Pendulum-type product slicing machine

A pendulum-type product slicing machine is provided wherein the product is carried on a support frame mounted for swinging movement in an arc with respect to a slicing blade. The slicing blade is an endless band which is supported in an inclined plane such that the lower end of the product carrier may traverse the lower run of the blade for complete severing of the product carried thereby. Mechanisms are provided for control of the thickness of the slices and for automatic operation of the carrier.

FIELD OF THE INVENTION 
This invention relates to apparatus for the slicing of products and, in 
particular, slicing of food products. It relates more specifically to an 
apparatus which is provided with a carrier for elongated food products 
adapted to swing on a pivot in the manner of a pendulum relative to an 
elongated, longitudinally movable slicing blade for severing a slice from 
the bottom end of the product during each stroke of the carrier. 
BACKGROUND OF THE INVENTION 
Various types of food product slicing machines have been devised and 
employed in the food industry to produce planar slices of the particular 
product. In general, these machines are of the type wherein a carrier is 
provided for the support and reciprocating or cyclic movement of a 
quantity of the food product relative to a slicing blade. Rotary-type 
blades are customarily used in these machines, although newer cutting 
mechanisms emply flexible band-type blades. An example of the flexible 
band-type blade and an apparatus which utilizes it for effecting slicing 
is the structure shown in U.S. Pat. No. 4,230,007 issued on Oct. 28, 1980 
to James E. Grote. This machine has a flexible blade which extends around 
a pair of pulleys or support wheels for support of a portion of the blade 
in a horizontal cutting plane. The food product which is in the form of a 
plurality of elongated sticks, pepperoni, for example, is carried in a 
turret in a vertically oriented manner for gravity feed and the turret is 
reciprocated across the continuously moving blade to sequentially sever 
thin slices of predetermined thickness from the bottom end of each of the 
several sticks. The slices, as they are severed, are deposited by gravity 
onto a moving receiver carried on a conveyor at substantially the same 
speed as the cutting rate. 
Another example of a band-type mechanism for the cutting of food products 
is that shown in U.S. Pat. No. 4,050,339 issued to Richard A. Soleri on 
Sept. 27, 1977. The food product carrier in the apparatus of this patent 
is of a carrousel type wherein a series of product carriers are revolved 
in a circular path and sequentially pass over the cutting portion of 
band-type blades for severing slices of predetermined thickness. The food 
product carriers frictionally grip the product to be cut by means of 
spring biased jaws that operate to permit incremental gravity feed. An 
apparatus of this type requires a large number of product carriers if any 
reasonably acceptable operating speed is to be obtained because of the 
full circle path of movement. Furthermore, an apparatus of this type 
requires a large amount of floor space. 
Still another example of a slicing apparatus is U.S. Pat. No. 3,667,522 
issued to David W. Bingham on June 6, 1972. The apparatus has a cutting 
blade which is movably mounted on a frame to oscillate along an arcuate 
path of travel in a horizontal plane beneath a plurality of fixed 
position, vertically extending food product chutes through which the 
product is gravity fed. The oscillating blade cuts slices from the lower 
ends of the food product which is contained in vertical guide tubes or 
chutes projecting upwardly with respect to the horizontal cutting plane in 
which the cutter blade oscillates. A disadvantage of an apparatus of this 
type is that suitable mechanisms to support an oscillating movement of a 
cutting blade in a precise cutting plane is difficult to construct and to 
maintain in proper adjustment. The blade support mechanisms are relatively 
heavy and their mass imposes additional stress on the apparatus as a 
consequence of the substantial forces required to effect oscillating 
movement. 
Machines of the above types require a large quantity of the food product to 
be supported in the product carriers. Further, in the case of the Grote 
patent, the turret is a relatively large, heavy device and the speed of 
the machine is, therefore, substantially inhibited and limited to a slow 
rate of reciprocating operation. Also, the machine shown in U.S. Pat. No. 
4,050,339, while being capable of high revolving speed for fast cutting 
operations, is not particularly suited for combining its operation with a 
conveyor used to transport receivers for the sliced food products as a 
consequence of its cutting speed resulting in problems of synchronization 
of its operation with a conveyor for receiving the slices. 
SUMMARY OF THE INVENTION 
In accordance with this invention, a pendulum type slicing apparatus is 
provided and includes a food product carrier mounted for swinging movement 
from one side to the other relative to slicing means having an elongated, 
horizontally, disposed blade. The food product carrier includes a rigid 
frame structure mounted on a horizontal pivot axis of a structural frame 
and is provided with means for reciprocating the carrier in an oscillatory 
manner. Incorporated in the carrier are a plurality of product receivers 
in the form of elongated tubes that are open at both the top and bottom. 
The product to be sliced, which product may be of an elongated stick form, 
is disposed in a tubular receiver through which it feeds by gravity toward 
a bottom end and from which it projects for slicing by the slicing 
mechanism. Cutting of the slices from the bottom end of the product sticks 
is effected by slicing means which includes a flexible, endless band blade 
having a portion of the blade mounted for movement transversely across the 
path of movement of the product carrier and the product carried thereby. 
In a preferred embodiment, the slicing means comprises an endless band 
blade carried by a pair of pulleys or support wheels for continuous 
revolution in a plane that is substantially vertically oriented, although 
it is slightly inclined to accommodate movement of the product carrier. 
The slicing means is also supported on the structural frame of the 
apparatus in a position where a bottom run of the band is at a relatively 
lowermost position and disposed in a substantially horizontal cutting 
plane adjacent which the product is caused to travel as a consequence of 
the oscillatory movement of the product carrier. With this structure, 
essentially all of the components are thus positioned above the cutting 
plane whereby the slices as they are severed from the product sticks may 
freely drop by gravity onto a receiver such as that which may be carried 
by a conveyor located below the operating blade and carrier components of 
the apparatus. 
