US3519047A - Centrifugal cutter with automatic balance - Google Patents

Description

July'7, 1970 v R. A. PETERSON .ETAL 3,519,047

' CENTRIFUGAL CUTTER WITH AUTOMATIC BALANCE Filed Feb. 13, 1968 v 2 Sheets-Sheet 1 FIG 6.

INVENTORS ROGER 1 A. PETERSON JOHN PAUL ELSON CHARLES R. SMITH BY LLOYD D. SLAGELL ATTY'S.

July 7,1970 R, T R ETAL 3,519,047

CENTRIFUGAL CUTTER WITH AUTOMATIC BALANCE Filed Feb. 13, 1968 r 2 Sheets-Sheet 2 I44 7 I42 I84 48 I00 INVENTORS, ROGER A. PETERSON JOHN PAUL ELSON CHARLES R. SMITH LLOYD D. SLAGELL United States Patent 3,519,047 CENTRIFUGAL CUTTER WITH AUTOMATIC BALANCE Roger A. Peterson and John P. Elson, Peoria, Charles R.

Smith, Pekin, and Lloyd D. Slagell, Peoria, 111., assignors to Creve Coeur Mfg. C0., East Peoria, Ill., a corporation of Illinois Filed Feb. 13, 1968, Ser. No. 705,125 Int. Cl. A23n 1/02 U.S. Cl. 14676 Claims ABSTRACT OF THE DISCLOSURE The disclosure describes a centrifugal cutting device having means to continuously orient the rotating mass centers of certain corotating parts in relation to the stationary resiliently mounted mass and thereby provide vibration-free uniform cutting action. In one embodiment a flat circular cutter blade is resiliently mounted on a shaft for both axial and radial movement from a pivotally mounted plate within the housing of a driven flywheel on the reference axis. The pivotal means comprises a ball and socket joint in the drive shaft in combination with a radially displaced resilient drive pin in a centrifugal type juicing machine wherein variations in the cutting rate affects the amount of unbalanced macerated mass distributed to a centrifugating basket and the combination controls both static and dynamic balance of the rotating parts to continuously orient the mass centers, redistribute the centrifugating cuttings to restore equilibrium and maintain uniform cutting action. Other embodiments are disclosed.

CROSS REFERENCE TO A RELATED PATENT The instant invention represents an improvement over the invention described andclaimed in Smith et a1. Pat. No. 3,407,858. The entire disclosure of said patent is hereby incorporated by reference into the instant application.

BACKGROUND OF THE INVENTION In accordance with said Pat. No. 3,407,858, the dynamic and static balance of high speed rotating parts is maintained by providing a cutter drive and mounting which allows the rotating parts to cant out of the normal plane of rotation at a point diametrically opposite a point of imbalance and thereby cut deeper into the stationary workpiece, to create and deposit increased cuttings in an amount proportional to the imbalance and automatically deposit this proportional mass at said diametrically opposite points. The means to allow the rotating parts to cant described in said co-pending application included a resilient sleeve to provide limited radial and circumferential movement between the driven means and the cutter means with means to resiliently hold the cutter axially against the driven means.

SUMMARY OF THE INVENTION In accordance with this invent-ion an improved vibration dampening effect along with simultaneous re-orientation of the reference and whirl axes is obtained by supporting the driven means on a pivot pin at the reference axis between means to provide limited radial and circumferential movement between the driven means and the working means or cutter. In a particular embodiment of this invention a drive axle is provided carrying a primary flywheel. The flywheel has a housing into which is spacially fitted a movable, balanced flywheel plate. A

primary drive pin connects the primary flywheel with the flywheel plate and a resilient means is interposed between the primary drive pin and the flywheel plate. A pivot pin or ball and socket joint carries the flywheel plate 'ice central of the drive axle with slight axial displacement and slight radial displacement provided by the housing. The work means or cutter is mounted therefrom on a second drive pin with both axial and radial displacement by the cap means of said c0-pending application.

More particularly, this invention provides a high speed machine adapted to macerate juice-containing fibrous materials having a vertical rotatable shaft, a centrifugal flywheel hub mounted on and adapted to rotate with the shaft, a perforated cylindrical walled basket carried by the flywheel hub and a fixed tube to introduce the fibrous materials, wherein a cutter disc is mounted on the base plate of the basket, the flywheel hub has a housing with balance flywheel plate in the housing and pivot or ball and socket means mounting the cutter disc, basket and balance flywheel plate central of the flywheel hub whereby any imbalance of the basket or cutter is translated into increased cutting action at the fixed tube to offset the imbalance by depositing additional cuttings diametrically opposite the imbalance.

