of head portions 218a and 218b described above), thereby providing head portion 318c that increases (222a), decreases (222a'), or has no effect (222b) on the speed of the helix drive rotation from the ram stroke.

[0042] Further to the modification of the head portion, in certain embodiments, a threaded helix 250 can be incorporated (threaded) as shown in Figures 22 and 23. To that end, the head portion 218d is formed with internal threads 252 so that a linear downward force A" (from the ram stroke) applied to the head portion 218d results in a translational rotational force on the threaded helix drive 250, i.e., it is pushed downward along the internal threads 252. To that end, the head portion 218d and outer housing 254 of the tool assembly of Figures 22 and 23 are rotationally fixed such that the rotational force originates from the threaded helix 250. Furthermore, in certain embodiments, the threaded helix 250 is operably coupled to the transmission system 204' such that the rotational motion of the helix 250 is transferred directly to the planetary gear set.

[0043] An embodiment of a "drive system for a machining tool or other work implement usable with a metalworking press or other machine" is disclosed. Those skilled in the art will recognize that the invention may be practiced in embodiments other than those disclosed. The disclosed embodiments are presented for purposes of illustration and not limitation, and the present invention is limited only by the following claims. The present disclosure also includes the following aspects. [Aspect 1] 1. A drive unit for a tooling tool usable with a metalworking press or other machine, comprising: a first portion and a second portion operably connected to the first portion such that the second portion is movable relative to the first portion, such that when a downward force contacts the first portion and contact occurs between the second portion and a rigid structure, an upward movement of the second portion relative to the first portion results; a work assembly; a gearing arrangement operably connected to the working assembly; a helix drive operably connecting the gearing arrangement to one of the first portion or the second portion; Equipped with said upward movement of said second portion results in a corresponding force conversion, converting an input linear force into an output rotational force, said force conversion resulting from said coupling and corresponding movement of said one of said first portion or said second portion and said helix drive relative to one another; Drive unit. [Aspect 2] 2. The drive unit of claim 1, wherein the helical drive is rotatable relative to the second portion, and wherein rotation of the helical drive is induced by the upward movement of the second portion. Aspect 3 the helix drive comprises a stem having an outer surface formed with a plurality of grooves curving upwardly around and along the length of the stem; the second portion includes a plurality of bearings each rigidly secured to the second portion, the bearings being respectively received within the grooves of the helix drive stem; the bearing is guided to move upward along the groove of the helix drive stem during the upward movement of the second portion relative to the first portion, corresponding to the rotation of the helix drive stem relative to the second portion. 3. The drive unit according to embodiment 2. Aspect 4 A drive unit as described in aspect 3, wherein the stem of the helix drive is located below the gear arrangement in the drive unit. Aspect 5 A drive unit as described in aspect 3, wherein the second portion is formed with a recess sized to receive the helical drive stem, and the bearings extend from a corresponding inner surface of the second portion that forms the recess, the bearings being spaced around the inner surface and correspondingly extending into the corresponding groove of the helical drive stem. Aspect 6 3. The drive unit of claim 2, wherein the gearing arrangement comprises a planetary gear set, an input gear or ring gear of the planetary gear set operatively coupled to the helix drive such that the rotation of the helix drive corresponds to the same rotation of the input gear. Aspect 7 7. The drive unit of claim 6, wherein the helix drive comprises a casing extending from the helix drive, the input gear located within the casing and coupled to the casing. Aspect 8 7. The drive unit of claim 6, wherein rotation of the input gear results in a greater rotation of an output gear of the planetary gear device, and the output gear is operably connected to the working assembly such that rotation of the output gear corresponds to the same rotation of the working assembly. Aspect 9 A drive unit as described in aspect 8, wherein the planetary gear device includes one or more sets of intermediate gears or planetary gears operatively connecting the input gear with the output gear, wherein the rotation of the input gear corresponds to a greater number of rotations of the one or more sets of intermediate gears and the rotation of the one or more sets of intermediate gears corresponds to a greater number of rotations of the output gear. Aspect 10 9. The drive unit of claim 8, wherein the machining assembly includes an insert that connects at one end to the output gear of the planetary gear device, and the other end of the insert is configured to connect to a tool. Aspect 11 11. The drive unit of claim 10, further comprising the tool, wherein the tool is a female thread cutting tool and the rigid structure is a material that is machined by the female thread cutting tool. Aspect 12 2. The drive unit of claim 1, wherein the first portion is an upper portion of the drive unit and the second portion is a lower portion of the drive unit. Aspect 13 1. A drive unit for a tooling tool usable with a metalworking press or other machine, comprising: an upper portion and a lower portion operably connected to the upper portion such that the lower portion is movable relative to the upper portion, such that when a downward force contacts the upper portion causing contact between the lower portion and a rigid structure, upward movement of the lower portion relative to the upper portion results; a planetary gear set operably connected to the lower portion; a work assembly operably connected to the planetary gear set; Equipped with the upward movement of the lower portion induces rotation of