WO2017139129A1 - Trancheuse - Google Patents

Trancheuse Download PDF

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Publication number
WO2017139129A1
WO2017139129A1 PCT/US2017/015752 US2017015752W WO2017139129A1 WO 2017139129 A1 WO2017139129 A1 WO 2017139129A1 US 2017015752 W US2017015752 W US 2017015752W WO 2017139129 A1 WO2017139129 A1 WO 2017139129A1
Authority
WO
WIPO (PCT)
Prior art keywords
cam
plate
cam follower
head
channel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/US2017/015752
Other languages
English (en)
Inventor
Douglas MCGUFFIN-NOLL
Peter Dierauer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Globe Food Equipment Co
Original Assignee
Globe Food Equipment Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from US15/042,172 external-priority patent/US20170232628A1/en
Priority claimed from US15/042,179 external-priority patent/US20170232629A1/en
Application filed by Globe Food Equipment Co filed Critical Globe Food Equipment Co
Priority to CA3011544A priority Critical patent/CA3011544A1/fr
Priority to EP17750576.5A priority patent/EP3414064A4/fr
Publication of WO2017139129A1 publication Critical patent/WO2017139129A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D5/00—Arrangements for operating and controlling machines or devices for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D7/00—Details of apparatus for cutting, cutting-out, stamping-out, punching, perforating, or severing by means other than cutting
    • B26D7/06—Arrangements for feeding or delivering work of other than sheet, web, or filamentary form
    • B26D7/0616—Arrangements for feeding or delivering work of other than sheet, web, or filamentary form by carriages, e.g. for slicing machines
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D1/00—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor
    • B26D1/01—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work
    • B26D1/12—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work having a cutting member moving about an axis
    • B26D1/14—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work having a cutting member moving about an axis with a circular cutting member, e.g. disc cutter
    • B26D1/143—Cutting through work characterised by the nature or movement of the cutting member or particular materials not otherwise provided for; Apparatus or machines therefor; Cutting members therefor involving a cutting member which does not travel with the work having a cutting member moving about an axis with a circular cutting member, e.g. disc cutter rotating about a stationary axis
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B26—HAND CUTTING TOOLS; CUTTING; SEVERING
    • B26D—CUTTING; DETAILS COMMON TO MACHINES FOR PERFORATING, PUNCHING, CUTTING-OUT, STAMPING-OUT OR SEVERING
    • B26D2210/00—Machines or methods used for cutting special materials
    • B26D2210/02—Machines or methods used for cutting special materials for cutting food products, e.g. food slicers

Definitions

  • This invention was not made as part of a federally sponsored research or development project.
  • the present disclosure relates generally to adjustable thickness slicers and, more particularly, to food product slicers and the components associated with adjusting a gauge plate.
  • Typical reciprocating slicers have a rotatable, circular or disc-like slicing blade, an adjustable gauge plate for determining the thickness of the slice and a carriage for supporting the product as it is moved back and forth past the cutting edge of the knife during slicing.
  • the gauge plate is situated along the edge of the knife toward the front of a slicing stroke and is laterally movable with respect to the knife for determining the thickness of the slices to be cut.
  • a mechanism such as an adjustment handle for setting a spacing between the plane of the gauge plate surface and the plane of the knife edge for the purpose of slicing is also typically provided so that operators can select a thickness of slices to be produced.
  • Movement of the gauge plate is generally a linear movement of the plane of the gauge plate relative to the plane of the knife edge. Thus, movement of the adjustment handle moves the gauge plate in a manner to make slice thickness adjustments.
  • a product slicer having an adjustable gauge plate precisely positioned by the unique cooperation of a cam plate and a cam follower.
  • FIG. 1 shows an isometric view of a product sheer embodiment
  • FIG. 2 shows a partial isometric view of a product sheer
  • FIG. 3 shows an isometric view of a cam plate, a slider assembly, an adjustment handle and a partial housing
  • FIG. 4 shows an isometric view of a cam plate, a slider assembly, an adjustment handle, a knife cover, a gauge plate and a partial housing;
  • FIG. 5 shows an exploded isometric view of a cam plate, a slider assembly, an adjustment handle and a partial housing
  • FIG. 6 shows an exploded isometric view of a cam plate, a slider assembly, an adjustment handle, a gauge plate and a partial housing;
  • FIG. 7 shows another exploded isometric view of a cam plate, a slider assembly, an adjustment handle and a partial housing
  • FIG. 8 shows a front elevation view of a cam plate embodiment
  • FIG. 9 shows a cross sectional view of a cam plate embodiment
  • FIG. 10 shows front and side elevation views of a cam follower embodiment
  • FIG. 11 shows an isometric view of a slider assembly embodiment
  • FIG. 12 shows an exploded isometric view of a slider assembly embodiment
  • FIG. 13 shows an exploded isometric view of an embodiment having a cam-to- follower biasing mechanism, a cam plate and a slider assembly;
  • FIG. 14 shows embodiment of cam follower having a cam follower channel and another cross sectional view of a cam plate embodiment having a cam plate projection
  • FIG. 15 shows another front elevation view of a cam plate embodiment
  • FIG. 16 shows another front elevation view of a cam plate embodiment
  • FIG. 17 shows another front elevation view of a cam plate embodiment.
  • the present invention enables a significant advance in the state of the art.
  • the preferred embodiments of the invention accomplish this by new and novel arrangements of elements, materials, relationships, and methods that are configured in unique and novel ways and which demonstrate previously unavailable but preferred and desirable capabilities.