Control of the thickness of the slices that are severed during each stroke 
of the product carrier is effected by a product support plate that is also 
mounted closely adjacent the horizontal cutting plane. This product 
support plate includes two sections with each section being disposed at 
opposite sides of the effective portion of the cutting blade. Thus, the 
product will be supported on one or both these plate sections throughout 
its oscillatory movement from one to the other side of the blade, thereby 
preventing the product stick from merely dropping out of the tubular 
receivers. A first section of the support plate structure is positioned in 
preceding relationship to the cutting edge of the blade and is primarily 
effective in controlling the thickness of the product slices. By 
appropriately adjusting the spaced relationship of the upper surface of 
this plate with respect to the cutting edge of the blade, it is possible 
to vary the relative vertical position of those components and thus vary 
the thickness of the slices that will be severed. Control mechanisms are 
mechanically coupled with this first support section to preferably enable 
adjustment of the plate as to angular relationship to the cutting plane as 
well as its vertical spacing to the bottom of the product carrier. 
Slicing means provided for use with the apparatus of this invention is 
advantageously of the type disclosed in U.S. Pat. No. 4,230,007 which was 
briefly discussed in the Background of the Invention. This structure is 
essentially that which is shown in the cited patent although in this 
combined mechanism, it is the bottom run of the blade that is utilized for 
the slicing function. Accordingly, a support and guide is positioned to 
cooperate with the lower run of the blade and thereby maintain that 
portion of the blade in a precisely located position to assure that the 
cutting edge will be maintained in the desired cutting plane for accurate 
slicing of the product in predetermined thickness as well as maintaining 
uniformity of thickness. As previously indicated, the flexible-band 
supporting wheels are positioned at an angle with respect to a vertical 
plane in much the same manner as disclosed in U.S. Pat. No. 4,230,007 with 
the upper run being inclined in a direction away from the region in which 
the product carrier oscillates. With this arrangement, when having the 
proper angle relationship of the blade, it is possible to accommodate the 
product carrier throughout its full extent of oscillation as it passes the 
cutting edge as is determined by the dimension of the product which is to 
be sliced. A particular advantage of the band blade in an apparatus of 
this type is that such apparatus is thus enabled to accommodate various 
sizes of product sticks or food product articles. By providing a band-type 
cutting blade of sufficient length to obtain a predetermined clear spacing 
between the blade supporting pulleys, it is readily possible from a 
practical standpoint to accommodate a large number of relatively small 
size product sticks or a comparatively smaller number of larger product 
sticks. By product sticks, it is intended to include those products which 
may comprise a number of smaller units that are merely positioned in 
stacked relationship in a respective tubular receiver of the product 
carrier and is not intended to be limited to only products such as food 
sticks including cheese and processed type meats. Also, a plurality of 
product receives having different cross-sectional areas for concurrently 
producing different sized product slices may be incorporated in a 
particular apparatus. 
To improve the performance of the apparatus, it is preferred that the 
product carrier include a pusher bar which accommodates the variations in 
spacing between the bottom end of the carrier receptacles and the top 
surface of the thickness determining support plate. This bar is mounted on 
the apparatus to also swing in the manner of a pendulum to cooperate in 
movement with the product carrier during its oscillatory excursions in 
traversing the cutting blade and, as a consequence of such movement, to 
also vertically oscillate with respect to the carrier. Providing of a 
pusher bar capable of functioning in this manner not only provides a stop 
plate carried at the trailing side of the product carrier receptacles 
during a forward or cutting stroke for back up support for that portion of 
the product projecting downwardly out of the receptacle, it also assures 
that the end pieces that will ultimately develop from slicing of an 
elongated product stick will not be ejected rearwardly from the carrier 
and over the support plate as a consequence of the resistance encountered 
from the slicing means blade. 
Drive means is also provided for causing revolution of the band-type blade 
of the slicing mechanism and the oscillatory movement of the product 
carrier. This drive means in the preferred embodiment comprises a 
hydraulic system including an electrically driven hydraulic fluid pump 
that provides the necessary pressurized fluid for operation of a fluid 
motor driving the carrier and an electric motor is provided for revolving 
the flexible blade of the slicing mechanism. A hydraulic ram comprising a 
cylinder and piston unit may be advantageously used to effect the 
oscillatory, swinging movement of the product carrier. As to this 
hydraulic ram, the cylinder may be mounted on the structural frame of the 
apparatus with the piston connected by means of a piston rod and suitable 
mechanical connections to the product carrier. Appropriate timing 
mechanisms may also be incorporated in the total control system to obtain 
oscillation of the product carrier in predetermined relationship to an 
underlying conveyor which may be transporting receivers for the food 
product slices and located beneath the operating mechanism. Alternative 
operation of the apparatus may be the continuous type slicing for 
producing a stack of sliced product suitable for packaging. 
The product slicing apparatus of this invention is not only capable of 
readily performing the slicing operations to produce an accurately 
controlled thickness slice at a fast operating rate, but it is also an 
extremely safe operating mechanism. The structure is arranged with the 
components located relative to each other in a manner whereby the 
relatively dangerous operating components may be easily covered by screens 
and protective covers. An operator is not unduly exposed to the moving 
components through the use of such protective covers and screens, but the 
operator may easily resupply the product carrier with additional product 
as may be necessary during the course of operation. 
These and other objects and advantages of this invention will be readily 
apparent from the following description of an illustrative embodiment 
thereof. Reference will also be made to the accompanying drawings which 
illustrate a preferred embodiment of the invention.

DESCRIPTION OF THE ILLUSTRATIVE EMBODIMENTS 
Having reference to the drawings, it will be seen that a pendulum type 
slicing apparatus embodying this invention is illustrated in its entirety 
in FIG. 1 which is a perspective view of such a machine. This illustrative 
embodiment is of a type which is particularly adapted for utilization with 
a conveyor for transporting of receivers for sliced food products. 
