DE212014000050U1 - System for mounting a tractor unit to a guide rail - Google Patents

Abstract

A mounting mechanism for connecting a welding head tractor unit (200) to a guide rail (100), comprising: a fixed block (F) having a first set (B) of roller devices; like rollers (210, 210A, 210B); a movable plate (M) having a second set of (A) roller devices, the movable plate being movable to adjust the distance between the first and second roller devices; a clamping assembly (C; 240; 640) comprising: a shaft (S) extending from the fixed block (F) and through the movable plate (M); a handle connected to the shaft and movable between an open position for releasing the tractor unit from engagement with the guide rail and a closed position for engaging the tractor unit with the guide rail, the guide rail comprising a first rail track and a second rail track (110 ); and wherein, when the handle is in an open position, a first distance between the first and second roller devices is greater than a width of the guide rail; wherein, when the handle is in a closed position, a first distance between the first and second roller devices is approximately equal to the width of the guide rail.

Description

PRIORITY

The present application is a partial refinement of US Provisional Application No. 13 / 676,170, filed Nov. 14, 2012, which is the priority of US Provisional Patent Application No. 61 / 561,811, filed on Nov. 18, 2011, the contents of which are hereby incorporated by reference is incorporated by reference in its entirety in the present text.

TECHNICAL AREA

Certain embodiments relate to welding systems, devices, and processes. In particular, certain embodiments relate to a system and / or method for mounting a tractor to a guide rail, engaging a tractor drive in a track gear, adjusting an angle of a welding head, and / or adjusting a burner lead / caster angle in brazing, plating -, build, fill, hardfacing, joining and welding applications.

BACKGROUND

This patent document relates to welding systems, devices and processes.

Welding in large industrial applications, such as metal inert gas (MIG) and tungsten inert gas (TIG) tube or plate welding, may involve welding very thick workpieces, for example, in an orbital welding process. For example, in an orbital welding process, the arc welding head may be rotated along a guide rail around the workpiece, for example, rotating the welding head 360 ° continuously around the workpiece, such as a pipe, or rotating the head 180 ° around the pipe on one side of the pipe, and then repeating the head rotation on the other side of the pipe. Many welding applications require precision welding, from small standard workpieces to larger scale ones. Welding systems can be designed to include a welding head and a guide rail with which the welding head is movably engaged. For example, the welding head may be mounted on a train drive unit to move along the guide rail. For example, some orbital welding systems may include the guide rail in a ring or orbital configuration that engages around a workpiece to guide and move the welding head along the weld joint. To assemble the guide rail around the workpiece, a plurality of rail segments may be interconnected to form the full guide rail and secure the guide rail to the workpiece, for example 360 ° around the workpiece.

Accordingly, in conventional welding systems, the quality of a weld may be affected by the way a tractor is mounted on a guide rail because the assembly may affect how smoothly the tractor travels along the guide rail. For example, a misassembled tractor may flex on a rail race as it moves around the rail race. The flexing may cause the tungsten electrode of the welding head attached to the tractor unit to move. For example, the tungsten electrode may angle inboard when the tractor is in the "12 o'clock" position and angle outward when in the "6 o'clock" position. This can happen if the tractor unit is not firmly mounted to the rail so that there is a tendency to drift due to vibration and impact. In addition, mounting mechanisms may be fragile and easily damaged, for example jamming, and tractor unit components may be damaged by over-tightening.

In addition, misalignment of the feed drive gear in the tractor unit to the track rail sprocket may also cause problems with weld quality and delays in the welding process. For example, if the mass center of gravity of the weld head shifts due to debris on the track gear, for example, the gears on the feed drive gear and track gear may jam, especially if the system has not been properly aligned. To reduce the problems associated with misalignment of the feed drive gear on the track gear, the feed rate of conventional train units may need to be set to a low value.

In addition, the mounting of the tractor unit to the guide rail may be troublesome due to the weight of the tractor unit. Typically, the rollers or wheels must be manually aligned on a tractor unit before the rollers or wheels can engage the guide rail and hold on to it. That is, while the tractor unit is mounted on the guide rail, an operator must physically move the tractor unit back and forth during adjustment of the engagement mechanism until the wheels or wheels of the tractor unit are properly seated on the guide rail are aligned. Because train units are relatively heavy, the assembly process can be physically demanding, especially when the operator has to counteract gravity during assembly of the tractor unit.

Furthermore, the orientation of the electrode with respect to the weld puddle and the arc length are important for drawing correct welds, especially when mechanical oscillation is used. However, conventional systems and methods for aligning welding heads are not ideal in that they can produce inferior welds. For example, illustrated 12 a prior art system for performing a fillet weld by means of an inert gas tungsten arc welding (GTAW) system ( 50 ). For brevity, only the components that are relevant to this meeting are illustrated. The GTAW system ( 50 ) contains a welding torch ( 10 ), which is oriented so that the burner ( 10 ), for example, perpendicular to the surface of the welding puddle ( 40 ) is arranged as through the line ( 12 ). The burner ( 10 ) is with a welding base ( 30 ), which provides mechanical oscillation, as indicated by the arrow ( 32 ). During the burner ( 10 ) over the sweat puddle ( 40 ), the length of the arc changes ( 5 ), ie the distance between the tip of the tungsten electrode ( 15 ) and the surface of the welding puddle ( 40 ) changes. Accordingly, to maintain the correct arc length, an Arc Voltage Control (AVC) assembly ( 20 ) the burner ( 10 ) in the appropriate direction along the arrow ( 22 ), while the mechanical oscillation of the burner ( 10 ) in one direction ( 32 ) emotional. That is, the AVC assembly ( 20 ) adjusts the distance between the burner ( 10 ) and the sweat puddle ( 40 ) to the arc ( 5 ) to the desired length. However, because the stroke direction of the AVC assembly is as shown by the arrow ( 22 ), other than the orientation of the burner ( 10 ), as through the line ( 12 ), the resulting weld may be of poor quality. Inferior welds may also be due to a limited AVC stroke (limited to, for example, about 1 inch AVC stroke) and / or limited rotation of the AVC assembly (limited to, for example, about 40 degrees) with respect to the torch and / or or the workpiece (the welding puddle) come. Furthermore, inferior welds may occur if the attachment between the welding torch and the AVC assembly and / or the fixture between the AVC assembly and the base unit is not stable because it is, for example, unsafe and / or faint, and / or if the fasteners have excessive wear due to, for example, overstress and / or poor durability.

In addition, in conventional welding systems, the burner electrode lead / lag angle adjustment is limited, typically in the range of 0 to 5 °, in some cases up to 12 °. Limited lead / lag adjustment also limits the flexibility in setting up the weld configuration. In addition, in conventional systems, the burner advance / trailing adjustment mechanisms have numerous disadvantages, such as welding head component scratching, weld head slippage due to weak locking mechanisms, difficult access to the leading / trailing angle mechanisms, and uneven leading / trailing angle settings, just to name a few.

Further limitations and disadvantages of conventional, traditional and proposed approaches will be recognized by those skilled in the art by comparing such approaches to embodiments of the present invention set forth in the remainder of the present application with reference to the drawings.

SUMMARY

Exemplary techniques, systems, and devices are described for welding systems that use a guide rail, for example, a guide rail with a curved rail track profile. However, the exemplary embodiments discussed below are not limited to curved rail systems and may be incorporated into any mobile welding system, whether mounted on a curved rail, a straight rail, or on another type of rail or in a stationary welding head.

In order to minimize or even eliminate the limitations and disadvantages of conventional, conventional and proposed approaches, the invention proposes a mounting mechanism for connecting a welding tractor to a guide rail according to claim 1. Preferred embodiments may be taken from the dependent claims. In one embodiment, a mounting mechanism for connecting a tractor unit to a guide rail is provided. The mounting mechanism includes a fixed block with a first set of roller devices and a movable plate with a second set of roller devices. The movable plate can be adjusted, thereby adjusting the distance between the first and second roller devices. There will also be a clamp assembly provided to adjust the movable plate relative to the fixed block. The clamp assembly includes a shaft extending from the fixed block and through the movable plate, and a cam spring between the fixed block and the movable plate for biasing the movable plate away from the fixed block. A cam handle is connected to the shaft and can be moved between open and closed positions. In the open position, the tractor unit is not engaged with the guide rail, and in the closed position, the tractor unit is engaged with the guide rail. When the cam handle is in the open position, the distance between the roller devices is greater than the width of the guide rail. When the cam handle is in the closed position, the distance between the roller devices is approximately equal to the width of the guide rail.

In a variant of the mounting mechanism, the shaft is adjustably screwed into the fixed block. Alternatively, an axis is provided between the cam handle and the shaft; the axle can be adjustably screwed onto the shaft.

The shaft may include a first threaded portion for engaging the fixed block and a second threaded portion for receiving the axle. In one arrangement, the shaft has a first screwing direction for engaging the block and a second screwing direction for receiving the axle. Alternatively, the shaft may have a first pitch for engaging the block and a second pitch for receiving the axle.

In another arrangement, an over-clamping spring may be present between the cam handle and the movable plate. The over-clamp spring may have greater rigidity than the stiffness of the cam spring.

The first and second roller devices are configured to roll on the rail and may include one or more pivotal blocks, with one or more rollers located on each of the pivoting blocks. The pivot blocks may be configured to pivot so that the rollers on each of the pivot blocks conform to a profile of the track while the tractor unit engages the guide block. The clamping assembly is configured to operatively engage the rollers of each of the pivot blocks when the clamping assembly is in a closed position.

Each of the pivoting blocks may include a locking mechanism configured to prevent the respective pivoting blocks from pivoting once the tractor unit has engaged the guide rail. The locking mechanism may be a bush arranged so that friction prevents pivoting of the pivot blocks when the tractor unit has engaged the guide rail. For example, the guide rail may have a profile that is concave, convex, straight, or a combination thereof. The guide rail can have tracks measuring from 1/16 '' to 2 ''. The shapes of the first and second tracks of the guide rail may be round, square, triangular or octagonal.

BRIEF DESCRIPTION OF THE DRAWINGS

The above and / or other aspects of the invention will become more apparent by describing in detail exemplary embodiments of the invention with reference to the accompanying drawings, in which:

1A . 1B , and 1C illustrate an exemplary guide rail having a tubular rail track;

1D FIG. 12 illustrates an exemplary multi-point roll of a weld head puller mounting bracket connected to an exemplary tubular rail track; FIG.

2A and 2 B illustrate an example mounting mechanism for a welding head tractor unit;

3A and 3B illustrate an exemplary pivot feed gear engagement for a weld head tractor unit;

3C Fig. 10 illustrates an exemplary welding head tractor unit moving along concave, convex, straight and variable guide rails;

4 FIG. 12 illustrates an exemplary adjustable welding head angle mechanism of an AVC assembly of a welding head tractor; FIG.

5A and 5B illustrate an exemplary swiveling lead / lag burner angle mechanism for a welding system;

6A and 6B illustrate an exemplary latching mechanism incorporated in the mounting mechanism of FIG 2A and 2 B can be integrated;

7 FIG. 12 illustrates an exemplary embodiment of a weld head angle adjustment system that has been integrated into an orbital rail welding system; FIG.

8th FIG. 12 illustrates an exemplary embodiment of an angle adjustment mechanism incorporated in the weld head angle adjustment system of FIG 7 can be installed;

9 FIG. 5 illustrates an exemplary welding system that may be used in brazing, cladding, build, fill, hardfacing, bonding, and welding applications; FIG.

10 FIG. 12 illustrates an exemplary embodiment of a lead / lag burner angle adjustment mechanism incorporated in the systems of FIGS 5A . 5B and 9 can be integrated;

11A to 11C Illustrate exemplary embodiments of a lead / lag burner angle adjustment mechanism incorporated in the systems of FIGS 5A . 5B and 9 can be integrated;

12 illustrates a welding system of the prior art;

13A and 13B illustrate an intersection of a roller contact line with a rail track connection interface 1A . 1B and 1C ;

14A and 14B 12 illustrate exemplary pivot angles for the pivot blocks of the exemplary mounting mechanism included in FIGS 2A . 2 B . 6A and 6B is illustrated;

15 FIG. 12 illustrates an exemplary pivot block / roller assembly according to an embodiment of the present invention; FIG.

