Boom and dipper handle assembly for an industrial machine

This application claims the benefit of U.S. Provisional Patent Application No. 61/619,361, filed Apr. 2, 2012, the entire contents of which are incorporated herein by reference.

The present invention relates to a boom and a dipper handle for an industrial machine, such as an electric rope or power shovel.

In the mining field, and in other fields in which large volumes of material must be collected and removed from a work site, it is typical to employ industrial machines including a large dipper for shoveling the materials from the work site. Industrial machines, such as electric rope or power shovels, draglines, etc., are used to execute digging operations to remove material from, for example, a bank of a mine. Electric rope shovels typically include a shovel boom, a handle movably coupled to the boom and supporting the dipper, and a pulley or boom sheave rotatably supported on the boom. The handle supports the dipper while the dipper is removing material from the bank. A hoist rope extends over a portion of the boom sheave and is connected to the dipper to raise and lower the dipper, thereby producing an efficient digging motion to excavate the bank of material.

Due to the current configuration and position of the boom and the handle of electric rope shovels, shovel operators generally have difficulties maneuvering the dipper and the dipper handle in the tuck back region of the shovel. Newer shovels also have an increased payload and a larger dipper that reduces the maneuverability of the dipper and the handle even further. At the same time, operators must maintain the flat floor cleaning distance of the shovel and be able to securely and accurately unload the dipper into a vehicle. Due to the payload increase, truck bed heights have also increased, making it harder for the shovel operator to accurately unload the dipper. Increasing the payload, the bail pull, and the reach of a shovel is detrimental to the shovel as it leads to a higher tipping moment range and a higher machine weight because of the necessary counterweight added to the shovel and increased required strength of the structures. This increases the swing inertia (i.e., cycle time), the front idler loading, and the rocking of the shovel that can lead to a lower structural life.

In one embodiment, the invention provides a mining machine supported on a support surface. The mining machine includes a base, a boom, a hoist rope, a member, and a dipper. The base includes a frame portion that is rotatable relative to the support surface about a machine axis. The boom includes a first end coupled to the base, a second end opposite the first end, and a sheave coupled to the second end of the boom. A first distance is defined between the machine axis and the second end of the boom. The hoist rope extends over the sheave. The member is movably coupled to the boom about a pivot point that is positioned substantially between the first end and the second end of the boom. A second distance is defined between the machine axis and the pivot point. A length ratio of the second distance to the first distance is between 27% and 43%. The dipper is coupled to an end of the member and is supported by the hoist rope so that the hoist rope raises the dipper as the rope is reeled in.

In another embodiment, the invention provides a mining machine supported on a support surface. The mining machine includes a base, a boom, a hoist rope, a member, and a dipper. The boom includes a first end coupled to the base, a second end opposite the first end, and a sheave coupled to the second end of the boom. A first height is defined between the support surface and the second end of the boom. The hoist rope extends over the sheave. The member is movably coupled to the boom about a pivot point that is positioned substantially between the first end and the second end of the boom. A second height is defined between the support surface and the pivot point, and a height ratio of the second height to the first height is between 50% and 64%. The dipper is coupled to an end of the member and is supported by the hoist rope such that the hoist rope raises the dipper as the rope is reeled in.

In yet another embodiment, the invention provides a boom for a mining machine including a base and a handle. The boom includes a first end adapted to be coupled to the base, a second end adapted to support a sheave; a boom axis extending through the first end and the second end, and a shipper shaft extending through a width of the boom and defining a transverse axis. A boom distance is defined between the first end and the second end. The shipper shaft is positioned between the first end and the second end. A first distance is defined between the first end of the boom and the shipper shaft, and a first ratio of the first distance to the boom distance is between 20% and 33%.

Other aspects of the invention will become apparent by consideration of the detailed description and accompanying drawings.

FIG. 1 is a side view of an industrial machine.

FIG. 2 is a side view of a boom for the industrial machine of FIG. 1 according to an embodiment of the invention.