Basically, the structure comprises a structural frame 10 and a slicing 
head 11 with the frame constructed to enable positioning of the slicing 
head over a conveyor. Although the structure could be fabricated as a 
fixed installation, this particular illustrative embodiment is designed 
for portability and movement from one position to another, either with 
respect to a single conveying system indicated in broken lines at 12 or 
utilized with a fixed station type operation. Included in the structural 
frame 10 is a base frame 13 and an upstanding frame housing 14 which is 
positioned adjacent to one end of the base frame. Carried by the frame 
housing 14 is a slicing head 11 which is attached to that housing at an 
upper end thereof and is suspended in a cantilever fashion with respect to 
the frame housing so as to overlie the horizontal portion of the base 
frame 13. This arrangement of components is particularly advantageous as 
it greatly facilitates the portability of the apparatus for positioning at 
a desired point with respect to a conveying system 12 as is illustrated in 
FIG. 1. 
Included in the base frame 13 are a pair of elongated beams 15 disposed in 
spaced parallel relationship and interconnection at their opposite ends by 
respective transverse beams 16. Portability of the apparatus is provided 
by means of a set of four castered wheels 17 which are bolted to the 
transverse beam 16 as can also be seen in FIGS. 2-5. Stability of the 
apparatus, when positioned in a desired operating position, is achieved 
through a set of four vertically adjustable feet 18. Each foot 18 includes 
an elongated threaded shaft 19 carrying a base plate 20 at its lower end. 
The upwardly extending portion of the shaft 19 is threaded through an 
attachment block 21 for each respective foot that is secured to the side 
of the elongated beams 15 adjacent their extreme end portions. Operation 
of the vertically adjustable feet 18 is readily apparent in that with the 
machine positioned at a desired point, the threaded shafts 19 are turned 
to cause the base plates 20 to lower and contactingly engage a supporting 
surface such as a floor. Once the shaft is threaded to a position whereby 
the frame may be slightly elevated to remove at least a portion of the 
weight from the castered wheels 17, a lock nut 22 is then turned on the 
shaft to contactingly engage a surface of the attachment block 21 and thus 
secure the shaft in fixed position in its block. The adjustable feet 18 
also provide a means for leveling of the apparatus. 
The frame housing 14 projecting upwardly from the one end of the base frame 
includes a pair of uprights 23 which may be advantageously formed from 
elongated C-shaped channels and thus provide the necessary structural 
rigidity and support for the other components, particularly the slicing 
head 11. Referring to FIG. 5, it will be seen that the upper end of the 
structure is closed by a panel 24 for purposes of both safety and 
appearance. The particular illustrated embodiment of the apparatus is 
designed to be powered by a hydraulic system and includes a hydraulic pump 
which is driven by an electric motor 25. A reservoir 25A for the hydraulic 
fluid is shown and is mounted in the base portion of the frame housing, 
but other associated components such as the hydraulic pump and its control 
valves, are not illustrated as such elements and their function are 
well-known to those familiar with this particular art. Also carried on the 
frame housing 14 are control and operating panels 26 and 27 for both the 
hydraulic and electrically operated components with it being understood 
that some of the hydraulic controls may be electrically actuated. 
As previously indicated, secured to and carried by the frame housing 14 at 
its upper end in a cantilevered manner is the slicing head 11. This 
slicing head 11, as shown in FIG. 1, is provided with protective covers 
and guards for operational safety with these covers and guards being 
removable to facilitate cleaning and maintenance. As seen in FIG. 1, these 
covers and guards include an end cover 28 which provides protection as to 
the slicing mechanism to be described in further detail, front guard 29, 
rear cover 30 and top cover panel 31. The top cover panel 31 closes the 
upper end of the frame housing to prevent objects from inadvertently 
entering that frame housing and perhaps engaging with the slicing 
mechanism. The end cover 28 is a closed panel housing which is secured to 
an internal structural frame of the slicing head and thus provides 
complete coverage as to the sides, top, bottom and end areas with respect 
to that portion of the slicing head. The front guard 29 may be of a screen 
or bar-grid type as is illustrated which provides adequate protection, but 
enables the operator to visually observe functioning of the various 
components in the center of the slicing head. The rear cover is also a 
closed panel housing for optimum protection. 
Construction and arrangement of the various components forming the slicing 
head 11 are best seen in the enlarged figures of the drawings, and in 
particular, FIGS. 2-8. The various covers and guards have been omitted 
from the slicing head and associated portions of the apparatus to 
facilitate illustration of these components. Included in the slicing head 
is a primary structural frame 35 which includes a pair of elongated beams 
36 extending horizontally and vertically disposed above the elongated 
beams 15. Attached to the outermost ends of each of the elongated beams 36 
is a respective one of a pair of vertical struts 37 with those struts 
being interconnected at their lowermost ends by a transverse beam 38. 
Marginal end portions of the elongated beams 36 extend across the inwardly 
facing surfaces of the uprights 23 and are securely bolted thereto. 
Accordingly, the structural frame 35 of the slicing head will be seen as 
suspended in a cantilever manner with respect to the frame housing. 
Mounted on the primary structural frame 35 of the slicing head is the 
product carrier 40 and slicing means 41. As previously noted, the slicing 
means incorporated in this apparatus is preferably of the type shown in 
U.S. Pat. No. 4,230,007 issued Oct. 28, 1980 to J. E. Grote. This slicing 
means 41 includes an endless, flexible-band blade 42, a pair of blade 
supporting wheels 43, respective wheel supporting brackets 44 and 45 and a 
mounting beam 46. The slicing means is thus seen as comprising an 
elongated assembly which is positioned horizontally on the primary 
structural frame 35 of the slicing head to extend longitudinally thereof 
with one of the wheels and its associated supporting bracket 45 being 
substantially enclosed within the uprights 23 of the frame housing 14. The 
other blade supporting wheel and its associated bracket 44 are thus 
disposed in outwardly extending relationship to the vertical struts 37, 
but are normally protected and enclosed by the end cover 28. A guide and 
support 47 are provided for the lower run of the blade 42 in substantially 
the same manner as shown in association with the upper run in the cited 
Grote patent. One further difference between the apparatus shown in the 
referenced patent and the slicing means as incorporated in the present 
apparatus is that the blade in the present apparatus is mounted in an 
inverted manner to position the beveled edge in proper relationship for 
enabling the bottom run to cut from the bottom of a food product. 