16A to 16D illustrate a tractor unit incorporating the exemplary pivot block / roller assembly in FIG 15 used;

17A to 17D illustrate exemplary configurations of serrated or toothed surfaces included in the angular adjustment mechanism of FIG 8th can be integrated;

18A Figure 11 illustrates a front view of the tractor unit with an alternative mounting mechanism in an open position;

18B illustrates a front view of the tractor unit with the alternative mounting mechanism of 18A in a closed position;

19 Figure 12 illustrates a perspective view of the locking mechanism assembly of the alternative mounting mechanism in a closed position;

20A Figure 11 illustrates a broken plan view of the latch mechanism assembly of the alternative mounting mechanism in an open position; and

20B FIG. 12 illustrates a broken plan view of the locking mechanism assembly of the alternative mounting mechanism in a closed position. FIG.

Like reference symbols and designations in the various drawings indicate like elements.

DETAILED DESCRIPTION

Exemplary embodiments of the invention will now be described below with reference to the accompanying figures. The described exemplary embodiments are intended to facilitate the understanding of the invention and are not intended to limit the scope of the invention in any way. Like reference numbers always refer to like elements.

There are shown examples illustrating various welding system techniques, systems, and devices that use a guide rail having two or more rail segments connected to guide the welding head and a welding head pulling device that drives the welding head along the guide rail during a welding operation.

A guide rail having two or more rail segments may be constructed to allow easy disengagement of the guide rail from a workpiece, such as a large pipe. One of the technical challenges in joining two or more rail segments to form a guide rail is the presence of a discontinuity between two connected rail segments. Such discontinuity may affect the advancing motion of the welding head, for example, by causing jumping, interrupting or stuttering of the continuous movement of the welding head in the welding gap. This can compromise the precision of the welding operation and lead to imprecise welding, such as a deterioration in the integrity and strength of the weld joint. Precision defects in welding can have serious consequences for a variety of welding applications. An imprecise weld may be related to the movement of a welding head tractor along a guide rail (for example, mounted around a workpiece, such as a pipe), which may be ...

... can be interrupted during the transition from one rail segment to the next rail segment on the vertical joint. For example, rail discontinuities at the rail segment transition region may cause the unit to skip or stutter until the transition point has passed, which may result in an inexpert or unacceptable weld. Welding rails that provide single point contact rollers on the rail tracks can be sensitive to uneven regions along the track rail.

In one aspect, the disclosed technology may include a guide rail configured to provide a planar interface with a weld head tractor unit (eg, a butt weld apparatus for orbital welding applications) along the guide rail, including a smooth and curved edge, for smooth movement of the weld head and to ensure a smooth and continuous transition at the interface between two adjacent rail segments. The curved edge of the rail may have various desired shapes, and for the following example a circular edge is assumed.

1A shows a three-dimensional view of an exemplary guide rail ( 100 ), the two rail tracks ( 110 ) configured as tubular tracks with circular outer surfaces. The two tubular rail tracks ( 110 ) are on the outside of the guide rail ( 100 ), which is shaped as a ring guide rail, which may be mounted on a cylindrical workpiece, such as a pipe. Each tubular rail track ( 110 ) is divided by two or more rail segments ( 111 ) and ( 112 ) educated. A rail segment, for example the rail segment ( 111 ) connects each rail track through at least one rail cross member ( 120 ) between respective engagement positions on the two rail tracks 110 are engaged. Between the two rail tracks 110 is a track gear ring ( 130 For example, at a middle position between the two rail tracks 110 provided to engage the Schweißkopfzugeinrichtung which transports the welding head. In this example, two semicircular rail segments ( 111 ) and ( 112 ) with each other at two joints ( 115 ) and ( 116 ) connected.

1B shows a side view of the tubular guide rail ( 100 ) in 1A , In this example, each tubular rail track ( 110 ) a transition between two rail segments ( 111 ) and ( 112 ) at the junction ( 115 ), which forms an interface at an acute angle with respect to the rail. The picture insert in 1B shows that the end facet of each rail segment ( 111 ) or ( 112 ) is an angular facet and that two opposite facets of the rail segments ( 111 ) and ( 112 ) to the angled connection interface (FIG. 117 ) to build. This construction creates a smooth transition across the connected region. When operating a welding system with such a rail, a welding head pulling unit moves on the tubular rail track (FIG. 110 ), via the angled connection interface ( 117 ) of two rail segments of the guide rail ( 100 ) away. The non-perpendicular orientation of the angled connection interface ( 117 ) allows a non-abrupt, smooth transition from one rail segment to the adjacent rail segment to ensure a smooth and continuous weld that is filled into the weld gap. As in the 13A and 13B illustrates why a non-perpendicular transition is smoother, that the contact points (or contact line) of the rollers lie on a line that is perpendicular to the rail (see 13A ). If the connection interface is also vertical, then all the contact points of the rollers encounter the transition at the same time, causing a jump or stutter. However, in the present invention, the connection interface ( 117 ) angled. Accordingly, the roles intersect the connection interface ( 117 ) only at a single point, while the contact with the rail track ( 110 ) is maintained at the other points along the line of contact.

There may be various materials for forming the rail tracks in the 1A and 1B be used. An exemplary track rail of the disclosed technology may be made of a metal, polymer, ceramic, or composite material. The shape of the exemplary track rail may include a tubular geometry having a circular cross-section that may be hollow, filled or partially filled. Other shapes of the exemplary rail track are a rectangular or square shape with curved or rounded edges, with one, two, three, or four edges rounded to one of many possible degrees of curvature, and the rail track may be hollow, filled, or partially filled. The exemplary track may include other shapes in which the leading edge includes a curved contour. The curved contour shape of the exemplary rail track may increase the surface area between the rail track and the tractor unit (e.g., increasing the number of contact points, providing greater support to the train unit through the rail track).

1C shows a further side view of the guide rail ( 100 ), which is the rail segment ( 111 ) shows which rail cross member ( 120 ) between several rail tracks, for example the two rail tracks, exemplified by the rail tracks ( 110 ) are shown. The rail cross element ( 120 ), the two rail tracks ( 110 ) in such a way that they are aligned substantially parallel to each other. This in 1C shown rail segment ( 111 ) contains several rail cross members, which the rail tracks ( 110 ) connect. At the rail cross member ( 120 ) can also be attached to a running track ring gear, such as the running track ring gear ( 130 ) shown sprocket. The rail segment ( 111 ) also includes a plurality of rail cross members on which the track gear ring ( 130 ) connected is.

1D shows the exemplary tubular rail track ( 110 ) having a rounded shape or geometry capable of providing a plurality of contact points for a mounting component of a welding head tractor, for example a mounting component ( 150 ) to the welding head along the rail track ( 110 ) to move. The exemplary mounting component ( 150 ) may contain rollers or wheels (which are the tubular rail track ( 110 ) at several contact points (or the contact line) ( 161 ) touch). Two multipoint rolls ( 160 ) are in 1D for touching the rail track ( 110 ) and rolling on the curved surfaces of the rail track ( 110 ) as part of the assembly component ( 150 ). In this example, the multipoint rolls ( 160 ) with a pivoting block ( 170 ) and can be about their respective roller rotation axis ( 165 ) when moving along a rail track ( 110 ) roll. The exemplary tubular rail track ( 110 ) of the guide rail ( 100 ) may provide a plurality of connection points to the welding head tractor unit, so that when the unit drives over bumps of the guide rail, a more even feed is enabled. The tubular geometry of the rail track may allow for an interface that allows the mounting component (FIG. 150 ) is in contact at a plurality of points, which may prevent the tractor unit from traveling in an undesired position, for example due to a left-side or right-side discontinuity, jumping, stuttering or swinging. For example, the multipoint roll ( 160 ) so along the rail with multiple contact points ( 161 ), that at the transition from one segment to another (for example, at the angled connection interface ( 117 )) may be present less interference than if the rail segments were connected vertically.

The disclosed technology includes a tubular rail that can use multi-point contact wheels and angled and / or gradual transition joint that creates a smooth transition of a mounted device (eg, a welding head tractor unit), causing unwanted movements of the assembled device, for example, deflecting, jumping, and stuttering , can significantly reduce. This allows a more precise weld to be made by significantly reducing abrupt, discontinuous movements of the weld head in the weld joint. In addition, the exemplary guide rail may have a reduced overall weight by using tubular members connected by cross members rather than using a solid rectangular rail. The exemplary guide rail may be made with a reduced amount of material (and may be hollow or partially filled, for example). For example, an exemplary guide rail may have a reduced weight due to the geometry and / or material of the track rails or by reducing the volume and / or density of the entire track rail. An advantage of the reduced weight may be that the exemplary guide rail is easier to move to the next welding position. In addition, a reduced weight can also improve manufacturability, for example, by making the guide rail from a plurality of smaller, less complicated parts instead of a single complex part. For example, the manufacturability of an exemplary guide rail can be simplified by forming steel tubes because the steel tube can be completed in a single machining operation rather than, for example, three machine operations as a typical one-piece rail would require. Cross member profiles can be designed to suit any diameter size, for example, with only two altered feature dimensions. The exemplary guide rail can provide long life because of its tubular configuration. The tubular configuration provides a smooth circular contact surface that significantly reduces friction. For example, the exemplary guide rail may be made of a steel material to allow the exemplary guide rail to resist dents and nicks in harsh operating environments so that such dents and nicks on the rail (eg, the tubular rail track) would not interfere with the movement of a mounted weld head tractor unit. The exemplary rail guide may include a track gear rim with gear profiles that may provide for a smoother traction movement. In addition, the exemplary guide rail of the disclosed technology can reduce welding system "facility" factors, such as Example time and quantity and complexity of components.

Exemplary embodiments of the present invention may include a puller assembly puller assembly mechanism that allows the towing unit to be mounted on track rails that may be of various shapes and / or sizes.

2A illustrates a welding head tractor unit ( 200 ) with a towing device mounting mechanism comprising a track rail clamping assembly ( 240 ) contained in 2A is shown in the released position. As can be seen in the front view of the figure, the tractor unit ( 200 ) in the released position on a guide rail (for example, the guide rail ( 100 )) by means of a rolling device or rolling devices, such as wheels and / or rollers to be movably mounted. The track clamp assembly ( 240 ) contains a clamping mechanism ( 220 ), which is operatively connected to a wheel / roller set A. For mounting or dismounting the tractor unit ( 200 ), the clamping mechanism ( 220 ) are turned so that the track clamping assembly ( 240 ) retracts the wheel / roller set A (see front view of 2A ). As part of the exemplary mounting mechanism, in some embodiments, the traction unit ( 200 ) are clamped or released by means of a single clamping action, ie by turning the clamping mechanism ( 220 ) for operating the wheel / roller set A.