gears of the planetary gear set; a rotation of an input gear or ring gear of the planetary gear set corresponds to a greater number of rotations of an output gear or sun gear of the planetary gear set, and the output gear is operably connected to the working assembly such that a rotation of the output gear corresponds to the same rotation of the working assembly; Drive unit. Aspect 14 14. The drive unit of claim 13, further comprising a helix drive operably connecting the planetary gear set to the lower portion, the helix drive operably connected to the input gear, wherein rotation of the helix drive corresponds to the same rotation of the input gear. Aspect 15 15. The drive unit of claim 14, wherein the helix drive comprises a casing extending from the helix drive, the input gear located within the casing and coupled to the casing. Aspect 16 A drive unit as described in aspect 13, wherein the planetary gear device includes one or more sets of intermediate gears or planetary gears operatively connecting the input gear with the output gear, wherein the rotation of the input gear corresponds to a greater number of rotations of the one or more sets of intermediate gears, and the rotation of the one or more sets of intermediate gears corresponds to a greater number of rotations of the output gear. Aspect 17 17. The drive unit of embodiment 16, wherein each set of intermediate gears comprises three gears arranged at a center of and equally spaced around the input gear. Aspect 18 Aspect 17. The drive unit of aspect 16, wherein the one or more sets of intermediate gears are two sets of intermediate gears, a first set of intermediate gears connecting the input gear to a second set of intermediate gears, and the second set of intermediate gears connecting the first set of intermediate gears to the output gear, thereby providing a rotation ratio from the input gear to the output gear of 1 / 3 rotation to 7 rotations. Aspect 19 A drive unit as described in aspect 14, wherein upon the upward movement of the lower portion, a corresponding force conversion occurs, converting an input linear force into an output rotational force, the force conversion resulting from the corresponding movement of the connection and the lower portion and the helix drive relative to each other. Aspect 20 20. The drive unit of claim 19, wherein the helical drive is rotatable relative to the lower portion, and wherein rotation of the helical drive is induced by the upward movement of the lower portion. Aspect 21 A drive unit as described in aspect 13, wherein the machining assembly includes an insert that connects at one end to the output gear of the planetary gear device, and the other end of the insert is configured to connect to a tool. Aspect 22 22. The drive unit of claim 21, further comprising the tool, wherein the tool is a female thread cutting tool and the rigid structure is a material that is machined by the female thread cutting tool. Aspect 23 1. A lubrication system for use with tooling usable with a metalworking press or other machine, comprising: a housing configured to be placed below a material to be machined by a machining press, said housing having a central recess forming a lubricant reservoir and a depressible upper surface that induces upward emission of lubricant from said recess onto the material to be machined when said housing is depressed; A lubrication system comprising: Aspect 24 24. The lubrication system of claim 23, wherein the housing includes a die, and the upper surface of the die is configured to be depressed to induce downward contact by the material to be machined resulting from a corresponding force applied by the tool drive unit to the material. Aspect 25 A lubrication system as described in aspect 24, wherein the lubrication system is configured for a drive unit for a female thread cutting tool, and the upward emission of lubricant onto the material to be machined includes application of the lubricant below and above a pre-drilled hole, as well as application of the lubricant to an area formed inside the pre-drilled hole. Aspect 26 24. The lubrication system of claim 23, further comprising a piston and a valve housed within the lubricant reservoir, wherein depression of the upper surface corresponds to downward movement of the piston within the reservoir and to upward emission of the lubricant from the reservoir via the valve. Aspect 27 27. The lubrication system of claim 26, further comprising a separate reservoir for containing additional lubricant and a separate valve connecting the lubricant reservoir with the separate reservoir, wherein when the downward contact from the top surface of the housing is removed, the piston rises in the lubricant reservoir and a corresponding vacuum within the reservoir results in the addition of additional lubricant to the reservoir via the separate valve. Aspect 28 1. A tooling assembly for use with a metalworking press or other machine, comprising: an upper portion and a lower portion, said upper portion and lower portion being operably coupled; a head portion operably coupled to the upper portion and configured for downward movement in contact with the machine Ramstrom; a drive unit including a helix drive and a transmission assembly operably coupled to the drive, the head portion being operably coupled to the helix drive; a work assembly operably connected to the transmission assembly; Equipped with downward linear movement of the head section from a ram stroke of the machine results in rotational movement of the helix drive relative to the head section, the rotational movement of the helix drive results in enhanced rotational movement of the transmission assembly, and the enhanced rotational movement of the transmission assembly results in corresponding rotational movement of the work assembly; Tool assembly. Aspect 29 29. The tool assembly of claim 28, wherein the transmission assembly comprises a planetary gear set. Aspect 30 29. The tool assembly of claim 28, wherein the transmission assembly is modular and removable from the helix drive. Aspect 31 29. The tool assembly of claim 28, wherein the helix drive is formed with an inclined groove that is the same as the length of the drive. Aspect 32 32. The tool assembly of claim 31, wherein the head portion is formed with one or more sets of grooves that cooperate with the helix drive grooves to increase, decrease, or maintain rotation of the drive.