This guide and support 47, as is fully described in the cited Grote patent, 
includes an elongated slot which receives the major portion of the blade 
and provides a back support at one longitudinal edge of the blade while 
the beveled cutting edge projects a slight distance outwardly of the slot. 
The side walls of the slot provide support and rigidity to the blade to 
prevent its oscillation or movement, thereby enhancing its ability to 
remain in a fixed position at a desired cutting line or cutting plane. 
Providing of the guide and support better assures that a uniform thickness 
slice is consistently obtained through the cutting operation. 
It will also be noted that the slicing means 41 includes means for tension 
adjustment in the form of a horizontally slidable, adjustment support 48 
that is incorporated in the outboard wheel supporting bracket 44. A 
screw-threaded adjusting rod and hand wheel 49 is provided in mechanically 
coupled relationship to the adjustment support 48 to effect the desired 
tension adjustment. Mounting of the slicing means is effected through 
positioning of the mounting beam 46 on the transverse beam 38 at the 
outboard end of the slicing head and a similar transverse beam 38a which 
extends between the uprights 23 adjacent a vertical edge of those 
uprights. Additional rigidity for the slicing means is provided by an 
upper frame element 50 which extends between and interconnects with the 
wheel supporting brackets 44 and 45. 
Revolution of the blade 42 is effected by an electric motor 51. The 
electric motor, as can be best seen in FIGS. 3 and 4, is positioned to 
extend through the rear upright 23 to which it is mechanically mounted and 
is disposed in perpendicular relationship to the slicing means 41. A shaft 
of the electric motor is mechanically coupled with the axle of the 
respective blade supporting wheel 43. Operating control of the electric 
motor is effected through switches and control mechanisms incorporated in 
the control and operating panel 26 and 27. It will be understood that 
although an electric motor is described as being provided for driving of 
the blade 42, other drive mechanisms may be alternatively provided. For 
example, a hydraulic motor may be substituted for the electric motor and 
utilize the hydraulic system provided for operation of other components of 
the apparatus with due regard to the system capacity. A hydraulic system 
would be provided in that case to adequately power all components. 
Forming the product carrier 40 is a structurally rigid swing frame 55 and a 
pair of elongated product receivers 56. The swing frame 55 comprises a 
pair of spaced apart and vertically extending end plates 57 which are 
interconnected at both front and rear by a plurality of vertically spaced 
cross bars 58. Thus, it will be seen that the end plates 57 and cross bars 
58 cooperatively define a box shaped structure which is open at both the 
top and bottom ends. If desired, side panels could also be provided for 
forming a substantially closed structure, however, in the illustrative 
embodiment, the space at the front and back of the frame is essentially 
open. The product receivers 56 are positioned and supported in fixed 
relationship within the interior space defined by the end plates 57 and 
the cross bars 58 and their construction and configuration will be 
described in further detail. 
In accordance with this invention, the product carrier 40 is mounted for 
swinging movement in the manner of a pendulum for carrying the products 
supported therein into slicing relationship with the blade of the slicing 
means 41. This swing mounting of the product carrier is obtained through 
securing of the upper end portions of the end plates 57 to the primary 
structural frame 35 by means of mounting bearings 59. A pair of mounting 
bearings 59 are provided with each being carried by a transverse support 
bar 60 which extends between and is rigidly secured at its opposite ends 
to the elongated beams 36. These support bars 60 being rigidly 
interconnected with those beams also serve to enhance the structural 
rigidity of that frame 35. The particular mounting bearings 59 illustrated 
in the drawings comprise a mounting plate 61 adapted to be bolted to the 
outer surface of the support bar and having a trunnion 62 extending 
through the support bar and into a bearing journal formed in each 
respective end plate. It will also be noted that the bearing axis for the 
product carrier is located vertically above the cutting edge of the blade 
42 resulting in the center of the carrier being at the blade's cutting 
edge when the carrier is vertically disposed. 
Since the end plates 57 and product receivers must have a predetermined 
width so as to accommodate the food products to be sliced, it will be seen 
that the frame must be capable of swinging through an arc which is of 
sufficient extent to permit complete cutting across the end face of the 
product that may be carried in the respective receivers 56 with that end 
face extending both forwardly and rearwardly with respect to the carrier's 
center. Referring to FIG. 3, it will be seen that this movement is 
accommodated by positioning the cutting blade on its supporting structure 
so as to revolve in a plane which is inclined at an angle of the order of 
20 degrees with respect to a vertical plane for a machine of the 
illustrative proportional dimensions. Providing blade supporting wheels 43 
of a diameter as is proportionally illustrated will result in spacing the 
upper and lower runs of the blade such that in cooperation with the angled 
disposition, the frame 55 is enabled to swing through the necessary arc. 
As a specific illustration, in a machine having a two foot swing radius 
from the trunnions 62 to the blade edge, providing blade support wheels 43 
of 12 inch diameter will enable the machine to accommodate a five inch 
diameter or thick food product. 
Cyclic reciprocation of the product carrier 40 in this embodiment is 
effected by a hydraulic fluid operated ram 65 as can be best seen in FIGS. 
2, 3 and 4. This ram comprises a cylinder 66 and an internal piston 
connected with an outwardly projecting piston rod 67. The cylinder 66 is 
supported on the primary structural frame 35 of the slicing head by a pair 
of mounting bars 68. These mounting bars 68 extend in a downward direction 
from their point of attachment to the upper rear elongated beam 36 to a 
point of termination in secured relationship to the upper frame element 50 
of the slicing means. These bars thus not only provide the mounting 
support for the ram 65, but also aid in enhancing the structural rigidity 
of the slicing head frame. Specific mounting of the cylinder 66 is by a 
pair of trunnions 69 carried at a forward end of the cylinder housing and 
projecting laterally outward into bearing journals formed in each of the 
respective bars. Mechanical coupling of the piston rod 66 to the product 
carrier is effected by a pivot coupling 70. This pivot coupling is secured 
to the end plates 57 by means of cross bars 70a secured to the swing frame 
end plates 57. Fluid coupling of the cylinder 66 to the hydraulic system 
is effected by means of flexible hoses. These hoses are not fully shown or 
described in any substantial detail as such fluid connections are 
well-known. Cyclic operation of the hydraulic ram is effected through the 
hydraulic fluid control system which also includes control elements 
mounted on the respective control and operating panels 26 and 27. 