FIG. 3A is a perspective view of a dipper and loading vehicle for an industrial machine including a boom according to the prior art.

FIG. 3B is a perspective view of a dipper and loading vehicle for an industrial machine including the boom of FIG. 2 .

FIG. 3C illustrates a top view of an industrial machine and a loading vehicle.

FIG. 4 is a side view of a handle for the industrial machine of FIG. 1 according to an embodiment of the invention.

FIG. 5 is a side view of an electric rope shovel incorporating the boom of FIG. 2 and the handle of FIG. 4 according to an embodiment of the invention.

FIG. 6 is a side view of a portion of the electric rope shovel of FIG. 5 with the handle in a vertical orientation.

FIG. 7 is a side view of a portion of the electric rope shovel of FIG. 5 with the dipper in a tuck-back position.

FIG. 8 is a side view of the electric rope shovel of FIG. 5 .

FIG. 9 is a side view of the boom of FIG. 2 .

FIG. 10 is another side view of the boom of FIG. 2 .

Before any embodiments of the invention are explained in detail, it is to be understood that the invention is not limited in its application to the details of construction and the arrangement of components set forth in the following description or illustrated in the following drawings. The invention is capable of other embodiments and of being practiced or of being carried out in various ways. Also, it is to be understood that the phraseology and terminology used herein is for the purpose of description and should not be regarded as limited.

Although the invention described herein can be applied to, performed by, or used in conjunction with a variety of industrial machines, embodiments of the invention described herein are described with respect to an electric rope or power shovel, such as the power shovel 10 shown in FIG. 1 . The shovel 10 includes a mobile base 15 , a drive mechanism or tracks 20 , a turntable 25 , a revolving frame 30 , a boom 35 , a lower end 40 of the boom 35 (also called a boom foot), an upper end 42 of the boom 35 (also called boom point), tension cables 50 , a gantry tension member 55 , a gantry compression member 60 , a dipper 70 having a door 72 and teeth 73 , one or more hoist ropes 75 , a winch drum (not shown), a dipper arm or handle 85 , a saddle block 90 , a shipper shaft 95 positioned in a shipper shaft aperture 96 (shown in FIG. 2 ), and a transmission unit (also called a crowd drive, not shown). The rotational structure 25 allows rotation of the upper frame 30 relative to the lower base 15 . The turntable 25 defines a rotational axis 27 of the shovel 10 . The rotational axis 27 is perpendicular to a plane 28 defined by the base 15 and generally corresponds to a grade of the ground or support surface.

The mobile base 15 is supported by the drive tracks 20 . The mobile base 15 supports the turntable 25 and the revolving frame 30 . The turntable 25 is capable of 360-degrees of rotation relative to the mobile base 15 . The boom 35 is pivotally connected at the lower end 40 to the revolving frame 30 . The boom 35 is held in an upwardly and outwardly extending relation to the deck by the tension cables 50 , which are anchored to the gantry tension member 55 and the gantry compression member 60 . The gantry compression member 60 is mounted on the revolving frame 30 , and a sheave 45 is rotatably mounted on the upper end 42 of the boom 35 .

The dipper 70 is suspended from the boom 35 by the hoist ropes 75 . The hoist rope 75 is wrapped over the sheave 45 and attached to the dipper 70 at a bail 71 . The hoist rope 75 is anchored to the winch drum (not shown) of the revolving frame 30 . The winch drum is driven by at least one electric motor (not shown) that incorporates a transmission unit (not shown). As the winch drum rotates, the hoist rope 75 is paid out to lower the dipper 70 or pulled in to raise the dipper 70 . The elongated member or dipper handle 85 is also coupled to the dipper 70 . One or more pitch brace links 101 provide a connection between an upper portion of the handle 85 and an upper portion of the dipper 70 . In one embodiment, a length of the pitch brace links 101 can be altered to adjust the angle of the dipper 70 relative to the handle 85 . Aside from this adjustment, the dipper 70 is generally fixed relative to the handle 85 . The dipper handle 85 is slidably supported in a saddle block 90 , and the saddle block 90 is pivotally mounted to the boom 35 at the shipper shaft 95 . The dipper handle 85 includes a rack tooth formation thereon that engages a drive pinion mounted in the saddle block 90 . The drive pinion is driven by an electric motor and transmission unit to extend or retract the dipper handle 85 relative to the saddle block 90 and shipper shaft 95 . Therefore, the handle 85 is movable relative to the boom 35 in both a rotational and translational manner.

