1998-07-14 Application filed by Zittel; David R. filed Critical Zittel; David R.
A machine for peeling and cleaning fruits and vegetables using a plurality of rotating abrasive rollers which are each driven by an electric motor. The machine has a frame with a pair of end plates that rotatively carry the rollers. Each motor is carried by an end plate and coupled to a roller solely to drive only that roller. In one preferred embodiment, the motor is coupled to a gear reducer that preferably is a cycloidal gear reducer having an output shaft coupled to one end of a roller and which has an output shaft axis of rotation generally coaxial with the axis of rotation of the roller. In another preferred embodiment, the motor can be directly coupled to the roller with its output shaft axis of rotation generally coaxial with the roller axis of rotation. To control operation and speed of the abrasive rollers, the motors are controlled by a motor controller that preferably is a variable frequency electric motor drive. Where the machine uses an auger to urge food product through the machine, the auger can be driven by an electric motor whose operation and speed preferably is controlled by a variable frequency electric motor drive. Where the machine is a rotating cage machine, the cage can be driven by an electric motor whose operation and speed preferably is controlled by a variable frequency electric motor drive. Each motor preferably is a three phase alternating current electric motor.
This application is a continuation of U.S. application Ser. No. 08/785,746, that was filed Jan. 17, 1997, and which issued Jul. 14, 1998, as U.S. Pat. No. 5,780,088.
The present invention relates to a method and apparatus for treating a product using rotating rollers and more particularly to a method and apparatus for abrasively treating a product using rotating, abrasive rollers.
In the peeling and cleaning of food products that are typically vegetables and fruits, food processing machines utilizing rotating rollers that abrade the food product to peel, clean or wash the food product are commonly used. Each abrasive roller peeling and cleaning machine utilizes several abrasive elongate rollers grouped in a circle or semicircle to form a chamber for receiving the food product. Each machine also includes a drive system for rotating each roller. Abrasive roller peeling and cleaning machines are favored and have enjoyed considerable commercial success because they are versatile and use little, if any, water during operation minimizing post-processing water treatment costs.
During operation, each of the rollers of an abrasive roller food processing machine are rotated about a central longitudinal axis and food product entering the machine engages one or more of the rotating rollers. While in contact with a roller, the roller contacts and at least slightly abrades the food product. Each roller typically comprises a central core that has brush bristles which extend radially outwardly from the core which engage food product to wash or abrasively clean, peel, or clean and peel the food product. Other commonly used roller configurations include a roller having an exterior made of a relatively rough sandpaper-like material and a roller having a plurality of slightly axially spaced apart circular flexible rubber or plastic fins (flanges) or fingers carried by the roller core.
When cleaning food product, the rotating rollers abrade the food product to remove dirt and other residue on the food product to prepare the food product to be further processed or to enable the cleaned food product to be packaged and shipped to market. When peeling food product, the rotating rollers abrade the exterior of the food product typically to remove its skin thereby also washing or cleaning the food product. In some instances, while either cleaning or peeling food product, some water or another solvent can be introduced in the food product receiving chamber of the machine along with the food product.
In one type of abrasive roller peeling and cleaning machine, the machine comprises a frame with a pair of generally upstanding and spaced apart endplates that carry the rollers between them. The rollers are journalled for rotation in the end plates, both end plates remaining stationary during operation. Generally, the rollers are arranged in an upturned U-shaped semicircle (stationary U-bed) with very little space between each pair of adjacent rollers to prevent food product from passing between adjacent roller pairs and falling downwardly. To enable food product to flow from an inlet end to an outlet end of the machine, a rotating auger between the rollers urges food product axially relative to the rollers from the inlet toward the outlet.
In another type of abrasive roller peeling and cleaning machine, the abrasive rollers are arranged to form a cylindrical food product receiving chamber and are each journalled for rotation in the end plates which in turn are rotatably carried by the frame. More particularly, the rollers, struts and end plates form a cage that is rotated in addition to each abrasive roller being rotated. To enable food product to flow from the inlet to the outlet of the machine, the machine can be tilted downwardly in the desired direction of product flow or an auger can be received in the chamber with relative rotation between the cage and auger causing food product to be urged by the auger from the inlet end toward the outlet end of the machine.
To rotate the abrasive rollers, several types of drive mechanisms or drive systems are used. In one commonly used drive mechanism, the rollers are interconnected by belts with one of the rollers being connected to an electric or hydraulic motor by another belt. These belts simply transfer power between the rollers and transfer power from the motor to the rollers. The belts do not function as a gear reducing mechanism and therefore do not reduce the output speed of the motor to enable the rollers to handle more torque caused by a greater load on one or more of the rollers.