In this illustrative embodiment of the apparatus as can be best seen in 
FIGS. 2, 4, 7, 8 and 9, a pair of product receivers 56 are shown 
positioned in the swing frame 55. Each of these receivers comprises an 
elongated tube that may be formed from sheet metal or other suitable 
material, plastic for example, and has a cross-sectional configuration 
designed to cooperate with a particular product. These tubes are open at 
both the top and the bottom and the product is fed into the receivers 
through the top end. By gravity, the food product then moves downwardly 
through the respective receiver to exit at the lower end under control of 
a slice thickness determining mechanism to be described hereinafter. Each 
of the illustrative product receivers 56 is formed in two channel shaped 
sections 71, 72, respectively, that are independently supported on the 
swing frame 55 to define an elongated tube for containing the product. 
Securing of the receivers in fixed relationship on the swing frame and at 
a desired vertical or transverse position is effected by means of clamping 
devices 73 or attachment mechanism 74 that are described hereinafter in 
further detail. It will suffice at this point to note that the receivers 
are of a design construction to be selectively positioned transversely 
across the swing frame to a desired position for placing the severed food 
product slices on the conveyor or slice receiver at a desired point. Also, 
the two-channel tube construction enables the cross-sectional area to be 
varied to a certain degree thereby enabling the tube to accommodate 
different sized food products as well as to be adjusted to best perform 
with a particular size food product. Vertical adjustment is provided to 
enable the bottom end of each tube to be properly positioned with respect 
to the cutting blade 42. 
Control of the thickness of the slices that are severed from the food 
product is effected by a support plate structure 75 which can be best seen 
by reference to FIGS. 2, 3, 7 and 8. This support plate structure includes 
a thickness control plate 76 disposed in preceding relationship to the 
lower run of the blade 42 and a limiting plate 77 disposed in trailing 
relationship to the blade. The limiting plate 77, as can best seen in FIG. 
3, has the sole function of preventing further downward displacement of 
the food product carried in the respective receivers 56 during the time 
that the swing frame 55 is swung in a counterclockwise direction to its 
maximum extent such as at the end of a cutting stroke and prior to a 
return stroke. The thickness control plate, however, has an important 
function other than supporting the food product within the respective 
receivers during such times as the swing frame 55 is swung in a 
counterclockwise direction as seen in FIG. 3 such as to the extreme right 
thereof and defined as an initial or start position. This additional 
important function of the control plate 76 is to provide a convenient 
means of enabling the operator to obtain a predetermined slice thickness 
and to selectively adjust the mechanisms to obtain different thicknesses 
as may be required for particular food products of their use. Accordingly, 
the thickness control plate 76 is pivotally mounted so as to be angularly 
positioned with respect to the cutting plane defined by the cutting blade 
42 and this cutting plane is essentially oriented parallel to a horizontal 
plane. 
The plate extends entirely across the effective cutting path and has a 
width sufficient to accommodate the full width of the swing frame and the 
product receivers and thereby fully support the food product carried 
thereby. Secured to each of the opposite ends of the control plate are 
respective trunnions 78 which project a distance outwardly and are 
disposed in respective bearing blocks 79. In a preferred embodiment of the 
apparatus, each of the bearing blocks 79 is connected to an adjustment 
block 80 that is affixed to a respective one of the transverse beams 38 
and 38a. Each of the adjustment blocks 80 is provided with slotted 
apertures for the attachment bolts 81 to permit longitudinal adjustment 
with respect to those transverse beams. This adjustment provides a means 
for controlling the spacing between a transverse edge of the thickness 
control plate with respect to the cutting edge of the blade 42. Vertical 
adjustment is also provided by means of a bolt and slot-type 
interconnection 82 whereby the bearing blocks 79 may be vertically 
adjusted with respect to those transverse beams 38 and 38a. Angular 
adjustment of the control plate 76 is effected by a lever arm 83 secured 
in fixed relationship to the control plate at one end thereof, such as 
adjacent the uprights 23, and a length adjusting mechanism 84. The length 
adjusting mechanism includes an elongated rod 85 having one end thereof 
pivotally interconnected with the upper end of the lever arm 83 by a pivot 
pin 86. The opposite end of the rod 85 extends through or into a mounting 
block 87 terminating in a screw-threaded end portion 88 that extends 
axially out the opposite end of the block. A knurled nut 89 is threaded 
onto the end portion 88 and, through rotation thereof, will enable a 
relative length adjustment as to the rod and consequently the angular 
position of the thickness control plate. The mounting block 87 may be 
affixed to the vertical flange of the upright 23 and a rod clamping 
mechanism is also advantageously provided. This rod clamping mechanism 
includes a clamping pin 90 extending through the mounting block 87 
transversely with respect to the rod 85 and having the rod extend 
therethrough. An end of the clamping pin projects through the flange of 
the upright 23 and has a clamping lever arm 91 threaded onto the end 
thereof. Maintenance of the angular position of the thickness control 
plate 76 set by means of the rod 85 and knurled nut 89 can be assured 
through operation of the clamping pin and its associated arm. 