An electrical power source is mounted to the revolving frame 30 to provide power to a hoist electric motor for driving the hoist drum, one or more crowd electric motors for driving the crowd transmission unit, and one or more swing electric motors for turning the turntable 25 . Each of the crowd, hoist, and swing motors can be driven by its own motor controller or drive in response to control signals from a controller, as described below.

The shovel 10 also includes a controller (not shown) associated with the operation of shovel 10 . The controller is electrically and/or communicatively connected to a variety of modules or components of the shovel 10 . For example, the controller is connected to one or more sensors, a user interface, one or more hoist motors and hoist motor drives, one or more crowd motors and crowd motor drives, one or more swing motors and swing motor drives, etc. (these elements are not shown in the drawings). The controller includes combinations of hardware and software that are operable to, among other things, control operation of the power shovel 10 , control the position of the boom 35 , the dipper handle 85 , the dipper 70 , etc., monitor the operation of the shovel 10 , etc. The sensors can include, among other things, position sensors, velocity sensors, speed sensors, acceleration sensors, an inclinometer, one or more motor field modules, etc.

In some embodiments, the controller includes a plurality of electrical and electronic components that provide power, operational control, and protection to the components and modules within the controller and/or shovel 10 . For example, the controller includes, among other things, a processing unit (e.g., a microprocessor, a microcontroller, or another suitable programmable device), a memory, input units, and output units (not shown). The processor of the controller sends control signals to control the operations of the shovel 10 . For example, the controller can monitor and/or control, among others, the digging, dumping, hoisting, crowding, and swinging operations of the shovel 10 .

The goal of this invention is to provide a new boom and dipper handle for the shovel 10 that improves the performance of a shovel having an increased payload. By modifying the geometry (e.g., the configuration) and the positioning of the boom 35 and the handle 85 , the invention improves tuck-back maneuverability and the digging envelope of the shovel, while also increasing the flat floor clean-up capability of the shovel. The invention also improves the truck-spotting range of a shovel's operator and improves the operator's line-of-sight. Further, the invention increases the structure life of the shovel's elements.

FIG. 2 illustrates an improved boom 35 B according to one embodiment of the invention and for use with the shovel 10 . In FIG. 2 , boom A (illustrated in broken lines) represents a conventional boom and boom B (illustrated in solid lines) represents the improved boom. The booms A, B are aligned about the boom foot 40 , and each of the booms A, B defines a boom point 42 and a shipper shaft aperture 96 for receiving the shipper shaft 95 . The shipper shaft 95 B ( FIG. 5 ) is in a position to pivotally support the handle 85 B on the boom. The boom point 42 is the point of the boom where the boom connects to the sheave 45 . As shown in FIG. 2 , the shipper shaft aperture 96 B of the boom B is located significantly closer to the rotational axis 27 B ( FIG. 5 ) of the shovel 10 when compared to shipper shaft aperture 96 A for the boom A. For example, in some embodiments, a horizontal distance 97 between the shipper shaft aperture 96 A of the boom A and the shipper shaft aperture 96 B of the boom B is approximately 12 inches. In other words, the shipper shaft aperture 96 B of the boom B is approximately 12 inches closer to the rotational axis 27 B as compared to the shipper shaft aperture 96 A of the boom A. In other embodiments, the shipper shaft aperture 96 B is positioned even closer to the rotational axis 27 B.