  • the description set forth below in connection with the drawings is intended merely as a description of the presently preferred embodiments of the invention, and is not intended to represent the only form in which the present invention may be constructed or utilized.
  • the description sets forth the designs, materials, functions, means, and methods of implementing the invention in connection with the illustrated embodiments. It is to be understood, however, that the same or equivalent functions, features, and material properties may be accomplished by different embodiments that are also intended to be encompassed within the spirit and scope of the invention.
  • the present disclosure is described with reference to the
  • FIG. 1 represents an embodiment of a product sheer (100) having a housing (200) that acts as external shell of the product sheer (100). Furthermore, the housing (200) provides a mounting foundation onto which various product sheer (100) components are attached. Some components may attach to other assemblies and parts which ultimately connect to a portion of the housing (200), thus reference to components "mounted to” or “attached to” to the housing (200) simply means that the components are ultimately supported via the housing (200), which need not be a direct connection to the housing (200) but may be via connection to, or interaction with, other components.
  • the product sheer (100) has a circular knife (300) mounted to the housing (200) which rotates about a knife axis (310) located in the center of the knife (300). Additionally, the knife (300) has a knife cutting edge (320) that is located around the knife's (300) perimeter which defines a knife cutting plane.
  • the knife (300) may be covered by a knife cover (330), as seen in FIGS. 1 and 2, during use in order to prevent injury to the end user.
  • the product sheer (100) has a carriage assembly (400) is configured for reciprocating motion past the knife cutting edge (320) and is slidably attached by a carriage assembly arm (420) to the housing (200).
  • the carriage assembly (400) may include a carriage assembly handle (410) which provides a hold point for the end user, as seen in FIG. 1.
  • the carriage assembly (400) cradles the product being sliced while reciprocating motion is provided manually by a user, or automatically by an electric motor, pneumatic motion system, or electromagnetic motion system.
  • the variability of product slice thickness is obtained through the use of an adjustable gauge plate (500), which in some embodiments has a gauge plate mount (510) and a gauge plate mount nut (520).
  • the gauge plate mount (510) joins the adjustable gauge plate (500) to a slider assembly (900), which may have a cooperating gauge plate receiver (940), as illustrated in FIGS. 2-7.
  • the gauge plate receiver (940) mates with the gauge plate mount (510) and are attached together by the gauge plate mount nut (520).
  • FIG. 6 shows an embodiment where the gauge plate mount (510) is a post extending from the gauge plate (500), which may pass through a portion of the housing (200), and the gauge plate receiver (940) is an aperture located on the slider assembly (900).
  • the gauge plate mount (510) may receive a post extending from the slider assembly (900).
  • the cam follower (800), the slider assembly (900), and the adjustable gauge plate (500) may each be separate and distinct components as illustrated in the figures, however the cam follower (800) may be an integral piece formed in the slider assembly (900), and the slider assembly (900) may be an integral portion of the adjustable gauge plate (500); in other words they need not be three separate and distinct pieces.
  • the slider assembly (900) may include a slide rail
  • the slide rail (910) is slidably coupled to the other components of the slider assembly (900) with mount brackets (920), which may include mount bracket bearings (922).
  • mount bracket bearings (922) allow for smooth low force linear travel of the slide rail (910) during the adjustment of the product sheer (100).
  • the slider assembly (900) also has a set of gauge plate adjustment screws (950) that allows the gauge plate (500) to be aligned, or zeroed out, with the knife (300) cutting plane and establish the gauge plate initial position.
  • the gauge plate (500) may have a gauge plate bearing surface (530) onto which sliceable product rest while cradled in the carriage assembly (400).
  • the bearing surface (530) need not be flat.
  • the gauge plate (500) is configured so that the gauge plate bearing surface (530) is substantially parallel to the knife cutting plane.
  • the adjustable gauge plate (500) is adjustable in an adjustment direction, which in the figures is parallel to the knife axis (310), from a gauge plate initial position, with the gauge plate bearing surface (530) that is substantially in the knife cutting plane, to a gauge plate (500) slicing position where the gauge plate bearing surface (530) is offset from the knife cutting plane.
  • the adjustment direction need not be parallel to the knife axis (310).
  • the gauge plate (500) slicing position is not limited to one specific thickness but can be varied based upon the sliceable product and its intended use. For instance, a ham may be sliced in a thickness of less than half of a millimeter to created what is called shredded ham; the ham may be sliced at 1 to 3 millimeters to create sandwich slices; additionally, the ham may be sliced at 7 millimeters or more to created ham steaks.
  • the product sheer (100) has an adjustment handle (600) ratably mounted to the housing (200), as seen in FIGS. 1, 2 and 4.
  • the adjustment handle (600) may be connected to a cam plate (700) through an opening in the housing (200) by an adjustment handle shaft (610), as seen in FIGS. 3, 5 - 7, or vice versa, so that the cam plate (700) rotates in conjunction with the adjustment handle (600).
  • references to the adjustment handle (600) need not be a handle in the traditional sense and may include touchscreen controls, touchpad controls, and/or buttons/keys that control the activation of a power drive system that in turn rotates the cam plate (700) to achieve the desired movement of the gauge plate (500).
  • one embodiment includes a gauge plate location sensor system that senses the location of the gauge plate (500); and a user may enter, or select, a desired thickness from the touchscreen controls, touchpad controls, and/or buttons/keys causing a drive system to rotate the cam plate (700) until the sensor system senses the desired thickness.
  • the gauge plate location sensor system includes a sensor measuring the location of the gauge plate (700) in relation to the circular knife (300) or knife axis (310), and feeds the location data to a gauge plate controller in communication with the thickness input device (i.e. the touchscreen controls, touchpad controls, and/or buttons/keys), as well as the drive system, wherein the controller instructs the operation of the drive system to achieve the desired thickness.