Having specific reference to FIG. 3, it will be clearly seen that with the 
product carrier 40 mounted for swinging movement that this results in a 
bottom edge of the food product traversing an arcuate path as it passes 
the cutting blade 42. Since it is desired that the product be severed into 
thin planar slices, it will be further apparent that the product, as it 
moves down through the respective receivers carried on the swing frame, 
will project a distance below the bottom edge of that swing frame in order 
that it may be presented for slicing by the blade 42. This movement, 
particularly with respect to the thickness control plate 76, results in 
the front edge or side of the swing frame becoming relatively more 
elevated with respect to a horizontal plane than the rear side. As a 
consequence, there may be a relatively larger gap or spacing between the 
bottom of the product receivers 56 and the upper surface of the control 
plate 76. At its furtherest extent of swinging movement in a 
counterclockwise direction as viewed in FIG. 3, that is at a point of 
initiation of a slicing stroke, there is a greater possibility that the 
cutting forces that will be generated may extrude or tend to extrude the 
product through that gap at this particular point in travel. 
In accordance with this invention, to minimize that problem presented by 
the gap, a pusher assembly 95 is provided to reduce the effect of that 
space or gap. The pusher assembly 95 includes an elongated pusher bar 96 
which is supported to extend transversely across the front of the swing 
frame 55 at its lowermost end. Supporting the pusher bar 96 are a pair of 
vertically extending rods 97 having their lowermost ends mechanically 
secured to the pusher bar. There are two such rods 97 which are disposed 
at respective opposite sides of the swing frame in substantial alignment 
with the front edge surfaces of the end plates 57. Each of the rods 97 
extends upwardly and is secured to a pivot 98 carried by the respective 
support bar 60. Respective guide blocks 99 are provided for maintaining 
each of the rods 97 in predetermined relationship to the respective end 
plate and to thereby effectively cause the pusher bar 96 to be held in 
close, adjacently disposed relationship to the front edge surfaces of 
those end plates. Each of the guide blocks 99 is provided with a guide 
surface through which the rod extends and may be axially reciprocated. 
Also, each of the guide blocks 99 is mounted on a respective end plate 57 
by a pivot bolt 100 to permit these blocks to oscillate to a limited 
degree and thereby accommodate differences in relative movement as between 
the rods and the end plates. 
With the pivots 98 for the pusher bar support rods 97 located as 
illustrated in FIG. 3 and as can also be seen in FIGS. 7 and 8, it will be 
noted that the swing frame 55 and the pusher bar 96 will oscillate through 
respective arcs as determined by their respective axes of revolution. 
Since the two axes of revolution are horizontally displaced, it will be 
readily apparent that these two arcs do not coincide and actually would 
intersect during the course of movement between extreme displacement 
positions of the swing frame. When the swing frame is displaced to its 
fullest extent in a counterclockwise direction as seen in FIG. 3, it will 
be at a relatively higher elevation than will be the pusher bar 96. 
Consequently, the pusher bar will, in effect, form a downward extension of 
the product receivers 56. As the swing frame moves in a clockwise 
direction, the pusher bar will progressively elevate with respect to the 
swing frame while the swing frame is moving in a downward portion of its 
arc of movement. This results in an automatic interchange of function with 
the pusher bar becoming ineffective as it approaches the cutting blade 42. 
However, during this portion of movement, the need for the pusher bar 
decreases. 
Operation of the slicing apparatus of this invention is diagrammatically 
illustrated in a sequential manner in FIGS. 10A-D. These figures are side 
elevational views to illustrate the functional relationships between the 
product carrier 40 and its swing frame 55 and the support plate structure 
75 and the blade 42 with its associated guide and support 47. In these 
diagrammatic figures, it is assumed that the thickness control plate 76 is 
disposed at a desired predetermined angle, vertical elevation and 
horizontal position with respect to the cutting blade to produce the 
desired thickness of slice. Referring first to FIG. 10A, it will be seen 
that the product carrier 40 has been displaced counterclockwise to its 
extreme forward position and that the stick of the food product to be 
sliced, indicated at P, is extending downwardly from the respective 
receiver 56 and is resting on the thickness control plate 76. At this 
point, it will also be noted that the pusher bar 96 is at its relatively 
furtherest downward position with respect to the receivers and is 
effectively closing the space between the bottom of the receivers and the 
upper surface of the thickness control plate. 
In FIG. 10B, it will be seen that the product carrier 40 has moved 
clockwise to a position wherein the leading edge or side of the stick of 
food product P has been brought into operative engagement with the cutting 
edge of the blade 42. Movement of the product carrier to this position 
will illustrate the operation of the pusher bar 96 in following the 
receptacles or receivers 56 and maintaining a minimum gap or space through 
which the food product could possibly be caused to extrude as a 
consequence of the slicing forces produced by the blade. FIG. 10C 
illustrates another point in the slicing operation with the swing frame 55 
and its product receives 56 further displaced along its arc of movement 
although the slice has not been completely severed. At this point, it will 
be seen that the pusher bar 96 is now moving relatively upward with 
respect to the product receivers 56. As the swing frame moves to its 
furtherest extent in a clockwise direction as shown in FIG. 10D, the 
cutting blade will have moved completely through the product P thereby 
severing the slice which then drops by gravity to a suitable receiver such 
as a conveyor or container while the food product P is maintained in its 
position in the receiver 56 by the limiting plate 77. Also, at this point, 
the pusher bar 96 as a consequence of its different location for axes of 
revolution, will have been displaced a sufficient distance upwardly to 
avoid any interference or contact with the cutting blade 42. Upon 
conclusion of the cutting or slicing operation, the apparatus will 
function to effect a reversal in the swinging movement of the swing frame 
55 resulting in the frame moving in a counterclockwise direction with the 
receiver and pusher bar moving relatively oppositely with respect to a 
vertical direction to the initial starting position as shown in FIG. 10A. 
A modified pusher assembly 105 is shown in FIGS. 12A-C and 13. This 
modified assembly is designed to better assure that a pusher bar 106 will 
be maintained in close association with the upper surface of the thickness 
control plate. Only a fragmentary portion of the modified assembly 105 is 
shown in these figures with FIG. 13 showing only an end portion of the 
pusher bar 106. This assembly, in addition to the pusher bar 106, includes 
vertically extending support rods 107 with one rod secured at a respective 
end of the pusher bar and extending upwardly therefrom for pivotable 
mounting of the upper end on the respective support bars 60. 