Accordingly, the objects of this invention are to provide simple, practical and effective drive mounts for the working elements of high speed rotary machines to reduce vibration due to working imbalance in such machines, to provide a floating centrifugal hub mounted on a pivot pin within a hub housing adapted to provide limited opposite radial, axial and combination radial-axial movement of the floating hub, and to provide means for mounting centrifugal working means from the floating hub whereby the machine is self-balancing both statically and dynamically. These and other objects will become apparent or be described as the specification proceeds.

DESCRIPTION OF THE DRAWINGS Reference is made to the drawings illustrating an embodiment of this invention wherein:

FIG. 1 is a partial side elevation view of the vegetable juicing machine incorporating the improvements of this invention;

FIG. 2 is a partial sectional view, enlarged to show the drive, cutter and hub assembly of this invention;

FIG. 3 is a partially exploded view, in cross-section of the parts shown in FIG. 2;

FIG. 4 is a diagrammatic view illustrating in a plane motion model, the dynamics of the centrifugal system during a condition of imbalance;

FIG. 5 is a diagrammatic View illustrating in a plane motion model the dynamics of the centrifugal system as the condition of imbalance is corrected; and

FIG. 6 is a diagrammatic view of these conditions translated to the machine to show that the imbalance is opposite the machine axis of rotation and that the wheel axis of rotation of the basket is parallel to the reference axrs.

THE PREFERRED EMBODIMENT Referring to FIG. 1, there is shown a vegetable-shredder and centrifugal juice extracting machine incorporating the drive and mounting of this invention by way of illustration, wherein a base housing member 10 supports and contains a drive motor (not shown), including the necessary electrical conduit and switch for its operation. The lower portion of the housing 10 is conventionally equipped with rubber foot elements 11 or equivalent devices to frictionally support the device on a horizontal surface with some resilient movement. A pair of oppositely disposed side supports 12 extend upwardly from the housing 10, and have oppositely facing recesses 14, hearing thumb screws 16 thereabove, designed to secure the radial ears 18 of the removable cover member 20. In its secured position the cover member 20 fits over the top of and closes the vessel 22, forming an enclosure to catch juices produced by the device.

The vessel 22 is removable and has a circumferential trough bottom 24 into which the juices collect for removal through a downwardly depending spout (not shown) communicating with the trough. The inner wall of the trough bottom 24 is formed into an up-turned circumferential flange 26 having a central opening 28 to receive a balanced flywheel hub member 30. The flange 26 is slightly off-set, as shown, to provide a retaining surface which engages and rests upon the upper edge of the housing 10. The flywheel hub 30 has a plurality of radial vanes 32 on its under side and is mounted for rotation at high speeds by the drive shaft 34, connected in turn to a drive motor (not shown) mounted within housing 10. The upper edge of housing 10, as well as the bottom of the device are provided with passageways (not shown) for the forced circulation of cooling air by the vanes 32 around the drive motor.

The flywheel hub 30 and shaft 34 carry a conventional basket 38 having a bottom wall 40 and perforated cylindrical side wall 42 with an open inwardly depending top rim 44.

A macerator disc 46, having a plurality of substantially radially arranged cutting teeth 48 on its top surface, is mounted axially of the shaft 34 contiguous to the bottom wall 40 of the basket. The cover has a vegetable feeding guide tube 50 formed integral therewith, which is open at the top and extends downwardly into the basket 38. The lower open end of the guide tube 50 is closely spaced from the macerating disc 46, as indicated at 52, at an off-center point in registry with the pattern of the cutting teeth 48 on the maceraing disc. This assembly of macerating disc 46, basket 38 is held together by means of the cap member of lead nut 54 which is attached to a ball and socket pivot pin and floating flywheel hub to the shaft 34 in a manner to be described. The rotation of the shaft 34 causes the hub 30, the basket 38, the macerator disc 46 and the cap member 54 to rotate, which parts constitute the principal elements subjected to imbalance during use of the machine. During operation, the material to be macerated is gradually introduced into the guide tube 50 into contact with the cutting teeth at the space 52. The resulting fibers and juices are flung outwardly and caught by the wall 42. The juices passes through the perforations and the fibers are retained on the inside circumferential surface of the basket. If desired, an elongated filter paper or fibrous mat can be placed circumferentially around and against the inside of the wall 42 to catch the finer vegetable or other types of pulp produced by the juicer.