The exemplary mounting mechanism may also include a plurality of opposed wheels and / or rollers (FIGS. 210 ), for example wheel / roller sets A and B, attached to the rail track, for example the track ( 110 ), which may be tubular or solid. The total number of wheels and / or rollers ( 210 ) at the train unit ( 200 ) can be eight, for example. However, the tractor may also include more or less wheels and / or wheels ( 210 ) to have. In some embodiments, the wheels and / or rollers (FIGS. 210 ) on pivot blocks ( 211 ) be mounted. Each swivel block ( 211 ) can be at least one wheel or a roller ( 210 ) to have. For example, in some embodiments, each swivel block ( 211 ) two wheels or rollers ( 210 ). Thus, the exemplary eight wheels / castors ( 210 ) four sets of pivoting blocks ( 211 ) with two wheels / rollers mounted on each block. Of course, the number of panning blocks ( 211 ) and the corresponding number of wheels / rollers ( 210 ) according to a number of factors, such as the size and weight of the tractor unit ( 200 ), the size of the diameter of the rail tracks ( 110 ), the size of the wheels / rollers ( 210 However, for typical rail-mounted welding applications, for example orbital welding applications, it is contemplated that four panning blocks ( 211 ), each block ( 211 ) two wheels / castors ( 210 ) and, for example, at a corner of the train unit ( 200 ) is arranged (see, for example 6B ). The pivoting blocks ( 211 ) each contain a central bearing that the respective pivot block ( 211 ) allows pivoting when the traction unit ( 200 ) is solved. There are no restrictions for the swivel angle. However, the assembly of the tractor unit ( 200 ) on the rail tracks ( 110 ), the pivot blocks ( 211 ) to an inward pivot angle of up to 26 ° (see 14A ) and an outward swing angle of up to 10 ° (see 14B ) with respect to a central axis between two pivoting blocks ( 211 ). This pivoting movement allows the rollers ( 210 ), directly to each rail track profile ( 110 ), for example, concave, convex, straight, or any combinations thereof. For size and shape of rail track ( 110 ), and the size of the rail track ( 110 ) may range from, for example, 1/16 inch to 2 inches, and the shape may be, for example, round, square, triangular, octagonal or other shape. Of course, the shape of the wheels and / or rollers ( 210 ) according to the size and shape of the rail track ( 110 ). In addition, the rail track ( 110 ) be either tubular or massive. Furthermore, the configuration of the guide rail ( 100 ) is not limited to that of a ring, and may be, for example, any of the rail configurations shown in FIG 3C are illustrated, ie the convex guide rail ( 391 ), the concave guide rail ( 392 ), the straight guide rail ( 393 ) and the variable guide rail ( 394 ), or another type of rail configuration.

When the train unit ( 200 ), the exemplary mounting mechanism may include a locking mechanism to move the pivot blocks (FIG. 211 ) to lock in place. For example, in some embodiments, each pivot block ( 211 ) a locking socket ( 213 ), which allows free movement without pressure (for example, when the traction unit ( 200 ) is not clamped), and then locked in a fixed position as soon as the tractor unit ( 200 ) is clamped. For example, in some embodiments, the socket (FIG. 213 ) so that when the train unit ( 200 ) is clamped between a sidewall of the tractor unit ( 200 ) and the roles ( 210 ) is compressed, as in the 6A and 6B illustrated. When clamped, the force on the bush ( 213 ) in such a way that the friction of the corresponding pivot block ( 211 ) holds in place when the rollers ( 210 ) on the rail track ( 110 ) roll. In some Embodiments, the locking bushing ( 213 ) made of bronze or other suitable material. When the train unit ( 200 ) is not clamped, then the pivot block ( 211 ) and to the profile of the rail track ( 110 ), for example, concave, convex, even, or any combinations thereof. This construction allows full contact of the tractor unit ( 200 ) with the rail tracks ( 110 ) and a smooth movement of the train unit ( 200 ). Additionally, in some embodiments, an engagement point of the tractor drive gear (FIG. 310 ) (see also 3A ) are aligned directly on the axis of the pivot bearings of the two front pivot blocks, for example, the pivot blocks ( 211 ) located next to the feed drive gear ( 310 ) are located. Thanks to this feature, the train unit ( 200 ) to each rail track ( 110 ) - without further adjustment or modification of the train unit ( 200 ). The orientation of the feed drive gear ( 310 ) on the front support pivot blocks, for example the pivot blocks ( 211 ), can be configured to remain the same for all rail configurations.

As discussed above and in the side view and cross-sectional top view of FIG 2A to see, a clamping mechanism ( 220 ) of the track clamping assembly ( 240 ) the pivoting blocks ( 211 ) of wheel / roller set A. In some embodiments, the clamping mechanism ( 220 ) manually operated and can turn knob ( 221 ) to enable fast manual turning. In some embodiments, the clamp assembly (FIG. 240 ) a heavy-duty screw ( 222 ) contain. The clamping assembly ( 240 ) may contain a coupling or similar mechanism so that the screw ( 222 ) can not be overridden manually or otherwise. The track clamp assembly ( 240 ) also contains a movable side plate ( 224 ), on which, for example, two pivoting blocks ( 211 ) of wheel / roller set A are mounted. In some embodiments, the movable side plate (FIG. 224 ) be configured to slide precisely on linear bearings, for example the four linear bearings ( 230 ). Of course, the present invention is not limited to the use of linear bearings ( 230 ) and / or a screw ( 222 ) to engage and disengage the roller set A, and other methods may be used.

In the fully released position, the distance of the movable side plate ( 224 ) of the exemplary mounting mechanism to the exemplary guide rail (FIG. 100 ) wide enough for the wheels / rollers ( 210 ) not the rail tracks ( 110 ) touch. That is, in the fully released position there is enough clearance between the wheels / rollers ( 210 ) and the rail tracks ( 110 ), so that the train unit ( 200 ) without being hampered by the rail track ( 110 ) can be dismantled. To the wheels / rollers ( 210 ) to the rail tracks ( 110 ) or engage with them, as in 2 B can be seen, the clamping mechanism ( 220 ) are operated so that the pivot blocks ( 211 ), which are the roles ( 210 ) in the direction of the rail tracks ( 110 ) move. Once the wheels and / or rollers ( 210 ) the rail tracks ( 110 ), the panning blocks ( 211 ) pivot freely so that the wheels and / or rollers ( 210 ) to each profile of the rail track ( 110 ), for example, concave, convex, even, or any combinations thereof. Once the clamping mechanism ( 220 ) the track clamping assembly ( 240 ) completely with the rail tracks ( 110 ) prevents the locking bushing ( 213 ), that the pivot blocks ( 211 ), as discussed above. In some embodiments, the surface of each wheel or roller ( 210 ) in the clamped state, several contact points ( 215 ) with the rail track ( 110 ), for example from two points to one line of contact. Of course, in other embodiments, the wheels / rollers ( 210 ) the track ( 110 ) only at a single point. In the embodiments described above, the wheel / roller set A was moved to the tractor unit (FIG. 200 ) on the guide rail ( 100 ) or disconnect from it. However, the present invention is not limited to moving only the wheel / roller set A, and the wheel / roller set B or both wheel / roller sets A and B by the clamping mechanism ( 220 ) to operate the tractor unit ( 200 ) to the guide rail ( 100 ) or to disconnect from it.

The exemplary mounting mechanism of the disclosed technology may allow convenient and easy assembly of a welding head to various profiles, shapes and sizes of rail tracks, thereby eliminating the need to make multiple adjustments for each rail configuration. The exemplary mounting mechanism, as discussed above, provides a quick and elegant way to mount a tractor unit (FIGS. 200 ) by means of a single adjustment (for example the rail track clamp assembly ( 240 ), which the clamping mechanism ( 220 ), so that no further adjustments are necessary. Exemplary embodiments of the above-discussed mounting mechanism may provide benefits such as reducing and / or eliminating the flexing and wearing of a welding head tractor and other components, and enabling a virtually jerkless movement of the welding head tractor along a guide rail at any speed, for example, at low speeds and high Speeds. In addition, the implementation of the exemplary embodiments of the above-discussed mounting mechanism may allow to mount tow units of any size and weight, to handle under conditions that are extremely demanding or where there is a high risk of misapplication, and in a simple manner on the guide rail clamp and release from it.

In another aspect, the disclosed technology may include a tractor mounting mechanism that is capable of mounting a weld head tractor to multiple shapes and sizes of a rail track.

The manner in which a welding head tractor unit is mounted on a guide rail can affect the quality of the weld according to the degree of uniformity of movement of the tractor along the guide rail. For example, a weld head may bend on a rail ring, which may cause tungsten to angle in at 12 o'clock and angle outward at 6 o'clock. This can happen if the welding head is not firmly mounted to the rail so that there is a tendency to drift due to vibration and impact. In addition, mounting mechanisms can be fragile and easily damaged, for example, jamming, and damage to welding head components due to over tightening can occur.

2A 1 shows an exemplary mounting mechanism of an exemplary welding head tractor unit (FIG. 200 ) which includes a side wheel track roller clamping assembly shown in the released position. As can be seen in the front view of the figure, the tractor unit ( 200 ) on a guide rail (for example the guide rail ( 100 )) by means of a single clamping action as part of the exemplary mounting mechanism. The exemplary mounting mechanism may include a plurality of opposed wheels and / or rollers, for example, eight opposed wheels / rollers (FIGS. 210 ), which may be adapted to the rail tracks, for example the tubular rail track ( 100 ). The exemplary eight wheels / castors ( 210 ) can consist of four sets of panning blocks ( 211 ), with two rollers or wheels mounted on each block. The pivoting blocks can each be adapted directly to their own central bearing to any size and shape of a rail. Each pivot block may have a locking bronze bushing which allows free movement without pressure and then locked in a fixed position as it is clamped. This design allows full contact of the tractor unit with the rail tracks and a smooth movement of the tractor unit. In addition, an engagement point of the tractor drive gear may be directly aligned with the axis of the pivot bearings of the two front pivot blocks. Thanks to this feature, the traction device can adapt to any rail without further adjustment or modifications of the drawbar. The orientation of the drive gear on the front support pivot blocks, for example, the pivot blocks ( 211 ), can be configured to remain the same for all rail configurations. As in the side view and the cross-sectional top view of 2A to see, a clamping mechanism ( 220 ) with two rotary knobs the four pivoting blocks ( 211 ) engage in a quick manual turn. The clamping mechanism ( 220 ) may contain a heavy duty screw that can not be manually overrun. The movable side plate, on which two pivoting blocks are mounted, may be configured to precisely slide on four linear ball bearings, for example the linear bearings ( 230 ). In the released position, the distance from the exemplary mounting mechanism to the exemplary guide rail (FIG. 100 ) wide enough for the wheels / rollers ( 210 ) not the rail tracks ( 110 ) touch. To the roles ( 210 ) to the rail tracks ( 110 ), as in 2 B can be seen, the clamping mechanism ( 220 ) the pivoting blocks ( 211 ), the wheels / rollers ( 210 ) in the direction of the rail tracks ( 110 ) bring. In the clamped state, the wheels are connected to the rail track via several contact points. The mounting mechanism may be configured to support all wheels / rollers ( 210 ) together.

The exemplary mounting mechanism of the disclosed technology may allow convenient and easy assembly of a welding head to various shapes and sizes of rail rings, thereby eliminating the need to make multiple adjustments for each rail configuration. The exemplary mounting mechanism provides a quick and elegant way of mounting a tractor unit with a single helical gear (for example, a mounting knob). 220 )), so that no further adjustments are necessary. This can provide benefits such as reducing and / or eliminating bowing and wear, and enabling virtually jerk-free movement of a welding head tractor along a guide rail at any speed, for example at low and high speeds. In addition, the implementation of the mounting mechanism may allow traction devices of any size and weight to be mounted, handled under conditions that are extremely demanding, or where there is a great risk of misuse. and easy to clamp on the guide rail and to solve from this.

In some embodiments, the roles are ( 210 ) are dimensioned so as to permit the assembly of the tractor unit ( 200 ) on the guide rail ( 100 ) enable. Like in 15 illustrated, the wheels / rollers ( 210 ) on each pivot block ( 211 ) have different widths. The wheel / the roller ( 210B ) may have a width (W2) smaller than the width (W1) of roll ( 210A ). The widths (W2) and (W1) are adjusted so that when the clamping mechanism ( 220 ) the train unit ( 200 ) in the released position, the rail tracks ( 110 ) of the guide rail ( 100 ) on the wheels / rollers ( 210B ), but not on the wheels / rollers ( 210A ) can pass by.

For example, as in 16A illustrated, the wheels / rollers ( 210A ) in the inner section of the tractor unit ( 200 ), and the wheels / rollers ( 210B ) are located on the outer section. When the train unit ( 200 ) is in the released position, the distance between opposing inner wheels / rollers ( 210A ) D1, and the distance between opposing outer wheels / rollers ( 210B ) is D2. Because the widths of the outer wheels / rollers ( 210B ) are set smaller than the widths of the inner wheels / rollers ( 210A ), the distance D1 is smaller than the distance D2. The distance D2 is set so that it is slightly larger than the widest section of the rail track ( 110 ), and the distance D1 is slightly smaller than the widest section of the rail track ( 110 ).