As shown in FIG. 2 , the shipper shaft aperture 96 B, and thereby the shipper shaft 95 B of the boom 35 B is positioned higher than the shipper shaft aperture 96 A of the conventional boom A. In one embodiment, a vertical distance 98 between the shipper shaft aperture 96 A of the boom A and the shipper shaft aperture 96 B of the boom B is approximately 22 inches. Further, in one embodiment, a vertical distance 99 between the boom point 42 A of the boom A and the boom point 42 B of the boom B is approximately 22 inches. In other words, the boom point 42 B of the improved boom B positioned higher than the boom point of the boom A. In other embodiments, the vertical distance 99 can be even larger.

Boom 35 B has significant advantages over a boom A. For example, the new position of the shipper shaft aperture 96 B improves visibility for the operator under the boom 35 B. In some embodiments, the boom 35 B improves (i.e., increases) the operator's ground visibility (i.e., the visibility of the area around the shovel 10 ) as well as the operator's visibility of the loading vehicle. FIG. 3A illustrates the view point of a shovel operator operating a shovel 10 with the boom A. FIG. 3B illustrates the improved view point of a shovel operator operating the shovel 10 with the boom 35 B. In addition, FIG. 3C illustrates additional area 77 of the ground that is visible to the operator of the shovel 10 with the boom 35 B.

FIG. 4 illustrates an improved dipper handle 85 B according to one embodiment of the invention. The dipper handle 85 B includes a first end 100 B, which is coupled to the boom 35 B ( FIG. 2 ), and a second end 105 B, which is coupled to the dipper 70 B. The second end 105 B of the handle 85 B includes a first or upper dipper connection lug 107 B, a second or lower dipper connection lug (not visible in FIG. 4 ), and a torsion box 109 B. A lower dipper pin 111 B, received by the lower lug, and an upper dipper pin 113 B, received by the upper lug 107 B through the pitch brace links 101 , connect the dipper handle 85 B to the dipper 70 B. The length of the pitch brace links 101 is adjustable to allow the position and the angle of the dipper 70 B relative to the handle 85 B to be changed. Prior to operation, the pitch brace link 101 is locked so that the dipper 70 B is fixed relative to the handle 85 B. A rack 117 B extends along a lower portion of the handle 85 B and facilitates extension and retraction of the handle 85 B with respect to the boom 35 B. A center line 115 B extends from the first end 100 B to the second end 105 B of the dipper handle 35 B parallel to the bottom flat surface of the rack 117 B. At the first end 100 B of the handle 85 B, the center line 115 B is positioned at equal distance from a top plate 116 B of the handle and a bottom flat surface of the rack 117 B. Further, the second end 105 B of the handle 85 B and the attachment points (i.e., the dipper pins 111 B and 113 B) are not symmetrically positioned about the center line 115 B. In one embodiment, the lugs and the torsion box 109 B of the improved handle 85 B are positioned approximately 24 inches higher in relation to the center line 115 B when compared to a conventional dipper handle.

In one embodiment, a total length C of the rack 117 B is approximately 318 inches. Further, a second lug distance D between the center line 115 B and the lower dipper pin 111 B is approximately 12 inches. Therefore, a ratio between the length C of the rack 117 B and the second lug distance D is approximately 26.5:1 for the dipper handle 85 B. In addition, a first lug distance E between the center line 115 B and the upper dipper pin 113 B is approximately 64 inches. Therefore, a lug ratio between the second lug distance D and the first lug distance E is approximately 1:5 for the dipper handle 85 B. In some embodiments, the ratio between the second lug distance D and the first lug distance E is always different than 1:1 (e.g., 1:2, 1:6, 1:8, 1:10, etc.). At the same time, a tooth angle α of the dipper handle remains the same (i.e., the orientation of the dipper teeth with respect to a bank is the same). As explained in more detail below, the configuration of the dipper handle 85 B increases flat-floor clean-up of the shovel 10 and allows greater tuck-back maneuverability and truck loading range because the torsion box 109 B is pulled closer to the underside of the boom 35 B before interference of the torsion box 109 B with the boom 35 B.