It is seen that the device as thus far described is readily assembled and disassembled. Removal of the cover 20 is accomplished merely by loosening the thumb screws 16, turning the cover 20 clockwise sufliciently to clear the ears 18 therefrom from the recesses 14 and raising the cover from the device. By unscrewing the cap 54 the macerator disc and the basket 38 can be lifted from the assembly. This allows ready removal of the vessel 22 for cleaning, etc. All parts are made of corrosion resistant metal and are fabricated with smooth surfaces and rounded corners where possible to exclude undesired accumulations of food particles and juice residues.

It is apparent that the introduction of vegetables, fruits and the like through the feed guide tube 50 into contact with the macerating disc 46 at the space 52 produces a continuously increasing mass of fibers on the inner wall of the basket, which mass is directly proportional to the cutting rate at any moment of time. Normally, a wooden pestle (not shown) is provided for insertion into the tube 50 to force the vegetables downward upon the rotating disc 46. The pestle would have a shoulder larger than the opening in the tube 50 to prevent its contact at the lower end with the teeth 48. The juices pass through the perforations of the wall 42 and are collected in the bottom 24. Some fibers are retained or caught by the teeth 48 of the rotating disc 46. The accumulations of fibers on the rotating parts are not uniform because of variations in cutting rates and as the juicing operation proceeds there is developed periodic imbalance in these rotating parts. At speeds of 2000 rpm. or faster any imbalance of these principle elements disturbs the rotational equilibrium of the device and severe vibrations of the device can develop unless means are provided to counteract the disturbing influences. The existence of an imbalance also has an influence on the cutting rate and the harmonic motions developed in the parts can further accentuate the disturbance of the equilibrium of the rotating system. Part of this vibration is offset by the action of the cap member 54, as described in said copending application.

In accordance with this invention, means are provided to cooperate with said cap member 54 for automatically and continuously maintaining the rotational and dynamic equilibrium of the parts so that at no time during operation of the device does the vibration become excessive and any vibration caused by uneven distribution of fibers in the basket is counteracted. It has been found that more complete and continuous elimination of vibration can be attained by supporting the basket and cutter on a pivotally mounted plate driven by the flywheel.

The details of the structures to accomplish these results are shown in FIGS. 2 and 3 wherein the drive shaft 34 is shown to have a weight bearing shoulder 56 adjacent the bottom of the centrifugal flywheel hub 30 with the threaded spindle 58 extending into and engaging the threaded bore 60 located central of the hub. The drive shaft 34 is directly connected to a source of rotational power such as an electric motor.

The primary flywheel hub 30 has a threaded bore 60 within the center block or nave 62 and is formed with an inner annular recess 64 and a peripheral flange 66, with a pair radial bores 68 extending from the recess through the outer body of the hub to the outer wall 70 defined above the flange 66. A flat top surface 72 is provided on the hub 30 extending from the central enlarged recess 74 in the nave 62 which communicates with the threaded bore 60.

A separable retainer ring with an annular base 82 encompasses the outer wall 70 of the hub 30. A pair of radial bore holes 84 extend through the base 82. The pp r end of the ring 80 has a circumferential shoulder 86 which rests upon the outer periphery of the surface 72 and is formed with an annular flange 88 extending radially inward from the top surface 90. The ring 80 is adapted to fit over and encompass the outer surface 70 of the hub 30 with the bores 84 registering radially with the bores 63 so that each can receive a shear pin 92, only one of which is illustrated. If desired only one pair of matching bores 68 and 84 can be used in the flywheel assembly. The bottom of the base 82 of the ring 80 is spaced axially from the flange '66 as indicated at 94.

The hub 30 has a drive pin 96 press-fitted into a suitable bore in the top surface 72 and axially spaced between the oppositely facing recesses 74 and 64. The pin 96 extends above the surface 72 and has a resilient drive washer 98 encompassing this extended end.