This relatively complicated drive mechanism is costly in construction and in maintenance. One known disadvantage to this type of drive mechanism is that all of the belt-interconnected rollers driven by a motor must all be driven at the same speed as the motor and cannot be varied in speed relative to another belt interconnected roller. Another known disadvantage to the belt drive mechanism is that belt wear during use can require time consuming and costly machine shutdowns to replace one or more worn belts. As a result of belt wear, one or more of the rollers can rotate at a speed less than the desired rotational speed which can result in incomplete peeling or cleaning of food product or which can cause the food product to have to remain longer in the chamber than desired to achieve the desired peeling or cleaning. Finally, these systems are bulky and use many moving parts, each of which decreases reliability while increasing maintenance.
In another kind of drive mechanism, each roller is driven by a hydraulic motor that is supplied with hydraulic fluid under pressure from a hydraulic pump. The motor is attached to an endplate of the peeling and cleaning machine and has an output shaft coupled to an abrasive roller. In a known U-bed stationary abrasive roller peeling and cleaning machine manufactured by Lyco Manufacturing Inc., 115 Commercial Drive, Columbus, Wis. 53925, the machine has two banks of rollers with the rollers of a given bank driven at the same speed and the roller speed and direction of one bank being variable relative to the roller speed and direction of the other bank. It is believed, and heretofore not known otherwise, that all of the rollers of a bank of rollers of the machine are not driven at exactly the same speed by the pump and motors because the motors are supplied in series with hydraulic fluid from the pump and fluid pressure losses downstream can cause downstream motors to run more slowly.
Unfortunately, without resort to relatively expensive hydraulic fluid throttling valves for each hydraulic motor, the speed of one roller in a bank cannot be selectively varied relative to another roller of the bank thereby at least somewhat limiting the versatility of the machine. Additionally, hydraulic drive systems are quite complicated and expensive to manufacture and can have reliability problems if hoses break or internal motor seals leak.
Another difficulty with hydraulic drive systems is that the hydraulic motor seals currently in use cannot typically withstand hydraulic fluid pressures of greater than about 1000 p.s.i. However, in many instances, to power in series as many as four or more rollers of a bank of rollers, an input pressure of as much as 1500 p.s.i. or greater is needed. To remedy this problem and prevent premature seal blowout, a flow divider is typically used. Unfortunately, using a flow divider results in pressure losses of as much as 150 p.s.i. or more in addition to pressure losses after each motor. All of these pressure losses accumulate resulting in a great deal of energy wasted as well as the rollers further downstream typically operating at a speed slightly slower than the speed of the upstream rolls.
In rotating cage type abrasive roller peeling and cleaning machines, either the inlet or outlet of the machine carries a hub that is driven through a belt by a motor that typically is an electric or hydraulic motor to cause the cage to rotate about a longitudinal axis of the cage. As the cage rotates, a ring-shaped stationary gear carried by the frame has inwardly extending teeth that engage a tooth of a gear at the end of each roller to drive the roller as the roller gears orbit interiorly the stationary gear. An example of this type of drive arrangement is found in U.S. Pat. No. 5,245,919.
This type of drive arrangement is rather elaborate and complicated because it uses so many moving parts to transfer rotary motion of the cage to each of the abrasive rollers. This complexity adds expense and increased maintenance. In addition to being more complicated and costly, this type of drive arrangement is limited because each of the drive rollers are driven by a single stationary gear as the cage rotates causing them all to rotate at about the same speed. As a result of being driven by a single stationary gear, none of the abrasive rollers can rotate at a different speed relative to any other roller. Moreover, the speed of all of the rollers is ultimately dependent upon the speed of rotation of the cage further limiting machine and processing flexibility.
What is needed is a drive system for an abrasive roller peeling and cleaning machine that enables each of the abrasive rollers to be driven independently of every other roller of the machine so that the speed of the rollers can be controlled and precisely varied. What is also needed is a more efficient abrasive roller drive system that provides more complete control over the entire peeling and cleaning process. What is further needed is a drive system for a rotating cage peeling and cleaning machine where the abrasive rollers are driven independently of the cage and auger. What is still further needed is a drive system for a rotating cage peeling and cleaning machine that enables the roller to be driven independently of the cage and independently of each other. What is also needed is a drive and control system for a peeling and cleaning machine that is more compact, more reliable, simpler and cheaper to manufacture and operate.
A peeling and cleaning machine for washing, cleaning or peeling fruits and vegetables that has a plurality of abrasive rollers that rotate during operation to engage and at least slightly abrade food product that comes into contact with one or more of the rollers to wash, clean or peel the food product. The rollers are rotatively carried by a spaced apart pair of end plates that form part of the peeling and cleaning machine frame. The rollers are mounted to the end plates such that at least a portion of the rollers define a generally semicircular food product receiving chamber that has an inlet and an outlet. In a rotating cage peeling and cleaning machine, the rollers and endplates form a rotatable cage and an elongate generally cylindrical food product receiving chamber.