  • the thickness input device i.e. the touchscreen controls, touchpad controls, and/or buttons/keys
  • the cam plate (700) may include a cam plate diameter (710), a cam plate thickness (720), a cam plate hub (730) with a cam plate hub thickness (732) and a cam plate hub diameter (734), a cam plate center axis (760), a cam plate center axis (760), and a cam plate turn limit (770).
  • the cam plate hub (730) provides an attachment area for the adjustment handle shaft (610), alternatively the adjustment handle (600) may include a hub that proves an attachment area for a cam plate shaft. As the adjustment handle (600) is rotated, the cam plate (700) rotates about the cam plate's center axis (760).
  • the cam plate (700) may include a cam plate turn limit (770), as illustrated in FIG. 7, to prevent damage to the product sheer (100) from overturning of the cam plate (700), and more specifically to prevent the cam follower (800) from getting to either end of the cam plate channel (740) and exit the cam plate channel (740), particularly in embodiments having angled cooperating surfaces on the cam plate channel (740) and the cam follower (800).
  • the cam plate (700) may include a cam plate channel (740), as seen in FIG. 9, or a cam plate projection (780), as seen in FIG. 14.
  • the product sheer (100) has a cam follower (800) having a cam follower head (810) which engages the cam plate channel (740), as seen in FIG. 3.
  • the cam follower (800) may include a cam follower stem (820), having a cam follower stem length (822), a cam follower stem proximal end (824), a cam follower stem distal end (826), a cam follower stem diameter (828), and a cam follower attachment engager (829).
  • cam follower (800) may be connected to the slider assembly (900) in a cam follower mounting bracket (930) with a cam follower retainer attachment (830) that engages the cam follower retainer attachment engager (829) located on the cam follower stem distal end (826), as seen in FIGS. 10-12.
  • the slider assembly (900) is connected to the adjustable gauge plate (500).
  • the cam follower head (810) engages the cam plate channel (740) at an initial cam head position (860).
  • Rotation of the adjustment handle (600) causes rotation of the cam plate (700) thereby moving the cam follower head (810) within the cam plate channel (740) to a slicing cam head position (870).
  • the repositioned cam follower (800) moves the slider assembly (900) and the adjustable gauge plate (500) to the gauge plate slicing position.
  • the product sheer (100) has an initial head-to-cam-center distance (862), which is defined as the distance from the center of the initial cam head position to the cam plate center axis (760).
  • the initial head-to-cam-center distance (862) is greater than a slicing head- to-cam-center distance (872), which is defined as the distance from the center of the slicing cam head position to the cam plate center axis (760).
  • a slicing head- to-cam-center distance (872) is defined as the distance from the center of the slicing cam head position to the cam plate center axis (760).
  • FIG. 15 illustrates the cam follower (800) moving circumferentially about the cam plate center axis (760) simply for ease in illustrating the key relationships, when in actuality it is the cam plate (700) that rotates causing the cam follower (800) to translate in a single direction.
  • Tables 1 and 2 below illustrate an embodiment of the relationship of the initial head- to-cam-center distance (862) and the slicing head-to-cam-center distance (872), for various rotations of the cam plate (700).
  • the delta ( ⁇ ) column for each specific rotation value of the cam plate (700) is the initial head-to-cam-center distance (862) minus the slicing head-to- cam-center distance (872).
  • the delta ( ⁇ ) values are always positive because the cam follower (800) moves from the initial cam head position (860), toward the cam plate center axis (760), to the slicing cam head position (870), unlike traditional systems that move in the opposite direction at the sacrifice of performance and fine-tuning control.
  • Tables 1 and 2 below illustrate an embodiment of the relationship of the initial head-to-cam-center distance (862) and the slicing head-to-cam-center distance (872), for various rotations of the adjustment handle (600).
  • an advantage of this unique configuration is that a significant rotation of the cam plate (700), or adjustment handle (600), is required to produce a meaningful displacement of the adjustable gauge plate (500) from the gauge plate initial position to the gauge plate slicing position.
  • the delta ( ⁇ ) value which is the difference between the initial head-to-cam-center distance (862) and the slicing head-to-cam-center distance (872), directly correlates to the change in distance of the adjustable gauge plate (500) from the gauge plate initial position to the gauge plate slicing position.
  • rotation of the adjustment handle (600) through any 45 degrees produces a change from the gauge plate initial position to the gauge plate slicing position of no more than 0.100 inch, and results in the slicing head-to-cam-center distance (872) being 2-8% less than the initial head-to-cam- center distance (862); and a further embodiment produces a change from the gauge plate initial position to the gauge plate slicing position of no more than 0.080 inch, and results in the slicing head-to-cam-center distance (872) being 3-6% less than the initial head-to-cam- center distance (862).
  • rotation of the adjustment handle (600) through any 90 degrees produces a change from the gauge plate initial position to the gauge plate slicing position of no more than 0.200 inch, and results in the slicing head-to-cam- center distance (872) being 4-16% less than the initial head-to-cam-center distance (862); and a further embodiment produces a change from the gauge plate initial position to the gauge plate slicing position of no more than 0.160 inch, and results in the slicing head-to-cam- center distance (872) being 6-12% less than the initial head-to-cam-center distance (862).
  • the relative change in position of the cam plate (700) to the cam follower (800) from the initial cam head position (860) to the slicing cam head position (870) is a travel length (880), illustrated in FIG. 16.