A balance disc or upper flywheel 100 is contained within the ring 80 by means of the opposed positions of the flange 88 and the lower outwardly extending flange 102 of the disc. The disc 100 has a central threaded bore to receive the pivot pin 104, having at its lower end a ball joint 106 and threaded shank 108 at the upper end. The pivot pin 104 extends below the bottom surface 110 of the disc 100 into the central recess 74 and is axially aligned with the bore 60. The upper end of the threaded shank 58 of the shaft 34 has a recess or socket end 112 adapted to receive and mate with the ball joint 106 with a non-frictional pivotal action between these parts. Pin 104 and the shank 58 are adjustable to each other so that the space 114 between the surfaces 72 and 110 can be varied as desired Within the limits allowed by the spacing of the flange 88 over the flange 102.

The disc 100 has a recess 116 in its bottom surface 110 to engage the drive pin 96 and the resilient washer 98. The recess 116 is slightly larger than the outer circumference of the washer 98 so as to leave a space 120 therebetween. Also the recess 116 has a generally conical top wall 122 so that the top peripheral corner of the washer 98 engages same in a circumferential point contact. This edge contact arrangement imparts a greater degree of resiliency to drive action of the drive pin 96 than side wall contact and makes assembly and disassembly easy. The disc 100 is further dimensioned so that it is spaced peripherally from the retaining ring 80 as indicated by the annular spaces 124 and 126 which extend about the circumferences of these parts. The disc 100 also has a recess 128 in the top which defines a circumferential weight-bearing surface 130 around the outer edge of the disc 100. With the ring 80 in place over the hub 30, the disc 100 is held between the pivot 106-112 and the opposing contact between the flange 88 and the flange 102 in a resilient movable manner as will be described.

A second drive pin 132 is fixed within the body of the disc 100 and extends upwardly through the bore hole 134 of the bottom 40 of the basket 38. Likewise, central of the bottom, the bore hole 136 of the basket receives the top end of the pivot pin 104. The macerator disc 46 has a central bore 138 and a smaller bore 140, to receive the pivot pin 104 and second drive pin 132, respectively. Both the bores 134 and 140 are slightly larger than the drive pin 132, so that the spaces 142 and 144, therebetween, produce a slight play between these parts.

The bottom surface 146 of the basket 38 rests upon the circumferential surface 130 of the disc 100. The shank 108 of the pivot pin 104 extends through the assembled parts as an extension of the axis of the shaft 34 where it is engaged by the cap member 54.

The cap member 54 has the central threaded bore 152, engaging the shank 108 and a smaller bore 154 extending from the shoulder 156 to the chambered top. A transverse bore 158 extends radially through the cap and intersects with the bore 154. The transverse bore 158 is for the purpose of inserting a pin wrench to tighten or loosen the cap from its locked position on the pivot pin 104.

A plunger sleeve 160 encompasses and is slidably mounted on the body of the cap 54 and is held thereto in a downwardly biased position by means of the compression spring 162, held between the shoulder 164 of the annulus 166 and the internal radial flange 168 of the sleeve. A C-ring or spring washer 180 engaging a circumferential groove at the base of the plug member provides the means for retaining the sleeve 160 in place. The spring 162 allows the sleeve 160 to be moved axially of the assembly. When tightened in place on the pivot pin 104, the bottom peripheral surface 182 of the sleeve impinges against the top surface 184 of the cutter disc 46 and the base of the plug is spaced therefrom as at 186. This gives a slight axial and canting resilience to the cutter on the pivot pin 104 in cooperation with the spaces 142 and 144 around the drive pin 132. The unthreaded portion 188 of the shank 108 is long enough to engage the bores 136 and 138 in the sliding clearance fit supra.

The balancing members so far described have the following features and meet the following requirements: The basket 38 and the cutter 46 are free to tilt quite freely through a very small angle defined and limited by the spacing of the parts. The basket and cutter are also rigidly restrained from tilting any further than this small limited angle. These parts are free from any tendency to vibrate or create vibrational noise. The tendency for liquids to leak into these parts is mitigated or prevented. The structure is simple so that the parts are readily fabricated, assembled, adjusted and maintained.

The combination of the pivot pin 104, the resilient drive pin 96 and the spacing of parts comprise a spring pivot which keeps the upper flywheel disc 100 centered with respect to the axis of rotation of the hub or lower flywheel 30. The spring pivot oifers very little resistance to the tilting action of the disc 100 and holds this part tightly against the outer restraining ring and thus reduces the possibilities of vibration and vibrational noise from the disc during high speed operations. The flywheel hub 30 and the ring 80 operate as a unit and the pivot pin 104 imparts a spring pivot action strong enough to keep the disc 100 tightly against the flange 88 and allow movement provided by the spaces 124 and 126. At the same time the disc 100 is prevented from movement in a vertical or axial direction.