FIG. 5 illustrates the shovel 10 including the improved boom 35 B and dipper handle 85 B discussed above. As mentioned, the shipper shaft 95 B of the boom 35 B is moved approximately 12 inches closer to the rotational axis 27 B of the shovel 10 . Thus, maximum reach of the dipper 70 B is closer to the frame of the shovel 10 and to the rotational axis 27 B when compared to the reach of a conventional dipper that is supported by a conventional boom and handle. A center of gravity 91 B of the boom 35 B is also closer to the rotational axis 27 B than a center of gravity of the boom 35 A. Consequently, as a result of the improved boom 35 B and dipper handle 85 B, less counterweight is required to support the dipper 70 B and the overall machine weight and inertia is reduced. Also, the reduced reach minimizes the overturning tipping moment of the shovel 10 . Although the reach of the dipper 70 B is closer to the rotational axis 27 B than a conventional shovel, the new boom and handle configuration increases the active digging area of the shovel 10 in the low area of the bank and the outer region of a dig envelope “F” shown in FIG. 5 . Therefore, in the illustrated embodiment, the dig envelope F of the dipper 70 B is greater than a conventional shovel 10 by approximately 65 square feet, which improves the overall performance of the shovel 10 .

FIG. 5 further illustrates a door clearance distance 118 B (i.e., a distance from the ground or the plane 28 B to a lower end of the dipper door 72 B when the door 72 B is open) of the shovel 10 . By raising the shipper shaft 95 B of the boom 35 B, the lugs and the torsion box 109 B of the handle 85 B, the door clearance distance 118 B of the shovel 10 increases as compared to a conventional shovel, which allows for easier maneuvering over a truck when the handle 85 B of the shovel is in a horizontal position. Consequently, the shovel 10 can be accurately positioned relative to trucks with increased bed heights and the shovel operator can precisely unload the dipper. In some embodiments, the door clearance 118 B of the shovel 10 is increased to approximately 281 inches (i.e., 46 inches more than a conventional shovel). In other words, the door clearance of the improved shovel increases approximately 19.5 percent as compared to a conventional shovel.

The configuration and attachment of the boom 35 B and the handle 85 B also improves flat floor cleanup of the shovel 10 . In other words, the shovel 10 maintains a longer base of flat floor during every dig cycle. FIG. 5 shows an increased flat floor range 121 B that is defined by the difference between an outermost distance 123 B of flat floor reach from the rotational axis 27 B and an innermost distance 125 B of flat floor reach from the rotational axis 27 B. In some embodiments, the outermost distance 123 B of flat floor reach is approximately 647 inches and the innermost distance 125 B of flat floor reach is approximately 345 inches. In one embodiment, the flat floor range 121 B defined by the boom/handle configuration is approximately 302 inches, which is an approximately 12 inch increase when compared to conventional shovels. In other words, the flat floor range 121 B of the improved shovel increases approximately 4 percent as compared to a conventional shovel. Thus, the outer most distance 123 B of flat floor reach and the flat floor range 121 B are both improved as compared to a conventional shovel.