For example, as in 16A shown, the track rails ( 110 ) adjusted so that the distance between the outermost sections of the rail tracks ( 110 ) D3 is. Accordingly, the released position of the tractor unit ( 110 ) is set so that the distance D2 is greater than the distance D3 and the distance D1 is smaller than the distance D3. Why fit when the train unit ( 200 ) first on the guide rail ( 100 ), the outer wheels / rollers ( 210B ) over the rail tracks ( 110 ), as in 16B shown. The train unit ( 200 ) is then on the inner wheels / rollers ( 210A ), when the rail tracks ( 100 ), as in 16C shown. The width (W1) of the inner rollers ( 210A ) is set so that the train unit ( 200 ) securely on the section of wheels / rollers ( 210A ), which is the leading tracks ( 110 ) touched. Once the train unit ( 200 ) on the rail tracks ( 110 ) rests, the clamping mechanism ( 220 ) to operate the tractor unit ( 200 ) on the guide rail ( 100 ). When the clamping mechanism ( 220 ), the track rails ( 110 ) and the wheels / rollers ( 210A ) and ( 210B ) due to the conical shape of the inner wheels / rollers ( 210A ) guided in the correct orientation, as in 16D shown. During the locked state, the swivel block ( 211 ) with the wheels / rollers ( 210A ) and ( 210B ) in the manner discussed above. Of course, the width (W2) of the wheels / rollers ( 210B ) adjusted so that in the clamped condition sufficient contact surface between the wheels / rollers ( 210B ) and the rail tracks ( 110 ), so that the train unit ( 200 ) can be operated safely.

The clamping mechanism ( 220 ) can be configured so that the released position will be the correct distances D1 and D2 on the wheels / rollers ( 210A ) respectively. ( 210B ) for rail tracks ( 110 ) with a width D3. In some embodiments, the clamping mechanism ( 220 ) several released settings according to rail tracks ( 110 ) with different widths D3. That is, a single train unit ( 200 ) may be configured to be attached to guide rails ( 100 ) with a varying width D3, which may range from, for example, 2 to 12 inches. A single train unit ( 200 ) may be configured to be connected to all or only some of the guide rails ( 100 ) that fall into this area. Of course, other widths and areas are possible. In some embodiments, an indicator or operator-configurable end stop (not shown) may be inserted into the clamping mechanism (FIG. 220 ), so that the clamping mechanism ( 220 ) Reliably to the corresponding width D3 of the various guide rails ( 100 ) can be opened. Thus, exemplary embodiments of the present invention allow the traction unit ( 200 ), to the guide rail ( 100 ), without first pulling the train unit rollers ( 210 ) on the rail tracks ( 110 ). In addition, the operator need not worry about the tractor unit slipping past the inner wheels / rollers and damaging the feed drive gear and / or the track gear when the tractor unit is assembled or disassembled.

In some example embodiments, the present invention may include a feed drive gear engagement mechanism for a weld head tractor unit which, inter alia, easily engages and disengages the tractor drive gear from a track gear rim so that an operator can quickly position the weld head tractor and the operator Traction unit can operate at any desired feed rate, for example, slow or fast. 3A illustrates a train unit ( 300 ), which may be mounted on a guide rail, for example, the guide rail ( 100 ), as in the 1A - 1C illustrated. The guide rail ( 100 ) includes a track gear rim ( 130 ) by the feed drive gear ( 310 ) of the train unit ( 300 ) is engaged. The feed drive gear ( 310 ) and the track gear rim ( 130 ) may have an optimal gearing configuration to allow the traction unit ( 300 ) evenly along the guide rail ( 100 ) to move. It should be noted that although the exemplary embodiments are described with reference to a train 300 ), which are attached to the guide rail ( 100 ), the present invention is not limited in this respect, since the exemplary feed drive gear engagement mechanism can be integrated into other types of train units, and not only those which are mounted on the type of guide rails, which in 1 are illustrated. In addition, the present invention may be used on guide rails of a variety of different configurations. For example, as in 3C 1, a traction unit incorporating exemplary embodiments of the feed gear engagement mechanism, as discussed further below, provides smooth feed along convex guide rails (FIGS. 391 ), concave guide rails ( 392 ), straight guide rails ( 393 ) and variable guide rails ( 394 ), just to name a few.

As in the 3A and 3B 1, the feed drive gear engagement mechanism may include a clutch lever (FIG. 320 ), which, when actuated, quickly moves the feed drive gear ( 310 ) with the track gear rim ( 130 ) or disengages from this intervention. For example, in some embodiments, when the clutch lever ( 320 ) is rotated to a first position (see 3A ), a connecting element ( 311 ) the feed drive gear ( 310 ) with the track gear rim ( 130 ) and when the clutch lever ( 320 ) is rotated to a second position (see 3B ), the connecting element ( 311 ) the engagement between the feed drive gear ( 310 ) and the track gear rim ( 130 ). In some embodiments, the connector includes ( 311 ) a pivot point and a pivot pin ( 312 ). The pivot pin ( 312 ) is connected to the connecting element ( 311 ), so that the connecting element ( 311 ) in a tilting movement about the pivot pin ( 312 ) is pivoted around to the feed drive gear ( 310 ) with the track gear rim ( 130 ) and to be released from this intervention. For example, a first end of the connecting element (FIG. 311 ) by a coupling arm ( 321 ), while a second end of the connecting element ( 311 ) connected to the feed drive gear ( 310 ), the drive gear ( 310 ) with the track gear rim ( 130 ) and disengages from this engagement. In further exemplary embodiments, the clutch lever ( 320 ) an eccentric cam section ( 320A ), which with the coupling arm ( 321 ) at a point on the cam portion (FIG. 320A ) which is offset from the center of its elongated section (see 3A and 3B ). In some embodiments, the coupling arm ( 321 ) with the cam portion ( 320A ) at a point located on the central axis of the elongated portion of the cam portion (Fig. 320A ) lies. Accordingly, the coupling arm pivots ( 321 ) due to this staggered cam configuration when the clutch lever ( 320 ) is moved to the first position, the connecting element ( 311 ) so that the drive gear ( 310 ) is engaged. Similarly, due to the staggered cam configuration, the connector ( 311 ) disengaged when the clutch lever ( 320 ) is moved to the second position. Thus, the exemplary configuration of the clutch lever ( 320 ) an operator, the train unit ( 300 ) quickly and, if necessary, at any time on the guide rail ( 100 ) to reposition. In addition, if the cam section ( 320A ) is moved to the first position, the cam crosses the central axis of its elongate portion, so that the clutch lever ( 320 ) at the bottom of the tractor unit ( 300 ), instead of opening towards the second position. Accordingly, the cam ( 320A ) so that the clutch lever ( 320 ) is not accidentally moved out of position when the tractor unit ( 300 ) is shaken, for example, due to material debris on the track gear ( 130 ). In some embodiments, the clutch lever ( 320 ) easily accessible to the operator; for example, it is located on the welding head tractor unit ( 300 ). However, the clutch lever ( 320 ) everywhere on the train unit ( 300 ), as long as the body does not control the advance of the tractor unit ( 300 ) or impedes the welding process. In addition, although some embodiments of the engagement mechanism utilize a single pivot point, the present invention is not limited in this regard, and the linkage mechanism between clutch levers (FIGS. 320 ) and drive gear ( 310 ) can contain any number of pivot points or no pivot points.

In some embodiments, the feed gear engagement mechanism may include an engagement biasing mechanism (FIG. 313 ), which provides a biasing force to the drive gear ( 310 ) so that it engages with the track gear ( 130 ) remains. In some embodiments, the engagement biasing mechanism ( 313 ) it the drive gear ( 310 ) to retract far enough to be aware of debris on the track gear ( 130 to drive away) to help alleviate problems such as jamming gears and / or moving the welding head on the tractor unit ( 300 ). After the drive gear ( 310 ) has passed the material debris, the engagement biasing mechanism ( 313 ) help the drive gear ( 310 ) again in engagement with the track gear ring ( 130 ) bring to. In some embodiments, the engagement biasing mechanism is ( 313 ) arranged so that it with the connecting element ( 311 ) is operatively connected there, where the coupling arm ( 321 ) is attached (see 3A ). Of course, the engagement biasing mechanism ( 313 ) may also be disposed at other points in the feed gear engaging mechanism, as long as a biasing force on the drive gear ( 310 ) acts to guide the track gear ( 130 ) to engage. In some embodiments, the engagement biasing mechanism (FIG. 313 ) consist of at least one spring, but in other embodiments, other types of biasing devices may be used. In some embodiments, the feed gear engagement mechanism may also include a retraction biasing mechanism (FIG. 314 ) to ensure that the drive gear ( 310 ) in engagement with the track gear ring ( 130 ) remains. In some embodiments, the withdrawal biasing mechanism (FIG. 314 ) are arranged so that it is connected to the connecting element ( 311 ) is operatively connected there, where the coupling arm ( 321 ) is attached (see 3B ). Of course, as in the case of the engagement biasing mechanism ( 313 ) - the withdrawal biasing mechanism ( 314 ) may also be located at other points in the feed gear engaging mechanism as long as a biasing force is applied to ensure that the drive gear ( 310 ) out of engagement with the track gear ring ( 130 ) remains released when in the disengaged position. In some embodiments, the withdrawal biasing mechanism (FIG. 314 ) consist of at least one spring, but in other embodiments, other types of biasing devices may be used.

For the type of gear configuration for the feed drive gear ( 310 ) and the track gear rim ( 130 ), there are no restrictions, for example spur gear with spur gear, worm wheel, etc., as long as the drive gear ( 310 ) the train unit ( 300 ) along the guide rail ( 100 ) can move. In some embodiments, as in 6A see, contains the feed drive gear ( 310 ) a drive gear section ( 315 ) and at least one drive roller section ( 316 ) on at least one side of the drive gear section ( 315 ). For the construction of the drive roller section ( 316 ) and the drive gear section ( 315 ) are so far no restrictions, as the drive gear section ( 315 ) and the at least one drive roller section ( 316 ) may be an integral unit or separate components that have been assembled in an operative composite. In some embodiments, the gear section (FIG. 315 ) a spur gear with straight teeth, and the dimensions of the or the roller sections ( 316 ) correspond to the pitch circle diameter of the spur gear with straight teeth. As in 1C illustrated, the track gear ring ( 130 ) a track gear rim portion ( 131 ) configured to engage with the drive gear portion (10). 315 ), for example, the spur gear with spur gear, the feed drive gear ( 310 ). In some embodiments, the track gear rim (FIG. 130 ) a paragraph section ( 132 ). The paragraph section ( 132 ) may be on one or both sides of the track gear section (FIG. 131 ) are located. In some embodiments, the one or more paragraph sections are ( 132 ) and / or drive roller sections ( 316 ) is configured such that the roll section (s) ( 316 ) in contact with the paragraph (s) ( 132 ) when the feed drive gear ( 310 ) with the track gear rim ( 130 ) is engaged. In some embodiments, the one or more paragraph sections ( 132 ) the pitch diameter of the track gear portion ( 131 ) for guide rails that are curved or the partial line of the track gear portion ( 131 ) for guide rails that are straight. In some embodiments, the dimensions of the one or more paragraph sections ( 132 ) and the one or more drive roller sections ( 316 ) or the respective pitch circle diameters or partial lines, whereby the correct alignment of the drive gear section ( 315 ) on the track gear rim portion ( 131 ) is ensured when they are engaged. That is, for a curved track gear section (FIG. 131 ) corresponds to the diameter of the heel section ( 132 ), which is equal to the pitch diameter of the track gear portion ( 131 ) is the diameter of the drive roller section ( 316 ) equal to the pitch circle diameter of the drive gear portion ( 315 ). For a straight track gear rim section ( 131 ) the dimension of the heel section ( 132 ), which is equal to the partial line of the track gear segment ( 131 ) is the diameter of the drive roller section ( 316 ) equal to the pitch circle diameter of the drive gear portion ( 316 ). The correct alignment ensures that there is no gear play and the tractor unit ( 300 ) experiences jerk-free, stable operation at all operating speeds. In addition, prevents a drive roller ( 316 ) on one or more paragraphs ( 132 ) rolls, too, that the drive gear section ( 315 ) on the track gear rim ( 130 ) due to the biasing force of the engagement biasing mechanism (FIG. 313 ) or jammed due to excessive tightening. This prevents excessive wear and jamming of the drive mechanism. In some embodiments, the feed drive unit ( 310 ) is configured to include a drive roller section ( 316 ) on each side of the drive gear section (FIG. 315 ), and the track gear ring ( 130 ) is configured so that a single paragraph section ( 132 ) on one side of the gear section ( 131 ) is located. Such a configuration maintains the correct mesh with the drive gear ( 310 ) and allows the train unit ( 300 ) in any orientation with respect to the rail guide ( 100 ) to assemble.