The ring 80 acts as a collar for the upper flywheel disc 100 holding the unwanted deflections to a minimum and preventing harmonic motions of the resiliently suspended parts. By restraining the flywheel dlisc 100 at its outermost edges instead of at its center and at its outer edges, the forces produced between the upper flywheel and its mating parts are held to a minimum and deflections are reduced. The collar effect of the ring 80 also provides definite and limited restraint of the upper flywheel 100 about any horizontal axis within the spaces 124 and 126 into which the forces may tend to cause it to tilt. The resilient drive pin 96-98 combination reduces vibrational noise due to torsional vibration between the upper and lower flywheels. Since the flanges 102 and 88 are in substantially constant axial pressure against each other, the possibility of liquids leaking into the spaces 114 and 126, and the recess 74 is minimal.

Referring to FIGS. 4, 5 and 6, the dynamics of the system will now be explained. M represents the effective mass of the entire machine body 10 while In represents the concentrated mass of the rotary basket 40 and the cuttter blade 46. The spring forces K represent the effective elasticity of the vibration dampening forces or isolaters acting in the plane of vibration of the system.

Under normal conditions the center of mass m will be coincident with the center line CL of the entire system. FIG. 4 illustrates the condition wherein the center of the mass m has been moved a radial distance e from the center of the machine axis of rotation. This condition results from an imbalance in the basket or cutter or both due to the uneven distribution of fibrous residue during the high speed juicing process. It can be shown that the horizontal motion of the mass M in the direction of the arrow x is given approximately by the equation:

where w is the constant speed of the motor and W1 represents the angular velocity of the mass m in the quadrant shown. A similar equation exists for horizontal motion in the y axis direction and for each quadrant of rotation about the center line. By defining r as the ration of the motor speed to the natural free vibration of the system in the horizontal plane, the motion of the mass, M in the x direction in quadrant shown is wherein A is a constant having a value of less than 1.0, since m M.

Equation 3 illustrates that the mass center mi of the rotating basket and blade is displaced opposite the ma chine axis of rotation C by the distance and direction x shown in FIG. 5. The basket and blade combination mass m rotates around the displaced center C and the mass M whirls or oscillates around the whirl axis C.

In FIG. 6 this relationship has been translated into a diagrammatic representation of the parts of the instant apparatus where C is the whirl axis of the mass M, C

is the original center line of rotation, the basket and cutter are designated by their reference members, and a is the tilt angle on the pivot 196. The stationary tube 50 is shown in two positions of rotation to illustrate that the cutter disc is tilted closer to the tube 50 when the mass m is opposite thereto and away from the tube 50 when the mass m is in the same quadrant as the tube 50. As the mass m of debris passes in the position shown, the pivot 106 allows the rotational plane threof to remain independetn of the whirl c of the mass M. This brings the cutter 40 into closer contact to the tube 50 by the amount of the tilt angle a. And as the mass m passes the fixed tube 50' the cutter 40 is inclined away from the tube 50 by an amount equal to the tilt angle a. In other words the plane of rotation of the cutting blade and the mass m is independent of the whirl axis of the mass M by an amount equal to the tilt angle a due to the pivot axis 106.

It is apparent from the foregoing that the pivot 106 allows the rotating elements to shift slightly radially and also tilt upon the axis 34 under the yielding action of the drive pin 96, the resilient holding action of the cap member 54 and the tilting support of the flywheel disc 100 within the spaces 124 and 126. The spaced relation of the drive pin 132 does not interfere with this action.

To provide at least part of this resiliency the washer 98 and the sleeve 160 are preferably constructed of a tough plastic having good molding qualities, high tensile strength in the order of 5,000 to 13,000 p.s.i (A.S.T.M., D 638, D 651), good flexural strength comparable to 8,000 to 14,000 p.s.i. (A.S.T.M., D 790) and a Rockwell hardness of about 100 to 120. Such plastics as nylon, polyvinyls, Teflon, polyethylene, urea formaldehyde, methylmethacrylates, modified styrene, and polyacrylics may be used for purposes of forming these parts. Softer, more flexible non-rigid vinyl chloride polymers and copolymers, vinyl chloride-acetate resins, rubber, polyethylenes, and elastomeric types of plastics can also be used.