The boom 35 B and handle 85 B further allows for improvement in vertical tuck-back maneuverability of the shovel 10 . For example, a vertical handle distance 124 B ( FIG. 6 ) of the shovel 10 increases to approximately 56 inches, which is approximately 27 inches more than a conventional shovel. The vertical handle distance 124 B is the distance between the tip of the teeth 73 B and the plane 28 B when the handle 85 B is in a vertical orientation and refracted upwards to a position limited by the dipper 70 B or when the torsion box 109 B enters a collision zone with the boom. In other words, the vertical handle distance 124 B of the shovel increases approximately 93 percent as compared to a conventional shovel. If only the boom 35 B or the handle 85 B are implemented in the shovel 10 , increases to the vertical handle distance, albeit smaller, are also achieved. In addition, FIG. 7 illustrates a tooth radius 126 B of the shovel 10 that relates to the improved tuck back maneuverability of the shovel. The tooth radius 126 B is a distance from the tip of the dipper teeth 73 B to the rotational axis 27 B. As shown in FIG. 7 , in one embodiment, the tooth radius 126 B is approximately 337 inches (e.g., when the handle 85 B is refracted upwards and backwards in a vertical and backward position until a bumper of the dipper 70 B touches the boom 35 B). In that embodiment, the vertical handle distance 124 B increases by 17 inches from approximately 26 inches to approximately 43 inches. In other words, the vertical handle distance 124 B of the improved boom and handle increase by about 65% as compared to a conventional shovel. This configuration improves the vertical and backward tuck-back maneuverability of the shovel 10 .

In some situations, as the dipper 70 B swings over a corner of crawler shoes 39 B ( FIG. 5 ), the dipper 70 B may hit the shoes 39 B. Generally, when the shipper shaft 95 B is moved closer to the rotational axis 27 B, interference between the dipper 70 B and the shoes 39 B of the shovel 10 increases. However, due to the improved handle 85 B the dipper 70 B is moved toward a more forward position (i.e., away from the rotational axis 27 B as shown in FIG. 7 ), the new boom/handle configuration of the shovel 10 allows the shoe interference of the shovel 10 to remain unchanged.

It is to be understood that FIGS. 5-7 illustrate one embodiment of the improved boom/handle configuration. In other embodiments, the position of the shipper shaft aperture 96 B and the shipper shaft 95 B on the boom 35 B may be different, which will also change the position of the dipper handle 85 B on the shovel 10 . FIGS. 8-10 illustrate the shovel 10 and identify different possible positions for the shipper shaft aperture 96 B and the shipper shaft 95 B. The relationship of different points along the boom 35 B and the shovel 10 are illustrated and discussed with respect to FIG. 8 . The relevant points or locations along the boom 35 B and the shovel 10 include the shipper shaft 95 B, the rotational axis 27 B, the boom point 42 B, and the plane 28 B.

As shown in FIG. 8 , a first shipper shaft distance 130 B is defined as a distance, in an X-direction, from the rotational axis 27 B to the shipper shaft 95 B. A first boom point distance 132 B is defined as a distance, in the X-direction, from the rotational axis 27 B to the boom point 42 B. A second shipper shaft distance 134 B is defined as a distance, in a Y-direction, from the shipper shaft 95 B to the plane 28 B. A second boom point distance 136 B is defined as a distance, in the Y-direction, from the boom point 42 B to the plane 28 B. Area 138 B represents a region that includes possible positions for the shipper shift 95 B according to an embodiment of the invention.

In one embodiment, a length ratio between the first shipper shaft distance 130 B and the first boom point distance 132 B is approximately 0.39 (e.g., when the first shipper shaft distance 130 B is approximately 285 inches and the first boom point distance 132 B is approximately 728 inches). Further, a height ratio between the second shipper shaft distance 134 B and the second boom point distance 136 B is approximately 0.51 (e.g., when the second shipper shaft distance 134 B is approximately 417 inches and the second boom point distance 136 B is approximately 814 inches). Referring to FIG. 8 , these ratios are used to define the position of area 138 B within which the shipper shaft can be located for boom 35 B. In one embodiment, a length of the area 138 B in the X-direction is between approximately 27% and 43% of the first boom point distance 132 B. Further, a height of the area 138 B in the Y-direction is between approximately 50% and 64% of the second boom point distance 136 B. Therefore, the shipper shaft 95 B of the improved boom 35 B can be positioned anywhere within the range of the area 138 B and coupled to the improved handle 85 B to achieve the shovel results described above.