Attachment of the lower end of each rod 107 to the pusher bar 106 is 
effected by a mechanism which permits vertical reciprocating movement of 
the bar on the rods. The objective of this method of attachment is to 
better enable the pusher bar to accommodate a larger variation in vertical 
height relative to the product receivers and thus enable the apparatus to 
accommodate larger cross-sectional shapes of food products. The specific 
construction comprises forming of a socket 110 in the pusher bar and 
opening upwardly to receive a lower marginal end portion of the respective 
rod 107. A helical compression spring 111 is coaxially disposed on the rod 
having one end thereof disposed in abutting relationship to the upper 
surface of the pusher bar and the opposite end restrained against a stop 
collar 112. This collar is fixed on the rod in predetermined relationship 
to the pusher bar to result in obtaining the desired spring force for 
operation of the assembly in the desired manner. A bolt 113 is threaded 
axially into the lower end of the respective rod 107 and projects through 
an aperture 114 in an upward direction through the pusher bar. The head of 
the bolt operates against a surface 106a formed on the bottom of the 
pusher bar and which is displaced upwardly with respect to the bottom edge 
106b of the bar so as to avoid interference with either the thickness 
control plate or other materials during the course of operation. The lower 
marginal end portion of the rod 107 extends into the upwardly opening 
socket 110 that is of a sufficient depth to permit a predetermined minimum 
relative axial reciprocation of the rod in the socket. This mechanism thus 
enables the pusher bar to oscillate on the lower end portion of the 
supporting rods as the bottom edge 106b thereof may be brought into 
engagement with the upper surface of the thickness control plate 76 and to 
thereby assure that there will be no gap or space through which the food 
product may be extruded through operation of the blade in a severing 
operation. 
Functional operation of the modified pusher assembly 105 is 
diagrammatically illustrated in the sequential views of FIGS. 12A-C. These 
three figures show in sequence the movement of the pusher bar 106 as it 
follows the arcuate swinging of the product carrier. FIGS. 12A and 12B 
show how the pusher bar maintains the bottom horizontal edge thereof in 
contacting engagement with the upper surface of the thickness control 
plate for a substantial amount of the arcuate movement of the assembly 
during a severing operation. When in the position of FIG. 12A, the pusher 
bar 106 will be displaced relatively upward on the rods 107 resulting in 
compression of the springs 111 as is indicated in broken lines in FIG. 13 
as a consequence of the bottom edge 106b engaging the thickness control 
plate 76. As the mechanism swings to the position shown in FIG. 12B, the 
springs 111 will assure that the pusher bar 106 is maintained in 
engagement with the thickness control plate. FIG. 12C illustrates the 
upward movement of the pusher bar as it approaches its furtherest extent 
of swinging in a clockwise direction as the head of the bolts 113 engage 
the bar surface 106a preventing further downward displacement of the bar 
on the rods and thus avoids contacting interference with the cutting blade 
42 by the pusher bar. 
Product receivers 56 of an elongated tubular construction are illustrated 
in the disclosed embodiments of the invention and are deemed convenient 
devices for holding and supporting of the food products for automatic 
feeding and in accomplishment of the severing or slicing operation. The 
tubular construction provides for a gravity feed and also greatly 
facilitates continuity of feeding of the product since additional product 
may be sequentially fed in through the top open ends of those tubes. In 
considering the proportional relationships of the components, it will also 
be noted that the upper end portions of the tubes do not project an 
extreme distance above the top of the machine and thus their oscillatory 
movement is of a more limited scope. Consequently, it is possible for the 
operator to continue feeding of the food product into the receivers while 
the machine remains in operation. 
Referring specifically to the drawings, it will be noted that the machine 
illustrated therein is provided with two of these tubular product 
receivers. It will be understood that the number of such receivers may be 
increased or decreased in accordance with the particular products being 
sliced and the operational requirements of a particular installation of 
the machine. It will also be noted that the tubular receivers may be 
displaced to the left or right as viewed in FIG. 2 to either accommodate 
additional product receivers or to place a particular receiver in a 
specific position as determined most advantageous with respect to a 
receiver that may be transported on the underlying conveyor system. 
The particular structure and construction incorporated in the illustrative 
product receivers 56 as previously described comprises a pair of 
tube-forming plates with these plates being designated by the numerals 71 
with respect to the receiver shown at the right side of FIGS. 2 and 9 and 
72 with respect to the receiver shown at the left side of those two 
drawing figures. These two sets or pairs of plates 71 and 72 are 
configured to essentially define an area which roughly approximates the 
cross-sectional configuration of the food product to be fed through the 
machine. As illustrated in FIG. 9, the pairs of plates 71 thus roughly 
define a circular cross-sectional area and are particularly adapted for 
use with an elongated stick-type of food product which also has a 
generally circular cross-sectional configuration. While pairs of plates of 
this type are illustrated, it will be readily apparent that the 
configuration of those channel-shaped plates may be modified or altered to 
other configurations or adaptable to a different type of food product 
having a cross-section other than generally circular. The particular 
configuration and shapes of the plates for such purpose will be readily 
apparent to those familiar with the food product field. A particular 
advantage of the dual channel-shape plate construction for the product 
receivers is that a single set of such plates can be positioned to provide 
a greater or lesser spacing therebetween and thus result in capability to 
accommodate further variations in the food products that may be desired to 
be processed through the machine. This difference in the spacing of the 
pairs of plates is illustrated as between the plates 71 and the plates 72. 
A further difference in configuration to also illustrate the adaptability 
of product receivers of this type to different food products is that the 
plates 72 are of a configuration to define a cross-sectional area of a 
more oval shape. 