One skilled in this art will know that various monomers and elastometer compositions can be formulated with or without fillers and plasticizers to produce molded parts having the desired physical and chemical properties to be suitable for use as the washer and sleeve parts and same can be cut from extruded plastic hose having the desired inside and outside diameters, or formed by compression or injection molding with or without machining to present a smooth bottom surface 182 and the proper internal dimensions and clearances, to maintain the spaces 124 and 126.

While the drawing discloses this invention in relation to a vegetable juicing machine, it is to be understood that this invention applies to any centrifugal device having a driving means and a driven means carrying a working member at a high rotational speed and adapted to do Work upon a stationary workpiece or a material wherein conditions of imbalance and vibration in the principle moving parts occur. The pins, 96 and 132 maintain a positive driving action between the centrifugal hub 30 and the working member 46. Any means of attaching the hub with the working members can be used which provides a direct driving action between these members yet allows pivot 106 to function therebetween and also allows easy assembly and disassembly.

The device shown in the drawing is in scale with an embodiment in which the mass weight of the hub is about 32 02., the macerator disc about 9 oz. and the basket is about 22 oz. The relative movement permitted by the pivot 106 is related to accommodate about a 1 oz. excess weight developing at one point on the periphery of the basket of a diameter of 7 inches. The speed of rotation in the order of 2,000 r.p.m. and higher is well above the oscillatory moment of the inertias involved at 7 inch diameter and are further dampened by the radial friction and pivotal action exerted by the parts. It is appreciated that with the weights mentioned for the parts, the tilt angle of the rotating parts is only a few minutes or part of a degree. Although this is critical for dampening undesirable vibration, the pivotal shift accomplished by the invention and creation of the new center of rotation takes place progressively as needed with little if any vibration building up at any time. As soon as an imbalance developes the device restores itself to balanced conditions.

It is apparent that other modifications of the structures shown can be made without departing from this invention. Thus, the hub 30 may be constructed integral with the collar 80, omitting the drive or shear pins 92, and the flange 88 can be a separable unit adapted to be atfixed to the integral flywheel by any suitable means after the balance plate is in position. The balance plate 100 can have a double flange arrangement with a top flange extending radially from the surface over the surface 90. The collar 80 can be formed in two parts, each encompassing one-half of the circumference of the hub. The ball 106 and socket 112 arrangement can be reversed. The cap 54 can be replaced by a resilient flat washer encompassing the pivot shaft 108 and held in place by a lock nut engaging the threaded portion 108. The shaft 34 and the hub 30 can be constructed as integral parts with the recess 74 serving as the socket joint.

Although but one specific embodiment of this invention has been herein shown and described, it will be understood that details of the construction shown may be altered or omitted without departing from the spirit of the invention as defined by the following claims.

What is claimed is:

1. A centrifugal cutting device having a rotatable driving means carrying a Working means for high speed contact with a work piece comprising:

(a) means supporting said working means pivotally carried at the axis of rotation by said driving means;

(b) means providing limited radial and circumferential movement between said support means and said working means; and

(c) means for resiliently holding said working means axially against the periphery of said support means whereby said working member and said support means are adapted to move relative to said driving means under an imbalance of said working member.

2. A centrifugal cutting device in accordance with claim 1 in which:

(a) said driving means comprises a flywheel mounted on the end of a rotatable drive shaft;

(b) said flywheel having a recess in its surface on the side opposite said shaft;

(0) said recess having a circumferential inwardly depending flange about its periphery; and

((1) said support means comprising a balance plate pivotally mounted at the axis of rotation within said recess and contained therein by said peripheral flange.

3. A centrifugal cutting device in accordance with claim 2 in which:

(a) said flywheel has a central recess opening to said balance plate;

(b) a pivot shaft is mounted through said balance plate with one end pivotally mounted within said recess;

(c) a drive pin extends from said flywheel into a blind bore hole in said balance plate; and

(d) resilient washer means are provided between said drive pin and said blind bore hole.

4. A centrifugal cutting device in accordance with claim 3 in which:

(a) said blind bore hole has a conical bottom engaging the peripheral corner edge of said resilient washer means.

5. A centrifugal cutting device in accordance with claim 3 in which:

(a) said drive shaft extends into the recess of. said flywheel; and

(b) said pivot shaft engages said drive shaft in a ball and socket relationship.