In another aspect, the disclosed technology may include a tractor unit drive pivot feed gear engagement mechanism for engaging and disengaging a weld head tractor from a guide rail. Excessive wobble or backlash in a gear drive of a welding head tractor mounted on a guide rail can cause improper feed motion as the welding head position shifts and the loading direction on the drive gear changes, which can result in uneven feed speed. To avoid improper movement, some methods may include eliminating the backlash between the drive gear and the track gear rim.

The exemplary drive pivot feed gear engagement mechanism may enable the feed motor to be easily engaged with and disengaged from a quick release lever so that an operator can quickly position the weld head on the rail. In addition, the quick-release mechanism allows more flexibility in optimizing the feed speed of the drawbar, since the translation of the drawbar does not need to be set to a fast feed rate to position the weld head. That is, if a tractor does not have a quick-release mechanism, the engine ratio is adjusted to drive the tractor very quickly to minimize the time required to properly position the weld head on the rail for the start of, for example, a welding operation , However, if the ratio is set to a very fast feed, there may be problems if the traction unit drive is set to slower speeds. With the quick-release lever of the present invention, the tractor can be positioned at the correct position on the rail (or very close to the proper position) while the feed gear is disengaged. Thus, for example, the feed gear can be optimized for welding operations rather than for positioning the welding head on the rail. 3A shows an exemplary welding head tractor unit ( 300 ) with an exemplary drive pivot feed gear engagement mechanism mounted on a guide rail (for example, the guide rail (FIG. 100 ), which supports the track gear ring ( 130 ) is mounted, for example in an engaged position. The exemplary drive pivot feed gear engagement mechanism may include a lever (FIG. 320 ) on the welding head tractor unit ( 300 ), which via a eccentric cam a drive gear ( 310 ) raises and lowers. As in the front and side views of 3A can be seen, the drive gear ( 310 ) with a drive assembly as part of the track gear ring ( 130 ) are engaged, so that the intervention in a tilting movement of the drive gear ( 310 ) on a single pivot rod ( 311 ) can take place along a pivot pin ( 312 ) can pivot. The exemplary pivot feed gear engagement mechanism may also include a spring (FIG. 313 ) to apply pressure to the drive gear ( 310 ), for example, when connected to the guide rail (for example, the track gear ring ( 130 )), as in 3A shown. The drive gear ( 310 ) can be withdrawn from the guide rail by the lever ( 320 ), which can lead to a spring ( 314 ) yields its pressure and swings out of engagement, as in the front and side views of 3B to see. The drive gear ( 310 ) may contain multiple pitch spokes. There are no limitations on the pitch circle diameter of the spokes, and it may be any desired pitch circle diameter and may vary from one traction unit to another. For example, the geometry of a pitch circle spoke may be an involute, such that the diameter of a cross section at the apex of the pitch circle spoke is smaller than the diameter of a cross section at the base of the pitch circle spoke. However, there are no restrictions on the geometry of the pitch circle, and the pitch radius may also have other geometries, for example conical. In addition, the drive gear ( 310 ) includes a pitch diameter roller on both sides of the drive gear and on one side of the track gear rim, which may be configured to maintain a proper engagement with the drive gear and allow the traction device to be mounted on both sides of the rail.

The exemplary pivot feed gear engagement mechanism may be the the following features and advantages: a quick release and repositioning of a welding head on a guide rail by using an easily accessible lever, for example lever ( 320 ); A traction unit with the exemplary pivot feed gear engagement mechanism may move over debris on the track gear rim (for example, the track gear ring (FIG. 130 )), without jamming, and then fall back to their correct position; and a tractor unit having the example swing-feed gear engaging mechanism may be configured to maintain an exact gear pitch circle diameter distance between gears so that there is minimal gear play at different positions. For example, a substantially zero clearance can result in a very smooth and stable feed at slow and fast speeds. In addition, the exemplary pivoting flywheel engagement mechanism may allow for advancement along guide rails of a variety of different configurations, as in FIG 3C to see. For example, the train unit ( 300 ) incorporating the exemplary pivot feed gear engaging mechanism provides smooth feed along convex guide rails (FIGS. 391 ), concave guide rails ( 392 ), straight guide rails ( 393 ) and variable guide rails ( 394 ) enable.

In some example embodiments, the present invention may include a weld head angle adjustment mechanism for a weld head to adjust the angle between the weld head and a workpiece, ie, a weld puddle on the workpiece. As in 7 Illustratively, exemplary embodiments of the weld head angle adjustment mechanism may be incorporated into a weld head (FIG. 760 ) integrated with a welding base unit ( 750 ) is operatively connected. The welding base unit ( 750 ) can have a fixed relationship to the workpieces ( 705A and 705B ) to have. Accordingly, the angle between the welding head ( 760 ) and the surface of a welding puddle ( 740 ) of the workpieces ( 705A and 705B ) by adjusting the angle between the welding head ( 760 ) and the welding base unit ( 750 ). The welding head ( 760 ), an AVC module ( 710 ) and a welding torch ( 715 ) contain. The AVC assembly ( 710 ) is with the welding torch ( 715 ) and may include an AVC assembly control unit (not shown) configured to maintain a desired arc length (x) extending from the tip of the torch electrode (10). 717 ) to the surface of the welding puddle ( 740 ) of the workpieces ( 705A and 705B ), which in this exemplary embodiment are tubes of various diameters. Of course, the present invention is not limited to use on pipes, but can be used on any desired workpiece. The AVC module control unit maintains the arc length (x) by moving the burner ( 715 ) in the direction of the arrow ( 712 ). For the arc length (x) there are no restrictions; it can be any desired length suitable for the welding parameters. In some embodiments, the welding head (FIG. 760 ) include other components, such as a wire feeder and a wire guide (both not shown), but for the sake of brevity only those components relevant to the present invention will be discussed.

The welding head ( 760 ) contains a Schweißkopfwinkeljustiermechanismus ( 720 ), which determines the angle between the welding head ( 760 ) and the welding base unit ( 750 ) adjusted. In some embodiments, the angle adjustment mechanism ( 720 ) the welding head ( 760 ) with the welding base unit ( 750 ) at a single pivot point ( 765 ). The welding base unit ( 750 ) may be a drive unit, for example an orbital traction drive configured to lock the welding head (FIG. 760 ) with the burner ( 715 ) along the circumferential weld joint passing through the workpieces ( 705A and 705B ) is formed. Of course, in situations where the welding head ( 760 ) is to remain stationary while the workpiece is moving, the adjustment mechanism ( 720 ) the welding head ( 760 ) to a stationary welding base unit (not shown) instead of a mobile drive unit, for example a welding base unit ( 750 ). The welding base unit ( 750 ) (or another device) may be configured to perform a mechanical oscillation as indicated by the arrow (FIG. 752 ) to provide the desired welding weave pattern.

The angle adjustment mechanism ( 720 ) can be designed so that it forms an angle α between the welding head ( 760 ) and the welding base unit ( 750 ) adjusted. The freedom of movement of the welding head ( 760 ) can be in any desired range, for example up to 90 degrees, up to 140 degrees or up to 180 degrees. In some embodiments, the angle adjustment mechanism (FIG. 720 ) the angle α between the welding head ( 760 ) and the base unit ( 750 ) from -30 degrees to +150 degrees, and in other embodiments from -30 degrees to +110 degrees. As in 8th illustrates the angle adjustment mechanism ( 720 ) in exemplary embodiments of the present invention, a screw ( 722 ). The screw ( 722 ) is with the welding head ( 760 ) and the base unit ( 750 ) so actively connected that when the screw ( 722 ), the angular position of the welding head ( 760 ) with respect to the base unit ( 750 ), and when the screw ( 722 ) is solved, the angle α between the welding head ( 760 ) and the base unit ( 750 ) can be adjusted. In some embodiments, the screw ( 722 ) Threads ( 724 ), which in the welding head ( 760 ) and / or the base unit ( 750 ) are screwed into it. In some example embodiments, the angle adjustment mechanism (FIG. 720 ), the welding head ( 760 ) and / or the base unit ( 750 ) include a locking mechanism so that the angular position of the welding head ( 760 ) with respect to the base unit ( 750 ) remains unchanged (for example, when the screw ( 722 ) is tightened) and an exact angle is maintained even under heavy load or improper use. For example, the locking mechanism may include interlocking surfaces, such as serrated or serrated surfaces (FIGS. 721 ), which lock against each other when pressed together. In some embodiments, at least one serrated or toothed surface ( 721 ) in the adjustment mechanism ( 720 ) (for example, the screw ( 722 )) and / or the welding head ( 760 ) and / or the base unit ( 750 ) integrated. Like in 8th illustrated, the welding head ( 760 ) and the base unit ( 750 ) each have an integrated serrated or toothed surface ( 721 ). In some embodiments, the serrated or serrated surfaces (FIG. 721 ) lock directly against each other. In other embodiments, a washer or plate ( 725 ) between the serrated or toothed surfaces ( 721 ) arranged. In some embodiments, the washer or plate (FIG. 725 ) are made of a material (for example, brass, copper, plastic, nylon, etc.) that is softer than the serrated or serrated surfaces ( 721 ), so that the serrations in the washer or plate ( 725 ) to the welding head ( 760 ) fixed to the base unit ( 750 ) to lock. Because the washer or plate ( 725 ) is made of a softer material, any signs of wear in the locking mechanism are first detected by the washer or plate ( 725 ), and not in the serrated or toothed surfaces ( 721 ). Because the washer or plate ( 725 ) can be made from inexpensive materials that are easily replaced after showing signs of wear, the latching mechanism remains sufficiently durable and stable even after repeated use. The selection of the screw ( 722 ) with regard to size and material depends on the size and weight of the welding head ( 760 ) and the welding environments in which the present invention operates. However, it is considered that in most cases a large heavy-duty bolt made of high strength carbon steel, stainless steel or other high strength materials is used.

17A to 17D illustrate exemplary configurations of serrated or toothed surfaces ( 721 ) according to the present invention. 17A illustrates a configuration wherein the tooth configuration is V-shaped. Each V-groove is continuously cut straight, as shown in section AA, by keeping the depth of the cutting tool constant. Because the depth of the cut is constant, the preparation of the serrated or serrated configuration is 17A pretty easy.

Another exemplary embodiment of a serrated or serrated surface configuration is shown in FIG 17B illustrated. As in the previous embodiment, the tooth configuration is V-shaped. However, in this embodiment, the V-groove is cut at an angle (θ) as shown in section AA. The angle θ depends on the number of teeth and the V-groove cutting tool angle. For example, if the toothed surface ( 721 ) Has 40 teeth and the groove angle is 60 degrees, so an angle θ of about 3.89 degrees leads to an ideal toothing. Of course, if the number of teeth changes or the groove angle changes, then the angle θ will be different. As a result, opposing teeth touch along the entire length as shown in section BB, resulting in higher strength. This almost perfect gearing is achieved by changing the depth of the cutting tool as it cuts the groove.