  • the preferential control is achieved when the travel length (880) is relatively long compared to the difference from the initial head-to-cam- center distance (862) to the slicing head-to-cam-center distance (872), or delta ( ⁇ ) value; in other words, when an travel-delta ratio of the travel length (880) to the delta ( ⁇ ) value is high and the delta ( ⁇ ) value is positive.
  • preferential control is achieved when the travel length (880) is relatively long compared to rotation of the cam plate (700); in other words, when an travel-rotation ratio of the travel length (880) to the degrees of rotation of the cam plate (700), or slicing angle, associated with the movement from the initial cam head position (860) to the slicing cam head position (870), is high.
  • Table 3 illustrates characteristics of this embodiment through the first 10 degrees of rotation of the cam plate (700).
  • the initial cam head position (860) is at 0 degrees and has an initial head-to-cam-center distance (862) of 1.748".
  • a first slicing head-to- cam-center distance (872) is 1.744"
  • a first delta ( ⁇ ) value is a positive 0.004", meaning that the rotation of the cam plate (700) results in the cam follower (800) moving closer to the cam plate center axis (760).
  • first travel length (880) of 0.076" which produces a first travel-delta ratio of 19.00 and a first travel-rotation ratio of 0.030.
  • second slicing head-to-cam-center distance (872) is 1.739"
  • a second delta ( ⁇ ) value is a positive 0.009.
  • preferential control is achieved when the delta ( ⁇ ) value is a positive, the travel-delta ratio is high, or when an travel-rotation ratio is high, or a combination thereof.
  • the delta ( ⁇ ) value is negative, meaning that rotation of the cam plate (700) causes the cam follower (800) to move away from the cam plate center axis (760) as the cam follower (800) goes from the initial cam head position (860) to the slicing cam head position (870), as seen in FIG. 17.
  • Table 4 illustrates characteristics of such a negative delta ( ⁇ ) value embodiment through the first 10 degrees of rotation of the cam plate (700).
  • the initial cam head position (860) is at 0 degrees and has an initial head-to-cam-center distance (862) of 0.334".
  • a first slicing head-to-cam-center distance (872) is 0.339"
  • a first delta ( ⁇ ) value is a negative 0.005", meaning that the rotation of the cam plate (700) results in the cam follower (800) moving away from the cam plate center axis (760).
  • first travel length (880) of 0.0129" which produces a first travel-delta ratio of -2.58 and a first travel- rotation ratio of 0.0052.
  • first 10 degrees of rotation of the cam plate (700) from the initial cam head position (860) has a travel length (880) that is at least 0.075", while in a further embodiment it is at least 0.150", and in an even further embodiment it is at least 0.225".
  • first 10 degrees of rotation of the cam plate (700) from the initial cam head position (860) also produces a travel length (880) that is less than 0.600", while in a further embodiment it is less than 0.500", and in an even further embodiment it is less than 0.400".
  • a second series of positive delta ( ⁇ ) value embodiments preferred control is achieved when the first 10 degrees of rotation of the cam plate (700) from the initial cam head position (860) has an travel-delta ratio that is positive and at least 3.0 throughout the entire 10 degree range, while in a further embodiment it is at least 5.0, and in an even further embodiment it is at least 10.0.
  • the first 10 degrees of rotation of the cam plate (700) from the initial cam head position (860) has an travel-delta ratio that is positive and less than 40, while in a further embodiment it is less than 30, and in an even further embodiment it is less than 25.
  • preferred control is achieved when the first 10 degrees of rotation of the cam plate (700) from the initial cam head position (860) has an travel-rotation ratio that is at least 0.010 throughout the entire 10 degree range, while in a further embodiment it is at least 0.015, and in an even further embodiment it is at least 0.020.
  • the first 10 degrees of rotation of the cam plate (700) from the initial cam head position (860) has an travel-rotation ratio that is less than 0.100, while in a further embodiment it is less than 0.075, and in an even further embodiment it is less than 0.050.
  • a fourth series of positive delta ( ⁇ ) value embodiments preferred control is achieved when for the first 45 degrees of rotation of the cam plate (700) from the initial cam head position (860), each slicing head-to-cam-center distance (872) is at least 25% of the cam plate diameter (710), while it is at least 30% in another embodiment, and at least 35% in yet another embodiment.
  • preferred control is achieved when for the first 90 degrees of rotation of the cam plate (700) from the initial cam head position (860), each slicing head-to-cam-center distance (872) is at least 25% of the cam plate diameter (710), while it is at least 30% in another embodiment, and at least 35% in yet another embodiment.
  • each slicing head-to-cam-center distance (872) is at least 20% of the cam plate diameter (710), while it is at least 25% in another embodiment, and at least 30% in yet another embodiment.
  • Such embodiments having long travel lengths (880) compared to the rotation of the cam plate (700), and thus the difference from the initial head-to-cam-center distance (862) to the slicing head-to-cam-center distance (872), or delta ( ⁇ ) value, and the criticality of the associated ranges and ratios, produce unexpected performance improvements characterized by finer and more accurate control, with reduced backlash and improved repeatability, in part because for a particular angular rotation of the cam plate (700) the travel length (880) is significantly increased over conventional systems, which is apparent when comparing FIGS. 16 and 17.
  • Increasing the travel length (880) increases the contact area of the cam plate (700) and cam follower (800) throughout a given range of motion, which leads to smoother operation and reduction of the impact of any initial lurch that occurs upon initial rotation of the cam plate (700) when the initial resistance to rotation is overcome. For instance, if the initial lurch upon overcoming friction is 10% of the cam follower proximal head width (816) the impact is less in embodiments having longer travel lengths (880). Further, the increased travel length (880) reduces the likelihood of deformation of the cam plate (700) within the region of most common use.