6. A centrifugal cutting device in accordance with claim in which:

(a) said drive shaft has a ball socket at the end thereof; and

(b) said pivot shaft has a ball joint adapted to pivotally engage said socket.

7. A centrifugal cutting device in accordance with claim 2 in which:

(a) said balance plate has a marginal edge extending circumferentially therefrom;

(b) said inwardly depending flange of said flywheel overlaps and axially engages the marginal edge "of said balance plate; and 1 (c) the peripheral surfaces of said balance plate are uniformly spaced from the inner axial surfaces of said recess in said flywheel.

8. A centrifugal cutting device in accordance with claim 7 in which:

(a) said flywheel has a detachable collar defining said recess and said inwardly depending flange;

(b) said collar has a radial bore through a side wall thereof matching a radial bore in the body of said flywheel; and

(c) a shear pin engages said matching bores to hold said flywheel and collar as a rotatable unit.

9. A centrifugal cutting device in accordance with claim 1 in which:

(a) said Working means includes a flat circular member with cutting teeth on its peripheral surface and a catch basket therearound adapted to receive a stationary work piece therein in engagement with said cutting teeth;

(b) said balance plate has a raised peripheral edge engaging said working means radially of the axis of rotation thereof;

(c) a second drive pin extends from said balance plate into a bore hole in said working means, said bore hole being circumferentially spaced from said second drive pin; and

(d) the means for resiliently holding said working means axially against the periphery of said support means comprises a cap member engaging said shaft, a tubular friction member supported by said cap member and biased against said working means.

10. In a high speed machine adapted to macerate juicecontaining fibrous materials and separate the juice and fibers thereof, wherein said fibrous materials are introduced through a fixed inlet into a rotating perforated basket subject to vibration due to uneven accumulations of said fibrous material therein, the combination of:

(a) a flat base plate in said basket having a central bore;

(b) a cutter disc on said base plate with a central bore in alignment with the central bore of said base plate and having cutting teeth extending upwardly along its periphery in close proximity to said fixed inlet;

(c) a rotatable shaft in said machine with a socket joint at the extended end thereof;

(d) a flywheel hub member aflixed to the end of said shaft;

(c) said hub member having a substantially cylindrical 10 outer wall, and a flat face on the side opposite said shaft with a central recess in said face receiving said socket joint of said shaft;

(f) a collar member encompassing the outer wall of said hub and aflixed thereto by means of a shear member;

(g) said collar member having a peripheral shoulder engaging the outer edge of said flat face of said hub member and a peripheral inwardly depending flange circumferentially spaced from said flat face;

(h) a balance plate having a central bore axially aligned with said socket joint on the end of said shaft;

(i) said balance plate having a flat bottom face and a radial flange extending under said circumferential flange of said collar member;

(j) said balance plate having its peripheral surface spaced from the inner surfaces of said collar member;

(k) a pivot pin affixed within the central bore of said balance plate;

(1) said pivot pin having a ball joint at its bottom end in engagement with the socket joint of said rotatable shaft and supporting said balance plate within said collar with its radial flange axially engaged by the inwardly depending flange of said collar member;

(m) the end of said pivot pin extending through the central bores of said cutter disc and said base plate;

(n) a first drive pin extending from said hub member into a blind bore in said balance plate radially spaced from said recess;

(0) a second drive pin extending from said balance plate into a pair of aligned radially spaced bores in said cutter disc and said base plate, said second drive pin having a diameter less than the diameters of said bores to provide lateral spacing therein;

(p) a detachable cap member aflixed to the extended end of said pivot pin having its base spaced from the top of said cutter disc; and

(q) a peripheral resilient sleeve in said cap member with means biasing said sleeve into contact with cutter disc whereby said base plate and cutter disc are adapted to tilt about said pivot axis on the side opposite the accumulation of an imbalance in said basket about the whirl axis of said machine an amount sufficient to increase the proximity of said cutting teeth to said fixed inlet to increase the cutting rate thereof on said opposite side and centrifuge said increased cuttings to the radially adjacent portion of the basket and automatically compensate for said imbalance.

References Cited UNITED STATES PATENTS 2,466,153 4/ 1949 Chamberlin 210-367 X 2,519,813 8/1950 Bayless 210365 3,165,132 1/1965 Moline 4 14676 3,407,858 10/ 1968 Smith et al. 146-76 W. GRAYDON ABERCROMBIE, Primary Examiner US. Cl. X.R. 146-3

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