In a further embodiment, as in 17C illustrates a V-groove is cut at an angle (θ), which has the result that the Top of the teeth are on the same level. This is achieved by cutting the V-groove at an angle, as shown in section AA. As before, the angle θ for this embodiment also depends on the number of teeth and the V-groove cutting tool angle. For example - again assuming 40 teeth and a groove angle of 60 degrees - an angle θ of about 7.76 degrees results in ideal toothing with the top of the teeth on the same plane. Such a construction is ideal when a washer or plate ( 725 ) is arranged between opposing teeth, as shown in section BB, because the teeth evenly into the washer or plate ( 725 ), resulting in a better grip and even clamping.

In a further embodiment, as in 17D illustrates, a V-groove is cut in a curved path. In some embodiments, the shape of the curve is an involute that keeps the width of the teeth constant. During cutting, the depth is kept constant, as shown in section AA, ie the bottom of the groove is flat. By keeping the width and depth of the teeth constant, this configuration results in the top of the teeth lying on the same plane and allows opposing teeth to have nearly perfect gearing. Thus, the teeth touch along the entire length. The constant tooth depth simplifies manufacture, and the almost perfect toothing leads to a higher locking strength. If desired, a washer or plate ( 725 ) between the toothed surfaces ( 721 ), the fact that the teeth lie on the same plane has the consequence that the teeth fit evenly in the washer or plate ( 725 ), resulting in a better grip and even clamping. Of course, the configuration of the serrated or toothed surface ( 721 ) is not limited to the above embodiments, and other configurations may be used.

Because a single screw (or similar device) in the angle adjustment mechanism ( 720 ) of the above embodiments, the present invention enables a fast and precise bending of the welding torch (FIG. 715 ), which may be particularly important for specialized welding applications with a variety of difficult angles. However, the present invention is not limited to a single screw design, and any number of bolts (or other type of construction) may be used as long as the angle α between the welding head (FIG. 760 ) and the base unit ( 750 ) can be adjusted. In some embodiments, the angle adjustment mechanism (FIG. 720 ), the welding head ( 760 ) and / or the base unit ( 750 ) Scribing lines ( 723 ) to allow easy identification of the exact angle α for repeatable devices. Like in 8th illustrated, the scribe lines ( 723 ) on the welding head ( 760 ) and the base unit ( 750 ). Of course, the scribe lines ( 723 ) not on the in 8th illustrated points and can be anywhere on the welding head ( 760 ) and / or the base unit ( 750 ) as long as the scribe lines ( 723 ) identify the angle α.

In some embodiments, the angle adjustment mechanism (FIG. 720 ) allow the stroke direction of the AVC assembly ( 710 ) on the orientation of the burner ( 715 ). That is, the AVC assembly ( 710 ) and the burner ( 715 ) are aligned so that the stroke direction of the AVC assembly ( 710 ), as by the arrow 712 in 7 illustrated, perpendicular to a surface of the welding puddle ( 740 ) runs. Of course - depending on the application - the AVC board ( 710 ) and / or the burner ( 715 ) in any desired orientation to the welding puddle ( 740 ) and / or the workpieces ( 705A and 705B ). In exemplary embodiments of the present invention, the orientation of the burner ( 715 ) with respect to the orientation of the AVC assembly ( 710 ) unchanged, while the angle α between the welding head ( 760 ) and the base unit ( 750 ) is adjusted. As discussed above, the exemplary angle adjustment mechanism ( 720 ) a wide range of pivoting or rotation (for example -30 ° to 110 °) of the welding head ( 760 ). In some embodiments, the welding head (FIG. 760 ) with several burner projection settings (for example, two or more settings), so that the burner ( 716 ) can protrude very far and / or perform a large stroke (for example, an AVC hub of 3 1/2 ''). In addition, the implementation of the angle adjustment mechanism ( 720 ), as discussed above, also reduce and / or eliminate harmful wear on the angle adjustment mechanism.

In exemplary embodiments, the angle adjustment mechanism (FIG. 720 ) can be used to adjust the orientation of the welding torch ( 715 ) with respect to the sweat puddle ( 740 ) in a fillet weld application, such as in 7 illustrated. In this case, the angle α and the orientation of the AVC assembly ( 710 ) with respect to the burner ( 715 ) is adjusted so that the stroke direction of the AVC module ( 710 ) and the corresponding movement of the burner ( 715 ) perpendicular to the surface of the welding puddle ( 740 ), as indicated by the arrow 712 illustrated. While the base unit ( 750 ) (or another device) mechanically welds the welding head ( 760 ) oscillates as indicated by the arrow 752 In order to produce the desired welding weave pattern, the arc length (x) changes if this remains uncorrected. As in the conventional system discussed above, the AVC assembly ( 710 ) the position of the welding torch ( 715 ) to maintain the desired arc length (x). However, in contrast to the conventional system, the stroke direction of the AVC module ( 710 ) so that the AVC assembly ( 710 ) the welding torch ( 715 ) in a direction perpendicular to the surface of the welding puddle ( 740 ), which allows better control of the arc length (x) over the entire surface of the weld puddle (FIG. 740 ) allowed away. Because the stroke direction of the AVC assembly ( 710 ) perpendicular to the welding puddle ( 740 ), moreover, the sensitivity and speed of the AVC stroke need not be adjusted based on the angle α (as would be the case if the AVC stroke direction remained vertical). Accordingly, the resulting weld has better quality.

In another aspect, the disclosed technology may include an adjustable fillet angle that provides freedom of movement of an arc voltage control (AVC) device. Assembly, for example, can allow up to 180 degrees. For example, a single adjustment may allow for a quick and accurate bending of a welding torch, which may be particularly important for specific welding applications having a variety of different difficult angles.

Aligning an AVC separately from the burner angle may result in poor quality fillet welds. Inferior welds may also be the result of a variety of reasons related to the throat angle of an AVC assembly, such as insufficient stability of adjustment (eg unsafe and weak), overuse and lack of longevity, limited AVC stroke (e.g. 1 inch AVC stroke limited) and limited rotation of the AVC assembly (limited to approximately 40 degrees, for example).

4 shows an exemplary adjustable fillet angle mechanism of an AVC assembly ( 410 ) of a welding head tractor unit ( 400 ). The exemplary adjustable fillet angle mechanism may include a built-in serrated latch mechanism (US Pat. 420 ), so that an accurate angle is maintained even under heavy load or improper use. The exemplary locking mechanism allows for fillet angle adjustment by a single adjustment, for example, by tightening or loosening a screw, ( 422 ) (for example, a large high-performance screw), so that toothed surfaces ( 421 ) in a manner that reduces the alignment of scribing increments ( 423 ). Scribing increments ( 423 ) of the exemplary adjustable fillet angle mechanism may allow easy identification of an exact angle for repeatable devices. The implementation of the exemplary adjustable fillet angle mechanism may enable AVC alignment in such a manner as to be aligned with the torch angle. The exemplary adjustable fillet angle mechanism may also allow pivoting or turning about a desired angle α (for example, 140 °) of the entire burner assembly with multiple adjustments (eg, three settings) for increasing burner protrusion so that the burner can protrude very far and can run a large stroke (for example, an AVC hub of 3 1/2 ''). The implementation of the adjustable fillet angle mechanism may also reduce and / or eliminate harmful wear on the angular adjustment of the AVC assembly.

In some example embodiments, the present invention may include a lead / lag burner angle adjustment system for a weld head for adjusting the lead / lag angle of an electrode. As in 9 1, exemplary embodiments of the lead / lag burner angle adjustment system may be incorporated into a welding head (FIG. 905 ) of the welding system ( 900 ), which can be used in brazing, cladding, building, filling, hardfacing, bonding and welding applications. For the sake of brevity, only those components needed to explain the exemplary embodiments of a lead / lag burner angle adjustment system of a welding head are illustrated and discussed. The welding system ( 900 ) contains a welding head ( 905 ) and a welding base unit ( 940 ). The welding head ( 905 ) contains a burner assembly ( 920 ), a burner head drum assembly ( 910 ) and a burner head support device ( 930 ), which may be an arc voltage control (AVC) assembly when an AVC is desired. In the following description, the burner head support device ( 930 ) as an AVC assembly ( 930 ). However, the supporting device ( 930 ) may also be another component, for example a mounting plate. The burner assembly ( 920 ) contains a burner head ( 921 ) and an electrode ( 925 ) and is connected to the burner head drum assembly ( 910 ). The burner head drum assembly ( 910 ) contains a burner mounting bracket ( 912 ), a lead / lag burner angle adjustment mechanism ( 914 ) and at least one drum clamp ( 916 ). The burner head drum assembly ( 910 ) Actuates the burner assembly ( 920 ) with the AVC module ( 930 ), which in turn communicate with the welding base unit ( 940 ) is operatively connected. It will be apparent to those skilled in the art that other components, such as wire feeders and wire guides, may also be used with the burner assembly (depending on the application). 920 ) and / or the burner head drum assembly ( 910 ) (see for example 5B ). The burner assembly ( 920 ) may be of a type used in inert gas tungsten arc welding (GTAW) or plasma arc welding (PAW). In this case, the electrode ( 925 ) be a tungsten electrode. However, the present invention is not limited to GTAW and PAW systems and may also be integrated with other systems, such as inert gas metal arc welding (GMAW) systems, laser welding systems, etc.

The AVC assembly ( 930 ), an AVC base unit ( 936 ), an AVC sliding plate ( 932 ) and an AVC assembly control unit (not shown) configured to maintain a desired arc length (x) extending from the tip of the electrode (10). 925 ) to the workpiece ( 906 ). The AVC module control unit maintains the desired arc length (x) by moving the AVC side plate ( 932 ) (and the Burner Head Drum Assembly ( 910 )) in the direction of the arrow ( 938 ). The welding base unit ( 940 ) may be a mobile unit, for example a train unit on a rail / track system, or a stationary unit. If, for example, the workpiece ( 906 ) is a pipe to be welded, the welding base unit ( 940 ) is an orbital traction drive configured to mount the welding head ( 905 ), the burner assembly ( 920 ), along a guide rail, for example, the guide rail ( 100 ) of the 1A - 1C that is, for example, arranged around a circumferential weld joint of the pipe (either inside or outside the pipe). Of course, in situations where the welding head ( 940 ) should remain stationary while the workpiece ( 906 ), the welding base unit ( 940 ) be a stationary unit instead of a drive unit. The welding base unit ( 940 ) (or another device) may be configured to perform a mechanical oscillation as indicated by the arrow (FIG. 942 ) to perform a desired welding weave pattern.