  • One embodiment obtains such performance improving relationships through the use of a cam plate channel (740), as seen in FIGS. 8 and 9, or a cam plate projection (780), as seen in FIG. 14, that include a portion of a two-dimensional spiral.
  • the portion of the spiral may include a logarithmic spiral, Archimedean spiral, Euler spiral, hyperbolic spiral, lituus, Fabonacci spiral, spiral of Theodorus, and/or the involute of a circle.
  • the performance improving relationships are achieved through the use of a cam plate channel (740) or a cam plate projection (780) that simply includes a portion of a curve that varies in distance from the cam plate center axis (760).
  • the portion of the spiral, or the portion of the curve extend throughout at least 90 degrees of the cam plate (700), while in a further embodiment it extends throughout at least 180 degrees of the cam plate (700), while in an even further embodiment it extends throughout at least 225 degrees of the cam plate (700), and in yet another embodiment it extends throughout at least 270 degrees of the cam plate (700), and in still a further embodiment it extends throughout at least 315 degrees of the cam plate (700). Another embodiment achieves the performance improving
  • cam plate channel (740) or a cam plate projection (780) that incorporates a portion of a straight line, or multiple straight line segments, that varies in distance from the cam plate center axis (760).
  • the cam plate channel (740) has a first channel sidewall (742), with at least a portion oriented at a first sidewall angle (743) greater than zero, and a second channel sidewall (744), with at least a portion oriented at a second sidewall angle (745) greater than zero.
  • the cam plate channel (740) may have a channel exterior width (748), a channel interior width (750), and in some embodiments a cam plate channel floor (746).
  • the cam follower (800) may have a cam follower head (810) with at least a portion of the cam follower head (810) having an angled head surface oriented at a cam follower pitch (818) that is greater than zero. The cam follower head (810) engages the cam plate channel (740), as seen in FIG. 3.
  • cam plate channel (740) having pitched sidewalls (742, 744) and the mating cam follower head (810) having with a corresponding cam follower pitch (818) allows for the compensation of cam plate channel (740) and cam follower head (810) due to wear, thereby reducing backlash.
  • the cam plate channel (740) has a first channel sidewall (742), with at least a portion oriented at a first sidewall angle (743) greater than five degrees, and a second channel sidewall (744), with at least a portion oriented at a second sidewall angle (745) greater than five degrees.
  • at least a portion of the cam follower head (810) has a cam follower pitch (818) that is within 2.5 degrees of the first sidewall angle (743) and the second sidewall angle (745).
  • cam plate channel (740) having pitched sidewalls (742, 744) and the mating cam follower head (810) having with a cam follower pitch (818) that is within 2.5 degrees of the first sidewall angle (743) and the second sidewall angle (745) allows for the compensation of cam plate channel (740) and cam follower head (810) wear and further reduces backlash.
  • a still further embodiment incorporates a cam plate channel (740) with at least a portion oriented at a first sidewall angle (743) of 5-45 degrees, and at least a portion oriented at a second sidewall angle (745) of 5-45 degrees.
  • the cam follower (800) has a cam follower head (810) with at least a portion of the cam follower head (810) having an angled head surface oriented at a cam follower pitch (818) of 5-45 degrees to further compensate for wear of the cam plate channel (740) and cam follower (800).
  • Another embodiment has a cam plate channel (740) with a first channel sidewall (742) having at least a portion oriented at a first sidewall angle (743) of 10-45 degrees, and a second channel sidewall (744) having at least a portion oriented at a second sidewall angle (745) of 10-45 degrees, as well as a cam follower (800) having a cam follower head (810) with at least a portion of the cam follower head (810) having an angled head surface oriented at a cam follower pitch (818) of 10-45 degrees.
  • another embodiment has a cam plate channel (740) with a first channel sidewall (742) having at least a portion oriented at a first sidewall angle (743) of 15-45 degrees, and a second channel sidewall (744) having at least a portion oriented at a second sidewall angle (745) of 15-45 degrees, as well as a cam follower head (810) with at least a portion of the cam follower head (810) having an angled head surface oriented at a cam follower pitch (818) of 15-45 degrees; while another embodiment has a cam plate channel (740) with a first channel sidewall (742) having at least a portion oriented at a first sidewall angle (743) of 20-30 degrees, and a second channel sidewall (744) having at least a portion oriented at a second sidewall angle (745) of 20-30 degrees, as well as a cam follower head (810) with at least a portion of the cam follower head (810) having an angled head surface oriented at a cam follower pitch (818) of 20-30
  • the cam follower proximal head width (816) is greater than the channel exterior width (748), as seen in FIG. 9, while in a further embodiment the cam follower proximal head width (816) is at least 10% greater than the channel exterior width (748), further accommodating wear while also ensuring the cam follower (800) does not bottom out in the cam plate channel (740) and introduce additional friction into the system.
  • a further embodiment ensures a preferred contact between the cam follower (800) and the cam plate channel (740) by having a cam follower distal head width (814) is less than the channel interior width (750).
  • Still another embodiment reduces the risk of bottoming out by incorporating a cam plate channel (740) having both a channel depth (752) and a channel converging sidewall depth (753), and the cam follower head (810) has a cam follower head length (812) that is less than the channel depth (752), while in a further embodiment the channel converging sidewall depth (753) is less than the cam follower head length (812).