Each roller is driven by its own electric motor thereby advantageously simplifying the roller drive mechanism while also making it more compact and reliable. Each abrasive roller drive motor preferably is an alternating current electric motor that preferably is of three phase construction. If desired, the motor can be of direct current construction or of 120 volt AC construction. If the roller is directly driven only by the motor, the output shaft of the motor preferably is substantially coaxial to the axis of rotation of the roller coupled to the motor output shaft.
Each motor is carried by one of the end plates and positioned such that its output shaft is adjacent one end of an abrasive roller so it can be easily coupled to the roller. Preferably, each motor is mounted to a motor mounting plate that is located outwardly of and adjacent to an end plate. Each motor is mounted to the mounting plate with its shaft extending through an opening in the plate toward an end of the abrasive roller. Preferably, the motor mounting plate is carried by or mounted to the frame of the machine and can be mounted to or carried by the end plate, if desired.
To provide a sufficient amount of torque to each of the rollers so that each roller can rotate despite being heavily under load, each motor is coupled to a gear reducer of relatively compact construction that is in turn coupled to one end of an abrasive roller. The output shaft of the gear reducer is coupled to the roller such that its axis of rotation is generally coaxial or coincident with the axis of rotation of the roller whether or not the motor output shaft is generally coaxial with the roller axis of rotation. Preferably, the gear reducer is a cycloidal-type gear reducer for providing heavy duty and reliable operation and which is capable of withstanding relatively large shocks such as what can be experienced during the peeling and cleaning of food product.
To control operation and speed of each of the abrasiver rollers, a motor control capable of controllably varying the rotational speed of each roller by controllably varying the rotational speed of each abrasive roller drive motor preferably is used. The motor control preferably is an inverter or a variable frequency electric motor drive. Such a motor drive is constructed and arranged to vary the rotational speed of each motor such that the rotational speed of each roller is between about 100 revolutions per minute (rpm) and about 600 rpm. Preferably, the abrasive roller motor and variable frequency speed drive can be selected to enable the abrasive roller to rotate at speeds as high as 900 rpm or higher, if desired.
Where it is desired to control the operation, speed and direction of one of the abrasive rollers relative to another of the abrasive rollers, more than one variable frequency drive can be used. For example, if it desired to rotate a bank of four rollers in one direction or at a certain speed and the remainder of the rollers forming a bank of rollers which rotate in another direction or at a different speed, two variable frequency drives are used with one drive in control of one bank and the other drive in control of the other bank. More than two variable frequency drives can be used to control the abrasive roller drive motors.
An auger comprised of a shaft rotatively carried by the peeling and cleaning machine frame has a continuous and generally helical auger flight that is carried by the shaft and which is rotated by a motor can be used to urge food product through the product receiving chamber of the machine. If an auger is used to facilitate food product flow through the product receiving chamber, the auger shaft preferably is coupled to an electric motor that is controlled by a variable frequency drive. By this construction, the rotational speed of auger can be controlled to control how long food product remains inside the chamber of the machine thereby providing relatively precise control over the quality of clean or peel that is imparted to food product passing through the machine.
Preferably, the auger drive motor is coupled to the auger shaft by a gear reducer that can be a conventional helical gear gear reducer or which can be a cycloidal gear reducer. If coupled to the shaft by a gear reducer, the gear reducer can be a generally right-angled gear reducer.
For rotating cage peeling and cleaning machines having the abrasive rollers rotatively mounted to end plates which rotate all of the rollers about a common longitudinal axis of rotation during operation, the cage is rotated independently of the rotation of each individual abrasive roller. Preferably, the cage is driven by an electric motor that also can be controlled by an inverter or variable frequency drive for controlling the direction and speed of rotation of the cage during machine operation.
To communicate electrical power to each abrasive roller drive motor carried by an end plate, the rotating cage machine has a slip ring or commutator for enabling electrical power to be supplied to each of the abrasive roller drive motors while the roller drive motors rotate in unison along with the rest of the cage about the axis of rotation of the cage. If an auger is used, the commutator preferably is a pair of telescopically nested generally cylindrical and hollow cores which are both telescoped over a portion of the auger shaft.
Wires extend radially inwardly from each roller drive motor to the outer core of the commutator which communicates with brushes or contacts that encircle both the radially inner surface of the outer core and radially outer surface of the inner core to communicate power between the cores while the cores are rotating relative to each other. A motor power supply wire or lead extends from the inner core to a motor control unit that preferably includes one or more variable frequency drives and a power supply. The inner core rides on bearings on the auger shaft enabling it to rotate relative to the auger shaft and enabling the auger shaft to rotate relative to the commutator. The outer core rides on bearings on the inner core permitting relative rotation between the outer core and inner core.