The lead / lag burner angle adjustment mechanism ( 914 ) can with the support device ( 930 ) at the welding head device ( 905 ), for example an AVC assembly, if an AVC is desired. In some embodiments, as in the 10 and 11A illustrated is an end, section ( 916 ), the lead / lag burner angle adjustment mechanism ( 914A / B) to the burner mounting bracket ( 912 ) or is an integral part of it. The other end, section ( 915A / B), the lead / lag burner angle drum mechanism ( 914A / B) is on the AVC mounting plate ( 934A / B). The adjustment mechanisms ( 914A ) and ( 914B ) and the AVC mounting plate ( 934A ) and ( 934B ), various embodiments of the adjustment mechanism ( 914 ) / Mounting plate ( 934 ) Interface. In the adjustment mechanism ( 914A ) and the mounting plate ( 934A ) have the end section ( 915A ) and the mounting plate ( 934A ) no serrations, and in the adjustment mechanism ( 914B ) and the mounting plate ( 934B ) have the end section ( 915B ) and the mounting plate ( 934B ) Toothings ( 951 ) (discussed below). In some embodiments, the end section (FIG. 915 / A / B) and / or at least one drum clamp ( 917 ) (or a similar device) configured so that a transverse movement of the at least one drum clamp ( 917 ) via the end section ( 915 / A / B) a force on the section ( 915 / A / B), so that the adjustment mechanism ( 914 / A / B) against the AVC mounting plate ( 934 / A / B) is pressed and in the desired lead / caster angle for the electrode ( 925 ) locked with respect to the workpiece. For example, how best in 10 to see the shape of the section ( 915A ) of the adjustment assembly ( 914A ) conical, and the drum clamps ( 917 ) (or similar devices) may be configured to control the conical section ( 915A ) of the adjustment mechanism ( 914A ). So if the drum clamps ( 917 ) (or similar devices) on the AVC assembly ( 930 ), the clamps ( 917 ) the lead / lag burner angle adjustment mechanism ( 914A ) against the AVC mounting plate ( 934A ) and lock the desired forward / caster angle. The drum clamps ( 917 ) (or similar devices) can be connected to the AVC mounting plate ( 934 / A / B) attached to the AVC sliding plate ( 932 ) or forms an integral part of it, for example by means of clamping screws or bolts ( 918 ) (or other devices). By loosening the clamping screws or bolts ( 918 ) (or other devices), the lead / lag burner angle adjustment mechanism ( 914 / A / B) to set the desired lead / lag angle for the electrode ( 925 ). In some embodiments, the lead angle or caster angle, or both, may range from 0 to at least 15 degrees, 0 to at least 90 degrees, or 0 to 180 degrees (ie, a full 360 degree adjustment of the adjustment mechanism (FIG. 914 /FROM)). Of course, the present invention is not limited to a conical shape for the end section ( 915 / A / B) of the adjustment mechanism ( 914 / A / B), and other shapes may be used. In addition, if the welding system does not have an AVC assembly ( 930 ), the end section ( 915 / A / B) of the adjustment mechanism ( 914 / A / B) may be attached to another type of supporting device, for example a mounting plate (or similar device), which is then attached to the welding base unit (FIG. 940 ) is attached.

To assist in adjusting the lead / lag angle, in some embodiments, the adjustment mechanism (FIG. 914 / A / B) and / or the AVC mounting plate ( 934 / A / B) (or other device) alignment lines ( 952 ) respectively. ( 953 ) (see for example 10 . 11A and 11B ). The alignment lines ( 952 ) and ( 953 ) can be used, for example, on the adjustment mechanism ( 914 / A / B) and / or the AVC mounting plate ( 934 / A / B). The alignment lines ( 952 ) and or ( 953 ) can be used as a pointer (see for example the lines ( 952 )), or may denote desired increments (see lines ( 953 ). The desired increments may, for example, be every 0.5 degrees or another increment. Of course, other methods can be used to adjust the alignment lines ( 953 ). For example, an insert may be mounted and marked clearly with numbers indicating the lead / lag angle, for example, 1 °, 1.5 °, 3 °, 5 °, etc. In some embodiments, the adjustment mechanism (FIG. 914 / A / B) the burner assembly ( 920 ) with the electrode ( 925 ) by a full 360 ° to allow for a high degree of flexibility in achieving the desired welding configuration device, ie, it extends the range of welder configurations as compared to conventional systems. In addition, in some embodiments, the adjustment mechanism (FIG. 914 / A / B) and / or the AVC mounting plate ( 934 / A / B) may be configured so that there is a locked position in each direction, whereby a double-pass welding with a leading / trailing angle becomes very easy. As indicated above, the exemplary lead / lag burner angle adjustment mechanism (FIGS. 914 / A / B) can be accessed in a simple manner in order to determine the leading / trailing angle of the burner assembly ( 920 ) without scratching welding head components. In addition, the drum clamps ( 917 ) provides a powerful locking mechanism that fixes the lead / lag angle when the clamping screws or bolts ( 918 ) are attracted.

In some example embodiments, further locking mechanisms may be incorporated such that the angular position of the burner head drum assembly (FIG. 910 ) with respect to the AVC assembly ( 930 ) / Support device remains unchanged and the desired forward / caster angle is maintained even under heavy load or improper use. For example, the additional locking mechanisms may include serrated or toothed surfaces that lock against each other when compressed. In some embodiments, at least one serrated or serrated surface is included in the advance / lag burner angle adjustment mechanism (FIG. 914 ) or the AVC mounting plate ( 634 ) / Support device or integrated in both. Like in the 11A and 11C illustrated, the end section ( 915B ) of the adjustment mechanism ( 914B ) and the AVC mounting plate ( 934B ) each have an integrated serrated or toothed surface ( 951 ). In some embodiments, the serrated or serrated surfaces (FIG. 951 ) lock directly against each other. In other embodiments, a washer or plate ( 950 ) between the serrated or toothed surfaces ( 951 ) arranged. In some embodiments, the washer or plate (FIG. 950 ) are made of a material (for example brass, copper, plastic, nylon, etc.) which is softer than that of the serrated or toothed surfaces ( 951 ), so that the serrations in the washer or plate ( 950 ) to adjust the adjustment mechanism ( 914B ) firmly with the AVC mounting plate ( 934B ) to integrate. Because the washer or plate ( 950 ) is made of a material softer than that of the serrated or toothed surfaces ( 951 ), any signs of wear in the locking mechanism are first detected by the washer or plate (FIG. 950 ) visible, noticeable. Accordingly, because the washer or plate ( 950 ) can be made of inexpensive materials that are easily replaced after showing signs of wear, the locking mechanism remains durable and stable even after repeated use. Thus, exemplary embodiments of the present invention may provide other benefits, such as a more versatile and powerful lock, and fixed lead / lag adjustments, for example, with indicated (marked) angles.

Because the lead / lag burner angle adjustment mechanism ( 914 / A / B) can be rotated by a single adjustment, for example by simply loosening the clamping screws or bolts ( 918 ) (or a similar device), the present invention allows a fast and accurate bending of the burner lead / lag angle and / or a reorientation of the burner assembly ( 920 ) with the electrode ( 925 ), which may be particularly important for specialized welding applications with a variety of difficult angles. Furthermore, in some embodiments, the clamping screws or bolts ( 918 ) (or a similar device) can be completely released (removed) so that the caster / fore burner angle adjustment mechanism ( 914 / A / B) (and the burner head drum assembly ( 910 )) can be easily attached or removed.

In another aspect, the disclosed technology may include a pan / tail burner angle mechanism of a torch head drum assembly on a welding head apparatus. 5A shows several views of an exemplary welding head system ( 600 ), which provides an exemplary swivel-advance / follow-up burner angle mechanism ( 510 ) contains. The swivel fore / aft burner angle mechanism ( 510 ) can make a 360 degree pan of the entire burner ( 520 by providing a rotational angle locking mechanism at the interface between a torch head drum assembly ( 521 ) and the remaining section of the welding head system ( 500 ) is used. However, the torch head drum assembly may require an insert ( 525 ), which determines the rotation of the forward / caster angle mechanism ( 510 ) limited. For example, use ( 525 ) in 5A marked with "5 °", that the burner ( 520 ) rotates more than 5 °. 5B shows several views of an exemplary welding head system ( 500 ) containing a cross-sectional plan view illustrating the swivel-advance / follow-up burner angle mechanism ( 510 ) shows. The swivel caster / flow burner angle mechanism ( 510 ) can have toothed surfaces at the interface of the torch head drum assembly ( 521 ) and the remaining section of the welding head system ( 500 ) contain. The serrated surfaces on either side of the interface can be connected in a manner that matches the orientation of the scribe lines (FIG. 511 ). The swivel caster / flow burner angle mechanism ( 510 ) can be rotated by a single adjustment, for example by tightening or loosening clamping screws ( 512 ). The orientation of the scribe lines ( 511 ) may allow a desired orientation. For example, the mechanism may be marked so that it can be easily adjusted to a certain angle. An insert can be mounted and marked clearly with a number indicating the leading / trailing angle, for example 1 °, 1.5 °, 3 °, 5 °, etc., so that there is a hard end stop in each direction, which Double wiping with a lead angle makes it very easy. The swivel caster / flow burner angle mechanism ( 510 ) may also allow clamping screws ( 512 ) completely from the welding head system ( 500 ) are unscrewed, so that the burner head drum assembly ( 521 ) can be attached or removed.

A conventional advance / caster adjustment assembly (barrel assembly) may be associated with limited angular adjustment, component scratching, slipping welder (for example, due to a weak mechanism of the torch angle component mechanism), difficult access for angular adjustments, and uneven leading / caster angle adjustments, just a few To name restrictions. The exemplary pan-run / lag burner drum assembly may provide substantially 360 degree pivoting without scratching, a powerful locking mechanism that fixes the lead / lag angle, and easy access for adjusting the angular adjustments. The swivel fore / aft burner angle mechanism ( 510 ) can expand the range of welder configurations. This can realize further advantages, such as a more versatile, more powerful locking and a fixed forward / tail, for example, with a specified (marked) angle.

Alternative rail track clamp embodiment

An alternative embodiment of the welding head tractor unit ( 600 ) for mounting on a guide rail ( 100 ) is in the 18A - 20 illustrates and includes a puller mounting mechanism that includes a rail track clamping assembly. The welding head tractor unit ( 600 ) is in the non-clamped position in 18A and in the clamped position in 18B shown.

18A illustrates a welding head tractor unit ( 600 ) with a puller mounting mechanism comprising a rail track clamp assembly ( 640 ), which in the non-clamped position in 18A is shown. As can be seen in the front view of the figure, the train unit ( 600 ) in the non-clamped position a fixed block ( 622 ) and a movable plate ( 624 ) operatively connected to a wheel / roller set A. The welding head tractor unit ( 600 ) can move on a guide rail (for example, a guide rail ( 100 )) by means of a roller device or roller devices, such as wheels and / or rollers, be mounted. The track clamp assembly ( 640 ) contains a clamping mechanism ( 640 ) connected to the movable plate ( 624 ) is operatively connected. To the train unit ( 600 ) to assemble or disassemble, the clamping mechanism ( 640 ) between an open and a closed position, whereby the track clamping assembly ( 640 ) to retract the wheel / roller set A (see 18A ). As part of the exemplary mounting mechanism, in some embodiments, the traction unit ( 600 ) are clamped or released by means of a single clamping action, ie by adjusting the clamping mechanism ( 640 ) to move the wheel / roller set A.

The in the 20A -B illustrated clamping mechanism ( 640 ) contains a block ( 622 ) connected to the welding head tractor unit ( 600 ), and a movable plate ( 624 ) relative to the block ( 622 ) is movable. The movable plate ( 624 ) is by a threaded shaft ( 626 ) and one or more cam springs ( 628 ), which the movable plate ( 624 ) from the block ( 622 ), with the block ( 622 ) connected. The term "spring" as used herein includes any assembly capable of applying a biasing force, such as linear springs, coil springs, pneumatic or hydraulic cylinders, inflatable bladders, resilient structures or materials, and the like. Therefore, the specific embodiments shown in the drawings and described herein are not to be considered as limiting. Likewise, the mention of a "spring" force or "spring" constant also includes the biasing force, which may be constant or variable, and the biasing constant, if constant, exerted by a particular biasing assembly, component, or structure.

The wave ( 626 ) contains a first end that is placed in the fixed block ( 622 ) and a second end extending through the movable plate (FIG. 624 ) and through the one axis ( 630 ) runs. A cam handle ( 632 ) is on the axis ( 630 ) and is located between a first, open position ( 20A ) and a second, closed position ( 20B ) movable. As in the 20A -B, the cam handle ( 632 ) 180 ° about the axis ( 630 ) between the open and closed positions, but other angles of rotation may also be considered.

When the cam handle ( 632 ) in an open position ( 20A ), the cam section allows the movable plate to move farther from the fixed block (FIG. 624 ) to sit away, since the cam springs ( 628 ) the movable plate ( 624 ) from the fixed block ( 622 ) push on. In this position, the distance between the wheel / roller sets (A, B) is maximized, and the Schweißkopfzugeinheit ( 600 ) can with the rail ( 100 ).

When the cam handle ( 632 ) is moved to a closed position ( 20B ), the cam section urges the movable plate ( 624 ) in the direction of the fixed block ( 622 ). This causes the distance between the wheel / roller sets (A, B) is lower, the cam springs ( 628 ), whereby the welding head tractor unit ( 600 ) with the rail ( 100 ), as described above.