Mounting of the receivers on the swing frame 55 was generally indicated to 
be by means of the cross bars 58. These cross bars are provided in pairs 
with two being located at the bottom ends of the end plates 57 and two 
being located at the upper ends thereof. FIGS. 7 and 8 also aid in showing 
the mounting and support of these product receivers. Each of the bars 58 
is also shown as having an elongated horizontal slot 58a formed therein 
which, as can be seen by reference to the drawing figures, is intended to 
provide a more universal mounting and ability to cooperate with different 
configured product receivers. Referring to the product receiver shown at 
the right side of FIGS. 2 and 9, each of the channel-shape plates 71 is 
secured at its upper and lower ends to the respective cross bar 58 by 
clamping devices 73 that are designed to enable horizontal displacement of 
the plates supported thereon as well as to permit vertical displacement of 
that plate. Such a clamping device comprises a threaded bolt 120 which 
extends through the longitudinally extending slot 58a of the respective 
support bar. A stop nut 121 is threaded onto the bolt to be positioned at 
the inwardly facing side of the bar 58 and a locking nut 122 is threaded 
onto the bolt at the outwardly facing side of the bar. Thus, these two 
nuts 121 and 122 serve to secure the bolt at a desired position on the bar 
and, through appropriate adjustment, can axially position the bolt with 
respect to that bar. This axial positioning thus enables the plates 71 to 
be displaced toward or from each other. An inner end of the bolt 120 is 
provided with a head 123 which is adapted to interfit in a T-shaped 
channel 124 formed on an exterior surface of the respective plate 71. A 
locking nut 125 is also threaded onto the bolt 120 at a position to be 
turned and clamp flanges of the T-shaped channel 124 between the bolt head 
123 and the locking nut 125. Operation of the bolt head and its locking 
nut can thus enable the plate 71 to be displaced vertically with respect 
to its support on the bars 58. 
The plates 72 for the left side product receiver are supported on the 
respective bars 58 by attachment mechanisms 74 as previously described in 
general terms. The illustrative attachment mechanism 74 includes a carrier 
frame 126 having a central opening through which the plates 72 vertically 
extend. Each of the plates 72 is secured to this carrier frame 126 and in 
this illustrative embodiment, they are shown as being fixed and not 
capable of vertical adjustment. However, it will be understood that these 
plates may also be mounted on the carrier frame in a manner similar to 
that described with respect to the plates 71 to permit vertical 
displacement. The carrier frame 126 is provided at both the front and rear 
thereof with flanges 127 which are of a length to project a distance 
downwardly in overlapping relationship to the respective surfaces of the 
supporting bars 58. A locking bolt 128 is threaded into a socket in each 
of the flanges 127 and is of a length to engage a surface of a respective 
support bar 58 and function to provide a compression clamp. This 
particular attachment mechanism thus is readily positionable as a unit 
horizontally along the support bars. 
Operating control of the product carrier 40 to effect its reciprocating 
swinging movement was generally indicated to be by means of a hydraulic 
system. That system was indicated to include a hydraulic fluid pump driven 
by an electric motor 25 and associated with a hydraulic fluid reservoir 
25a. A control system was provided and included the electrical control 
elements mounted in a panel 27 and hydraulic control devices included in a 
second control panel 26. These control devices indicated as hydraulic 
fluid control valves 130, 131 and 132 provide a means for the operator to 
adjust the movement of the product carrier 40 such as its length of stroke 
and its rate of movement. Automatic control of the product carrier is 
provided in this embodiment of the apparatus by a cam controlled hydraulic 
valve 133. This cam control valve 133, as can be best seen in FIG. 6, is 
mounted on the frame in a fixed position and is provided with a 
reciprocative actuator 134. Operation of the actuator 134 is effected by a 
cam 135 which is mounted on one of the end plates 57 of the product 
carrier. This cam 135 is formed with a cam surface 136 which is shaped to 
cause reciprocation of the actuator 134 in accordance with the arcuate 
position of the product carrier. This cam surface is shaped in a manner 
whereby the valve 133 will be operated to effect a change in the direction 
of movement of the product carrier through routing of the hydraulic fluid 
with respect to the hydraulic ram 65 that operates the product carrier. 
The preceding description relative to the actuating mechanisms for the 
swing frame 55 was directed to a hydraulic operated ram. The specific 
actuating mechanism for the swing frame may comprise other mechanisms and 
to illustrate such variations, reference will be had to FIG. 11 which 
illustrates a mechanical crank-type mechanism 140. This mechanical 
crank-type mechanism includes a crank shaft 141 which can be journalled on 
the mounting bars 68 and thus supported in substantially the same manner 
as the previously described hydraulic ram cylinder. However, in this 
instance, the crank shaft would be journalled in suitable bearings in 
those bars to accommodate the continuous rotating motion. Interconnecting 
the crank shaft with the swing frame is a connecting rod 142 which is also 
pivotally connected by a pivot coupling 143 to the cross bar 70a. Rotation 
of the crank shaft 141 may be conveniently effected by means of a 
hydraulic motor 144. This motor 144 may be mounted on one of the bars 68 
and have its output shaft coupled with the crank shaft 141 such as by a 
reduction gear mechanism 145. Thus, supplying of pressurized hydraulic 
fluid to the motor 144 will effect revolution of the crank shaft and, in 
turn, the oscillatory movement of the swing frame 55. Use of a hydraulic 
motor is advantageous in that its speed may be readily controlled and 
adjusted by control valves. However, it will be apparent that an electric 
motor may also be utilized and provided with necessary controls and speed 
control drive mechanisms as deemed appropriate. 
It will be readily apparent from the foregoing description of illustrative 
embodiments of the slicing apparatus of this invention that a particularly 
novel and improved apparatus is provided for this purpose. The 
pendulum-type mechanism is of particular advantage in that it is capable 
of rapid slicing and also slicing of the product in timed relationship to 
deposit the slices on receivers carried on an underlying conveyor. The 
mechanism includes thickness control and is operable to assure a uniform 
slice of the desired thickness. The apparatus with the cantilevered 
structure is extremely versatile in its utilization and can be readily 
positioned at any desired point with respect to a conveyor. The operating 
components are all included within an easily protected space for greater 
operator safety.