Claims

1. 1. A drive unit for a tooling tool usable with a metalworking press or other machine, comprising: a first portion and a second portion operably connected to the first portion such that the second portion is movable relative to the first portion, such that when a downward force contacts the first portion and contact occurs between the second portion and a workpiece, a linear upward movement of the second portion relative to the first portion results; a tool assembly; a gearing arrangement operably connected to the tool assembly; a helix drive operably connecting the gearing arrangement to one of the first portion or the second portion; Equipped with said linear upward movement of said second portion results in a corresponding force conversion, converting an input linear force into an output rotational force, said force conversion resulting from coupling and corresponding movement of one of said first portion or said second portion and said helix drive relative to one another; the helical drive is rotatable relative to the second portion, the rotation of the helical drive being induced by the linear upward movement of the second portion; the tool assembly is located below the helix drive; the helix drive is rotatable via a groove formed therein, and a bearing attached to the second portion is configured to be received in and slide along the groove of the helix drive, such that the linear upward movement of the second portion results in rotational movement of the helix drive; Drive unit.

2. the helix drive comprises a helix drive stem having an outer surface formed with a plurality of grooves curving upwardly around and along the length of the helix drive stem; the second portion includes a plurality of bearings each rigidly secured to the second portion, the bearings being respectively received within the grooves of the helix drive stem; the bearing is guided to move upward along the groove of the helix drive stem during the linear upward movement of the second portion relative to the first portion, corresponding to the rotation of the helix drive stem relative to the second portion.

2. The drive unit according to claim 1.

3. The drive unit of claim 2 , wherein the helix drive stem of the helix drive is located below the gearing arrangement in the drive unit.

4. 3. The drive unit of claim 2, wherein the second portion is formed with a recess sized to receive the helix drive stem, the bearings extending from corresponding inner surfaces of the second portion forming the recess, the bearings being spaced apart around the inner surfaces and correspondingly extending into the corresponding grooves of the helix drive stem.

5. 2. The drive unit of claim 1, wherein the gearing arrangement comprises a planetary gear set, an input gear or ring gear of the planetary gear set operatively coupled to the helix drive such that the rotation of the helix drive corresponds to the same rotation of the input gear.

6. The drive unit of claim 5 , wherein the helix drive comprises a casing extending therefrom, the input gear being located within and coupled to the casing.

7. 6. The drive unit of claim 5, wherein rotation of the input gear results in a greater rotation of an output gear of the planetary gear set, the output gear being operatively connected to the tool assembly such that rotation of the output gear corresponds to the same rotation of the tool assembly.

8. 8. The drive unit of claim 7, wherein the planetary gearing includes one or more sets of intermediate or planetary gears operatively connecting the input gear with the output gear, such that the rotation of the input gear corresponds to a greater number of rotations of the one or more sets of intermediate gears and the rotation of the one or more sets of intermediate gears corresponds to a greater number of rotations of the output gear.

9. The drive unit of claim 7 , wherein the tool assembly includes an insert that couples at one end to the output gear of the planetary gear set, the other end of the insert being configured to couple to a tool.

10. 10. The drive unit of claim 9, further comprising the tool, wherein the tool is a female thread cutting tool and the workpiece is a material to be machined by the female thread cutting tool.

11. The drive unit of claim 1 , wherein the first portion is an upper portion of the drive unit and the second portion is a lower portion of the drive unit.

12. 9. The drive unit of claim 8, wherein each set of intermediate gears comprises three gears equally spaced inwardly of the input gear.

13. 9. The drive unit of claim 8, wherein the one or more sets of intermediate gears are two sets of intermediate gears, a first set of intermediate gears connecting the input gear to a second set of intermediate gears, and the second set of intermediate gears connecting the first set of intermediate gears to the output gear, whereby a rotation ratio from the input gear to the output gear is 1 / 3 turn to 7 turns.

14. 1. A tooling assembly for use with a metalworking press or other machine, comprising: an upper portion and a lower portion, said upper portion and lower portion being operably coupled; a head portion operably coupled to said upper portion and configured for linear downward movement in contact with the machine ram stroke; a drive unit including a helix drive and a transmission assembly operably coupled to the helix drive, the head portion being operably coupled to the helix drive; and a tool operably connected to the transmission assembly, the tool being located below the helix drive; Equipped with downward linear movement of the head portion from a ram stroke of the machine results in rotational movement of the helix drive relative to the head portion, the rotational movement of the helix drive results in enhanced rotational movement of the transmission assembly, the enhanced rotational movement of the transmission assembly results in corresponding rotational movement of the tool assembly; the helix drive is rotatable via a groove formed therein, bearings mounted on the top portion are configured to be received in and slide along the grooves of the helix drive to provide rotational movement of the helix drive from the linear downward movement of the head portion, and the head portion is formed with multiple sets of grooves, each of which can be individually linked to cooperate with a groove of the helix drive via a corresponding number of bearings, allowing selective adjustment of the rotation of the helix drive resulting from the linear downward movement of the head portion. Tool assembly.

15. The drive unit of claim 1 , wherein the helix drive is single.

16. The drive unit of claim 1 , wherein the tool assembly is located below and aligned with the helix drive.

17. The tool assembly of claim 14 , wherein the helix drive is single.

18. The tool assembly of claim 14 , wherein the tool assembly is located below and aligned with the helix drive.

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