  • Preferential contact and reduced stress, while controlling friction and reduced backlash potential are further achieved in an embodiment having a channel converging sidewall depth (753) that is at least 30% of the channel depth (752), while in another embodiment the channel converging sidewall depth (753) is at least 50% of the channel depth (752), and in yet a further embodiment the channel converging sidewall depth (753) is 30- 75% of the channel depth (752).
  • the channel exterior width (748) is 0.125"-0.500", while in a further embodiment it is 0.175"-0.450", and in an even further embodiment it is 0.200"-0.400".
  • the channel depth (752) is 0.125"-0.500", while in a further embodiment it is 0.175"-0.450", and in an even further embodiment it is 0.200"-0.400".
  • the channel exterior width (748) is no more than 15% of the cam plate diameter (710), and the channel depth (752) of FIG. 9, or the cam plate projection length (782) of FIG. 14, which is discussed in detail below, is no more than 60% of the cam plate thickness (720).
  • the channel exterior width (748) is no more than 10% of the cam plate diameter (710) and the channel depth (752), or the cam plate projection length (782), is no more than 50% of the cam plate thickness (720).
  • the cam plate hub thickness (732) is at least 50% of the cam plate thickness (720), while in a further embodiment the cam plate hub thickness (732) is 50-150%) of the cam plate thickness (720), and in yet another embodiment the cam plate hub thickness (732) is 75-125%) of the cam plate thickness (720).
  • cam plate projection (740) and the cam follower (800) are also applicable to the cam plate projection (780) and the cam follower (800), as seen in FIG. 14.
  • all of the disclosed relationships disclosed herein in relation to a cam plate channel (740), and movement of the cam follower (800) apply equally to cam plate projection (780) embodiments, which is also true of FIG. 8 and section line 9-9, which can be thought of as section line 14-14 in cam plate projection (780) embodiments such as that illustrated in FIG. 14.
  • these geometries and relationships promote smooth operation of the cam plate (700) and cam follower (800) interface, and reduce backlash.
  • the cam plate projection (780) has a cam plate projection length (782), a cam plate distal projection width (784), a cam plate proximal projection width (786) and a cam plate projection pitch (788).
  • the cam plate (700) rotates about the cam plate's center axis (760).
  • the cam follower (800) has a cam follower head (810) that has a slotted configuration, as seen in FIG. 14.
  • the cam follower head (810) has a cam follower channel (840) having a cam follower first channel sidewall (842), which has a cam follower first sidewall angle (843), a cam follower second channel sidewall (844), which has a cam follower second sidewall angle (845), and in some embodiments a cam follower channel floor (846). Furthermore, the cam follower channel (840) further includes a cam follower channel exterior width (848), a cam follower channel interior width (850), a cam follower channel depth (852), and a cam follower channel converging sidewall depth (853).
  • the cam follower first channel sidewall (842) has at least a portion with a cam follower first sidewall angle (843) greater than zero
  • the cam follower second channel sidewall (844) has at least a portion with a cam follower second sidewall angle (845) greater than zero
  • the cam plate projection (780) may have a portion with an angled projection surface oriented at a cam plate projection pitch (788) that is greater than zero.
  • wear to the cam plate projection (780) and/or the cam follower (800) does not result in unwanted movement in the gauge plate (500).
  • the pitched configuration of the sidewalls (842, 844) and the corresponding cam plate projection pitch (788) compensate.
  • cam follower first sidewall angle (843) of greater than five degrees
  • cam follower second channel sidewall (844) is oriented at a cam follower second sidewall angle (845) of greater than five degrees
  • at least a portion of the cam plate projection (780) has a cam plate projection pitch (788) that is within 2.5 degrees of the cam follower first sidewall angle (843) and the cam follower second sidewall angle (845).
  • at least a portion of the cam follower first channel sidewall (842) is oriented at a cam follower first sidewall angle
  • cam plate projection (780) has a cam plate projection pitch (788) of 5-45 degrees.
  • cam follower first channel sidewall (842) is oriented at a cam follower first sidewall angle (843) of 10-45 degrees
  • cam follower second channel sidewall (844) is oriented at a cam follower second sidewall angle (845) of 10-45 degrees.
  • at least a portion of the cam plate projection (780) has a cam plate projection pitch (788) of 10-45 degrees.
  • another embodiment has at least a portion of the cam follower first channel sidewall (842) is oriented at a cam follower first sidewall angle (843) of 15-45 degrees, and at least a portion of the cam follower second channel sidewall (844) is oriented at a cam follower second sidewall angle (845) of 15-45 degrees.
  • at least a portion of the cam plate projection (780) has a cam plate projection pitch (788) of 15-45 degrees; while another embodiment has a cam follower first sidewall angle (843) of 20-30 degrees, and a cam follower second sidewall angle (845) of 20- 30 degrees.
  • at least a portion of the cam plate projection (780) has a cam plate projection pitch (788) of 20-30 degrees.
  • cam plate proximal projection width (786) is greater than the cam follower channel exterior width (848), while in a further embodiment the cam plate proximal projection width (786) is at least 10% greater than the cam follower channel exterior width (848), further accommodating wear while also ensuring the cam plate projection (780) does not bottom out in the cam follower channel (840) and introduce additional friction into the system.
  • a further embodiment ensures a preferred contact between the cam follower (800) and the cam plate projection (780) by having a cam plate distal projection width (784) is less than the cam follower channel interior width (850).
  • Still another embodiment reduces the risk of bottoming out by incorporating a cam follower channel (840) having both a cam follower channel depth (852) and a cam follower channel converging sidewall depth (853), and the cam plate projection (780) has a cam plate projection length (782) that is less than the cam follower channel depth (852), while in a further embodiment the cam follower channel converging sidewall depth (853) is less than the cam plate projection length (782).