An additional over-clamp spring ( 634 ) can be placed between the cam handle ( 632 ) and the movable plate ( 624 ), which prevents the cam from landing on the ground, and allows the cam handle ( 632 ) to close completely when the movable plate ( 624 ) flush with the fixed block ( 622 ) or when the rollers have already touched the rail before the cam has reached the closed position. The overclamp spring ( 634 ) has a very high spring force in comparison to the spring force of the cam springs ( 628 ), so that the cam springs ( 628 ) in front of the over-clamp spring ( 634 ) are compressed. The overclamp spring ( 634 ) is provided with sufficient rigidity, so that the welding head remains firmly on the rail when the cam handle ( 632 ) is in the closed position. The overclamp spring ( 634 ) can also be useful by allowing the train unit ( 600 ) in contact with a rail ( 100 ), which has some variation in the rail width. In this case, the train unit ( 600 ) set to the narrowest rail width, and the cam handle ( 632 ) will be closed. If the rail ( 100 ) becomes wider, so the Überklemmfeder ( 634 ), which compensates for the difference in rail width.

Linear bearing assemblies (consisting of a shaft and a linear bearing) ( 636 ), can also be used between the fixed block ( 622 ) and the movable plate ( 624 ) can be arranged to guide the linear movement and friction and wear during movement of the movable plate ( 624 ) relative to the fixed block ( 622 ) to reduce.

The adjustment of the distance between the fixed block ( 622 ) and the movable plate ( 624 ) can be adjusted by adjusting the position of the threaded shaft ( 626 ) and the axis ( 630 ) relative to the fixed block ( 622 ) be accomplished.

In a first adjustable embodiment, the threaded shaft (FIG. 626 ) in the movable block ( 622 ) and can have an adjustable screw depth. To set the distance between the fixed block ( 622 ) and the movable plate ( 624 ) when the cam handle ( 632 ) is in a closed position, the shaft ( 626 ) in the fixed block ( 622 ) or unscrewed from it. By turning the shaft, the distance between the axis ( 630 ) and the fixed block ( 622 ) become larger or smaller, whereby the distance between the wheels / rollers (A, B) is fixed in the closed position.

It may be desirable that the axis ( 630 ) in a preferred orientation (for example perpendicular to the rail (FIG. 100 )) is arranged. According to the first adjustable embodiment, in which the axis ( 630 ) in a fixed orientation relative to the shaft ( 626 ), it would be possible to use the wave ( 626 ) only in half-turn increments into the fixed block ( 622 ) in or out of it, about the axis ( 630 ) in the preferred orientation. For a wave ( 626 ) with a thread pitch of 32 TPI (0.03125 inches / rev) (0.8 mm / rev), the distance between the axis ( 628 ) and the fixed block ( 622 ) can only be adjusted in increments of 0.015625 '' (0.4 mm). This degree of adjustability may not be acceptable for precision control, and therefore other fine adjustment techniques may be provided.

In a second adjustable embodiment, the shaft ( 626 ) have a first threaded end and a second threaded end, wherein the axis ( 630 ) is screwed onto the second threaded end. The first threaded end and the second threaded end are provided with opposing (for example right and left-handed) threads, so that when the shaft ( 626 ) in the fixed block ( 622 ) is screwed, the axis ( 630 ) can be screwed in the opposite direction so that the preferred orientation is maintained. This arrangement allows a finer adjustment of the axis ( 630 ), because the wave ( 626 ) is not limited to fixed increments.

In a third adjustable embodiment, the shaft ( 626 ) have a first thread end and a second thread end, wherein the axis ( 630 ) is screwed onto the second threaded end. The first threaded end and the second threaded end are provided with different thread pitches. In the case of the configuration with different thread pitches, the displacement of the axis ( 626 ) equivalent to the difference of the slopes. In one case, the first slope 32 may be TPI (0.03125 inches / revolution) and the second slope may be 24 TPI (0.04167 inches / revolution) such that the displacement is 0.01042 inches per revolution (equivalent to 96 TPI). By reducing the slopes at each end, the adjustment becomes finer.

All of the adjustable embodiments described above may also be provided with a locking feature to lock the shaft and axle in place once the adjustment is adjusted. Adjusting screws may be used for this purpose, although it will be understood that other locking features may be used.

While this patent document contains numerous specific details, this should not be construed as limiting the scope of an invention or the claimed subject matter, but rather as describing features that may be specific to particular embodiments of particular inventions. Certain features described in this patent document in the context of separate embodiments may also be implemented in combination in a single embodiment. Conversely, various features described in the context of a single embodiment may also be implemented separately or in any suitable sub-combinations in several embodiments. Moreover, while features may have been described above as acting in certain combinations, and even claimed as such initially, one or more features of a claimed combination may also be released from the combination, and the claimed combination may be of one kind Obtain partial combination or variation of a partial combination.

Although work operations in the drawings may be shown in a particular order, this should not be construed as requiring that such operations be performed in the particular order shown or in sequential order, or that all illustrated operations must be performed to get to desirable results. Moreover, the separation of various system components in the embodiments described above should not be construed as requiring such separation in all embodiments.

Only a few implementations and examples have been described, and still further implementations, developments, and variations may be made based upon what is described and illustrated in this patent document.

In summary, while the invention has been described in terms of certain embodiments, it will be understood by those skilled in the art that various changes may be made and equivalents may be employed without departing from the scope of the invention. In addition, many modifications may be made to adapt a particular situation or material to the teachings of the invention without departing from its scope. Therefore, it is intended that the invention not be limited to the particular embodiments disclosed, but that the invention include all embodiments falling within the scope of the appended claims.

LIST OF REFERENCE NUMBERS

5

Electric arc

10

welding torch

12

line

20

module

22

arrow

30

welding base

32

Arrow or direction

40

weld puddle

50

system

100

guide rail

110

rail tracks

111

Running track segment

112

Running track segment

115

connection joint

116

connection joint

117

Connection interface

120

Rail cross member

130

Running rail sprocket

131

Rail gear portion

132

heel portion

150

mounting component

160

point role

161

contact point

165

axis of rotation

170

pivot block

200

tractor

210

Roller or roller devices

210A

Rad / Role

210B

Rad / Role

211

pivot block

213

locking bush

215

contact point

220

clamping mechanism

221

rotary knobs

222

screw

224

movable plate

230

linear bearings

240

clamping assembly

300

tractor

310

drive gear

311

connecting element

312

pivot pin

313

biasing mechanism

314

biasing mechanism

315

gear portion

316

roller section

320

clutch lever

320A

cam section

321

coupling arm

391

convex guide rail

392

concave guide rail

393

straight guide rail

394

variable guide rail

400

Schweißkopfzugeinheit

410

AVC assembly

420

locking mechanism

421

toothed surface

422

screw

423

Anreißinkrement

500

Welding head system

510

Torch angle mechanism

511

line alignment

512

clamping screw

520

entire burner

521

drum assembly

525

commitment

600

Schweißkopfzugeinheit

622

Fixed block

624

movable plate

626

wave

626A

first threaded section

626B

second threaded section

628

cam springs

630

axis

632

cam handle

634

About clamping spring

640

A track clamp assembly

705A

workpiece

705B

workpiece

710

AVC assembly

712

arrow

715

welding torch

717

torch electrode

720

adjustment mechanism

721

toothed surface

722

screw

723

scribe

724

thread

725

Washer or plate

740

weld puddle

750

base unit

752

arrow

760

welding head

765

pivot point

900

welding system

905

welding head

906

workpiece

910

drum assembly

912

Burner mounting bracket

914

adjustment mechanism

914A

adjustment mechanism

914B

adjustment mechanism

915A

cut

915B

cut

916

drum clamp

917

drum clamp

918

screw

920

burner assembly

921

burner head

925

electrode

930

support device

932

side plate

934

mounting plate

934A

AVC-mounting plate

934B

AVC-mounting plate

936

AVC base unit

938

arrow

940

base unit

942

arrow

950

Washer or plate

951

toothed surface

952

snapline

953

snapline

AVC

Arc voltage control

A

Rad / Role Set

B

Rad / Role Set

C

clamping assembly

D1

distance

D2

distance

D3

distance

F

Fixed block

GMAW

Shielded gas-metal arc welding

GTAW

shielded gas tungsten arc welding

M

movable plate

PAW

Plasma arc welding

S

wave

W1

width

W2

width

x

Arc length

Claims (15)

Mounting mechanism for connecting a Schweißkopfzugeinheit ( 200 ) with a guide rail ( 100 ), comprising: a fixed block (F) having a first set (B) roller devices; like roles ( 210 ; 210A . 210B ); a movable plate (M) with a second set of (A) roller devices, wherein the movable plate is movable to adjust the distance between the first and second roller devices; a clamping assembly (C; 240 ; 640 ) comprising: a shaft (S) extending from the fixed block (F) and through the movable plate (M); a handle connected to the shaft and movable between an open position for releasing the tractor unit from engagement with the guide rail and a closed position for engaging the tractor unit with the guide rail, the guide rail comprising a first rail track and a second rail track (Fig. 110 ); and wherein, when the handle is in an open position, a first distance between the first and second roller devices is greater than a width of the guide rail; wherein, when the handle is in a closed position, a first distance between the first and second roller devices is approximately equal to the width of the guide rail. Mounting mechanism according to claim 1, wherein the clamping assembly (S; 640 ) further comprises at least one cam spring ( 628 ) between the fixed block and the movable plate, and wherein the handle is a cam handle ( 632 ). Mounting mechanism according to claim 2, wherein the shaft (S; 626 ) adjustable in the fixed block (F; 622 ) is screwed. Mounting mechanism according to claim 2 or 3, wherein the clamping assembly (C; 640 ) an axis ( 630 ) between the cam handle and the shaft, and wherein the axle is preferably adjustably screwed to the shaft. Mounting mechanism according to claim 4, wherein the shaft has a first threaded portion ( 626A ) for engaging the fixed block and a second threaded portion ( 626B Preferably, one of the first and second threaded portions is clockwise and the other of the first and second threaded portions is left-handed, and more preferably, the first threaded portion has a first pitch and the second threaded portion has a second pitch. Mounting mechanism according to one of claims 1 to 5, further comprising an over-clamping spring ( 634 ) between the cam handle and the movable plate, and wherein preferably the stiffness of the overclamp spring is greater than the stiffness of the cam spring. A towing device mounting mechanism according to any one of claims 1 to 6, wherein the first roller device and the second roller device are adapted to roll on the rail. A towing device mounting mechanism according to any one of claims 1 to 7, wherein each of the first and second sets of roller devices comprises one or more pivoting blocks (Figs. 211 ) and one or more rollers on each of the pivot blocks. The towing device mounting mechanism of claim 8, wherein each of the pivot blocks is configured to pivot so that the rollers of the respective pivot blocks can conform to a profile of the track rail when the tractor unit engages the track rail. A towing device mounting mechanism according to claim 8 or 9, wherein the clamping assembly is configured to bring the rollers of each of the first pivot block and the second pivot block into operative connection with the guide rail when the clamping assembly is in a closed position. A towing device mounting mechanism according to any one of claims 8 to 10, wherein each of the first pivot block and the second pivot block includes a locking mechanism configured to prevent the respective pivot blocks from pivoting once the tractor unit has engaged the guide rail. A towing device mounting mechanism according to claim 11, wherein the locking mechanism is a bushing. The towing device mounting mechanism of claim 12, wherein the sleeve is arranged so that friction prevents the pivot block from pivoting when the tractor unit has engaged the guide rail. A towing device mounting mechanism according to any one of claims 1 to 13, wherein the profile of the guide rail is one of a concave profile, convex profile, straight profile or any combinations thereof. A towing device mounting mechanism according to any one of claims 1 to 14, wherein sizes of the first rail track and the second track rail of the guide rail are from 1/16 inch to 2 inches, and wherein shapes of the first rail track and the second track track one of round, square, triangular and octagonal included.

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