FIG. 9 illustrates the improved boom 35 B and the area 138 B that represents the possible positions of the shipper shift 95 B. As in FIG. 8 , the relationship of different points along the boom 35 B are illustrated and discussed with respect to FIG. 9 . The relevant points or locations along the boom 35 B include the boom foot 40 B, the shipper shaft 95 B, and the boom point 42 B. A boom axis 140 B (i.e., the boom length) is defined as a horizontal distance between the boom foot 40 B and the boom point 42 B. In some embodiments, the boom axis 140 B is approximately 810 inches. A first reference distance 142 B is defined as a distance from the boom foot 40 B to the shipper shaft 95 B in a direction parallel to the boom axis 140 B. A second reference distance 144 B is defined as a distance from the boom axis 140 B to the shipper shaft 95 B in a direction perpendicular to the boom axis 140 B.

In one embodiment, a ratio between the first reference distance 142 B and the boom axis 140 B is approximately 0.265 (e.g., when the first reference distance 142 B is approximately 215 inches). Further, a ratio between the second reference distance 144 B and the boom axis 140 B is approximately 0.032 (e.g., when the second reference distance 144 B is approximately 26 inches). Referring to FIG. 9 , these ratios are used to define the position of the area 138 B on the boom 35 B. In one embodiment, the maximum value for the ratio between the first reference distance 142 B and the boom axis 140 B is approximately 0.330 and the minimum value for the first ratio is approximately 0.200. In addition, the maximum value for the ratio between the second reference distance 144 B and the boom axis 140 B is approximately 0.143 and the minimum value for the second ratio is approximately 0.017. Consequently, the shipper shaft 95 B of the improved boom 35 B can be positioned within the range of the area 138 B defined by the two ratios.

FIG. 10 illustrates the boom 35 B and an annulus shape area 139 B that represents possible positions of the shipper shaft 95 B. As in FIGS. 8 and 9 , the relationship of different points along the boom 35 B are illustrated and discussed with respect to FIG. 10 . The relevant points or locations along the boom 35 B include the boom foot 40 B, the shipper shaft aperture 96 B (and thereby the shipper shaft 95 B), and the boom point 42 B. In the illustrated embodiment, the position of the shaft aperture 96 B is identified by an angle θ defined between the boom axis 140 B and a line 149 B extending from the boom foot 40 B through the center of the shaft aperture 96 B. In this embodiment, the angle θ is approximately 7 degrees. Further, a first angle θ 1 is defined between the boom axis 140 B and a line 148 B extending through a lower most region of the annulus area 139 B. A second angle θ 2 is defined between the boom axis 140 B and a line 150 B extending through an upper most region of the annulus area 139 B. In the illustrated embodiment, the angle θ 1 is approximately 3 degrees and the angle θ 2 is approximately 36 degrees.

In the illustrated embodiment, a reference distance or radius R is defined between the boom foot 40 B and the center of the shaft aperture 96 B. It this embodiment, the reference distance R is approximately 216 inches or 27% percent from the boom axis 140 B. The angle θ and the reference distance R define the position of the shaft aperture 96 B (and thereby the shipper shaft 95 B) in the illustrated embodiment. Further, a reference distance or radius R1 is defined as a distance from the boom foot 40 B to the innermost curved region of the annulus area 139 B. A reference distance or radius R2 is defined as a distance from the boom axis 140 B to the outermost curved region of the annulus area 139 B. In the illustrated embodiment, the reference distance R1 is approximately 20 percent from the boom axis 140 B (i.e., 162 inches) and the reference distance R2 is approximately 33 percent from the boom axis 140 B (i.e., 267.5 inches). The angles θ1/θ2 and the reference distances R1/R2 define the boundaries of the annulus shape area 139 B. The shaft aperture 96 B and the shipper shaft 95 B of the improved boom 35 B can be positioned within the area 139 B.

Thus, the invention provides, among other things, a boom and dipper handle assembly for an industrial machine. Although the invention has been described in detail with reference to certain preferred embodiments, variations and modifications exist within the scope and spirit of one or more independent aspects of the invention as described. Various features and advantages of the invention are set forth in the following claims.