  • cam follower channel converging sidewall depth (853) that is at least 30% of the cam follower channel depth (852), while in another embodiment the cam follower channel converging sidewall depth (853) is at least 50% of the cam follower channel depth (852), and in yet a further embodiment the cam follower channel converging sidewall depth (853) is 30- 75%) of the cam follower channel depth (852).
  • Wear accommodation, and backlash reduction may be further reduced in embodiments incorporating a cam-to-follower biasing mechanism (1000) to bias the cam follower head (810) and the cam plate (700) against one another, as seen in FIGS. 12 and 13.
  • the cam-to-follower biasing mechanism (1000) includes a cam follower biasing mechanism (1010) that exerts a biasing force to force the cam follower (800) against the cam plate (700), as seen in FIG. 12.
  • the cam-to-follower biasing mechanism (1000) includes a cam plate biasing mechanism (1020) that exerts a biasing force to force the cam plate (700) against the cam follower (800), as seen in FIG. 13.
  • a further embodiment incorporates both a cam follower biasing mechanism (1010) and a cam plate biasing mechanism (1020). Ensuring a relatively consistent force to bias the cam follower head (810) and the cam plate (700) against one another accommodates wear of the components and reduces the amount of play in the system thereby enhancing the control and reducing backlash.
  • the biasing force is at least 2 lbf, while in a further embodiment the biasing force is less than 12 lbf, and in an even further embodiment the biasing force is 4-10 lbf, with is further narrowed in another embodiment to 6-8 lbf.
  • the cam-to-follower biasing mechanism (1000) is adjustable so that the biasing force may be fine-tuned upon assembly, adjusted to a user's preference, and/or adjusted for component wear over time.
  • the position of the cam follower (800), and thus the cam follower head (810) is adjustable, which changes the amount that the cam follower biasing mechanism (1010) is compressed, thereby changing the biasing force.
  • the adjustable cam-to-follower biasing mechanism (1000) is capable of changing the biasing force by at least 1 lbf; while in another embodiment is may change the biasing force by 1-8 lbf; and in yet a further embodiment it may change the biasing force by 2-4 lbf.
  • the biasing force is at least 2 lbf and is adjustable ⁇ 1 lbf; while in another embodiment the biasing force is 2-12 lbf and is adjustable ⁇ 6 lbf; and in yet a further embodiment the biasing force is 4-10 lbf and is adjustable ⁇ 3 lbf.
  • At least one of the cam plate (700) and the cam follower (800) are formed of metallic material, and one of the cam plate (700) and the cam follower (800) are formed of non-metallic material.
  • majority of the cam plate (700) is formed of a non-metallic material and the portion of the cam follower (800) in contact with the cam plate (700) is formed of a metallic material.
  • the non-metallic component is formed of a non-metallic material having a non-metallic material density of less than 2 grams per cubic centimeter and a tensile modulus of at least 4500 MPa (ISO 527-1/-2 test standard); while in a further embodiment the non- metallic material density of less than 1.5 grams per cubic centimeter and a tensile modulus of at least 5000 MPa (ISO 527-1/-2 test standard).
  • the non-metallic material has a non-metallic material tensile strength of at least 85 megapascal (ISO 527-1/-2 test standard), and a non-metallic material strain at break of at least 3.0% (ISO 527-1/-2 test standard); while in an even further embodiment the non-metallic material tensile strength of at least 90 megapascal (ISO 527-1/-2 test standard), and a non-metallic material strain at break of at least 4.0% (ISO 527-1/-2 test standard).
  • the non-metallic component tensile modulus is at least 2 percent of metallic component tensile modulus and the metallic material density is at least 3 times the non-metallic material density.
  • a strain ratio of the metallic material strain at break to the non-metallic material strain at break is less than 25, while in an even further embodiment the strain ratio is less than 20.
  • Conventional thinking would be to make the non-metallic component as strong as possible, which leads to a part formed of material having a high ultimate tensile strength, but one that is generally plagued by a strain at break of 2.5% or less, leading to a large strain ratio and resulting in durability issues. Focusing on unique strain relationships, rather than simply ultimate tensile strength, provide enhanced durability. Such a multi-material interface possessing these unique relationships among the materials achieves the desired durability and wear control, while promoting smooth operation of the interface.
  • the metallic component is formed of a metallic material having a metallic material density of greater than 4 grams per cubic centimeter and a tensile modulus of at least 150 GPa (ISO 527-1/-2 test standard); while in a further embodiment the metallic material density of at least 6 grams per cubic centimeter and a tensile modulus of at least 175 GPa (ISO 527-1/-2 test standard).
  • the metallic material has a metallic material tensile strength of at least 400 megapascal, and a metallic material strain at break of at least 50%; while in an even further embodiment the metallic material tensile strength of at least 450 megapascal, and a metallic material strain at break of at least 60%.
  • the non-metallic component material includes a lubricating agent so that the non-metallic component is self-lubricating.
  • the non- metallic component has a specific wear rate against steel of less than 10 (10 ⁇ 6 mm ⁇ /Nm), wherein the specific wear rate was measured at low speed (0.084 m/s) with a contact pressure of 0.624 MPa in a reciprocating motion (total sliding distance: 4.25 km), while in a further embodiment the non-metallic component has a specific wear rate against steel of less than 7 (10 ⁇ 6 mm ⁇ /Nm), and in an even further embodiment the non-metallic component has a specific wear rate against steel of less than 4 (10 ⁇ 6 mm ⁇ /Nm).
  • the non-metallic component material has a dynamic coefficient of friction against steel is less than 0.50, wherein the coefficient of friction was measured at a high speed (0.5 m/s) with a load of 10 N in a sliding motion (Block-on-Ring), while in a further embodiment the dynamic coefficient of friction against steel is less than 0.40, and less than 0.30 in an even further embodiment.
  • the non-metallic component is an engineering thermoplastic.
  • the non-metallic component is composed primarily of a material selected from polyoxymethylene (POM), poly(methyl methacrylate) (PMMA), acrylonitrile butadiene styrene (ABS), polyamide, polylactic acid (polylactide), polybenzimidazole (PBI), polycarbonate (PC), polyether sulfone (PES), polyether ether ketone (PEEK), polyetherimide (PEI), polyethylene (polyethene, polythene, PE), polyphenylene oxide (PPO), polyphenylene sulfide (PPS), polypropylene (PP), polystyrene, polyvinyl chloride (PVC), polybutylene terephthalates (PBT), thermoplastic polyurethane (TPU), and semi-crystalline engineering resin systems that meet the claimed mechanical properties.
  • the non- metallic material is a polyoxymethylene (POM) homopoly
  • the non-metallic material may be fiber reinforced.
  • the non-metallic material includes at least 5% fiber reinforcement.
  • the fiber reinforcement includes long-glass fibers having a length of at least 10 millimeters pre-molding and produce a finished component having fiber lengths of at least 3 millimeters, while another embodiment includes fiber reinforcement having short- glass fibers with a length of at least 0.5-2.0 millimeters pre-molding. Incorporation of the fiber reinforcement increases the tensile strength of the component, however it may also reduce the strain at break therefore a careful balance must be struck to maintain sufficient elongation and ensure durability of the non-metallic component.
  • one embodiment includes less than 50% fiber reinforcement, while in an even further embodiment has 5-40% fiber reinforcement, and yet another embodiment has 10-30% fiber reinforcement.
  • Long fiber reinforced non-metallic materials, and the resulting melt properties produce a more isotropic material than that of short fiber reinforced non-metallic materials, primarily due to the three- dimensional network formed by the long fibers developed during injection molding.
  • Another advantage of long-fiber material is the almost linear behavior through to fracture resulting in less deformation at higher stresses.
  • metals and metal alloys that can be used to form the metallic component include, without limitation, magnesium alloys, aluminum/aluminum alloys (e.g., 3000 series alloys, 5000 series alloys, 6000 series alloys, such as 6061-T6, and 7000 series alloys, such as 7075), titanium alloys (e.g., 3-2.5, 6-4, SP700, 15-3-3-3, 10-2-3, or other alpha/near alpha, alpha-beta, and beta/near beta titanium alloys), carbon steels (e.g., 1020 or 8620 carbon steel), stainless steels (e.g., 304, 410, 416 stainless steel), PH (precipitation- hardenable) alloys (e.g., 17-4, C450, or C455 alloys), copper alloys, and nickel alloys.
  • magnesium alloys e.g., aluminum/aluminum alloys (e.g., 3000 series alloys, 5000 series alloys, 6000 series alloys, such as 60
  • thermoplastic materials e.g., polyethylene, polypropylene, polystyrene, acrylic, PVC, ABS, polycarbonate, polyurethane, polyphenylene oxide (PPO), polyp henylene sulfide (PPS), polyether block amides, nylon, and engineered thermoplastics
  • thermosetting materials e.g., polyurethane, epoxy, and polyester
  • copolymers e.g., polyurethane, epoxy, and polyester
  • elastomers e.g., natural or synthetic rubber, EPDM, and compounds thereof.
  • the metallic material has Rockwell hardness value of at least 25, while a further embodiment has a Rockwell hardness value of at least 28, while an even further embodiment has a Rockwell hardness value of 30-40, thereby further promoting smooth operation of the interface and desired wear tendencies.

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  • Life Sciences & Earth Sciences (AREA)
  • Forests & Forestry (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Food-Manufacturing Devices (AREA)

Abstract

Trancheuse de produit ayant une plaque d'écartement réglable positionnée avec précision par mise en coopération unique d'une plaque à came et d'un galet de came.
PCT/US2017/015752 2016-02-12 2017-01-31 Trancheuse Ceased WO2017139129A1 (fr)

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CA3011544A CA3011544A1 (fr) 2016-02-12 2017-01-31 Trancheuse
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Applications Claiming Priority (4)

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US15/042,172 2016-02-12
US15/042,172 US20170232628A1 (en) 2016-02-12 2016-02-12 Product slicer
US15/042,179 US20170232629A1 (en) 2016-02-12 2016-02-12 Product slicer
US15/042,179 2016-02-12

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EP4082732A1 (fr) * 2021-04-26 2022-11-02 Illinois Tool Works, Inc. Trancheuse de produit alimentaire avec identification de la position de la plaque d'écartement
PL448534A1 (pl) * 2024-05-11 2025-11-17 Bydgoskie Zakłady Maszyn Gastronomicznych Ma-Ga Spółka Z Ograniczoną Odpowiedzialnością Krajalnica

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Publication number Priority date Publication date Assignee Title
EP4082732A1 (fr) * 2021-04-26 2022-11-02 Illinois Tool Works, Inc. Trancheuse de produit alimentaire avec identification de la position de la plaque d'écartement
PL448534A1 (pl) * 2024-05-11 2025-11-17 Bydgoskie Zakłady Maszyn Gastronomicznych Ma-Ga Spółka Z Ograniczoną Odpowiedzialnością Krajalnica

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EP3414064A4 (fr) 2019-10-09
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