In another type of commutator for transferring power to rotating abrasive roller drive motors, each motor has an axially outwardly extending contact wheel that rides along the radially inner surface of a stationary ring secured to the frame. Both the ring and contact wheel have brushes or contacts that bear against each other as the contact wheel of each motor rides along the ring receiving electrical power from the ring thereby powering each abrasive roller motor. Electrical power is supplied to the ring by the variable frequency drive or drives responsible for controlling abrasive roller motor operation.
It is an object of the present invention to provide a machine that uses elongate and generally cylindrical abrasive rollers, that can be brushes or grit covered rollers, which are each rotated by an electric motor to clean, wash or peel food products that come into contact with a roller.
It is an advantage of the present invention to provide a peeling and cleaning machine that drives the abrasive rollers using fewer moving parts for decreasing assembly costs, increasing reliability and lessening maintenance.
It is another advantage of the present invention in that the use of electric motors to drive each abrasive roller provides greater control over abrasive roller speeds and direction of rotation.
It is another object to provide a peeling and cleaning machine control system that is capable of rotating the auger independently of the abrasive rollers.
It is still another object to provide a peeling and cleaning machine control system that is capable of rotating the abrasive rollers independently of and separately from a rotating cage carrying the rollers.
It is yet another object to provide a peeling and cleaning machine control system that can be used both with stationary U-bed peeling and cleaning machines and rotating cage peeling and cleaning machines.
It is a feature of the present invention that the rotational speed of the abrasive rollers can be more widely varied and more precisely controlled than planetary gear, belt drive and hydraulic abrasive roller drive systems.
It is another feature of the present invention that the peeling and cleaning machine control system is versatile in that it can be adapted for use with peeling and cleaning machines which have an auger, which do not which have an auger, have a rotating cage, and which do not have a rotating cage.
Further objects, features, and advantages of the invention will be apparent from the following detailed description when taken in conjunction with the accompanying drawings.
FIG. 19 is an end view of the rotating cage peeling and cleaning machine with parts missing to more clearly illustrate the bearing ring.
Referring more particularly to drawing FIGS. 1-4, wherein like numbers refer to similar parts, a food processing machine 40 for peeling and cleaning fruits and vegetables using one or more rotating abrasive rollers 42 is shown. Each abrasive roller 42 is driven by an electric motor 44 that is electrically connected to a drive motor control box 46 which controls motor operation and is electrically powered by a drive motor power supply 48. To help provide the necessary torque to each roller 42 so that the motor 44 will rotate the roller 42 even when the roller 42 is heavily loaded, the motor 44 can have and preferably is equipped with a gear reducer 50 in operable communication with its output shaft 52 (FIG. 9).
The peeling and cleaning machine 40 is carried by a frame 54 which is supported on legs 56. Enclosing the rollers is a housing 58 that is constructed of a hygienic, easy to clean material that can be stainless steel, nylon or the like. Below the housing 58 is a funnel-shaped collection pan 70 that collects the skin, juices, moisture, dirt and other residue that is produced during operation and which has an opening to direct this material into a collection basin 72 (shown in phantom in FIG. 4) below the pan 70. The collection basin 72 can be constructed with an outlet drain port 74 for enabling material that has collected in the basin 72 to be drained or purged from the basin 72.
Food product enters the machine 40 at an inlet end 60 through an inlet chute 62 and exits the machine 40 at an outlet end 64 through a discharge chute 66. Typically, food product is carried by a conveyor (not shown) to the inlet chute 62 and processed food product is carried away from the discharge chute 66 by another conveyor (not shown). As is shown in FIG. 1, the machine 40 can have a shroud 68 at its inlet end 60 that substantially encloses the inlet chute 62 and covers all of the abrasive roller drive motors 44.
Referring to FIGS. 3 and 4, the abrasive rollers 42 are rotatively carried by the frame 54 in a generally upturned semicircular or U-shaped configuration defining a product receiving chamber 76 between the rollers 42. Received between the rolls 42 in the chamber 76 is an auger 78 that rotates during operation to urge food product received in the chamber 76 from the inlet end 60 toward the outlet end 64.
The auger 78 is constructed of a single generally helical and continuous flight 80 with bristles 82 that extend outwardly from its periphery to help urge food product through the machine 40 without damaging it. The auger flight 80 is carried by a shaft 84 that is rotatively carried by the frame 54. The frame 54 is shown in FIG. 3 having a pair of arms 86 that each extend downwardly from the top of the frame 54 to which an end of the auger shaft 84 is rotatively journalled. Each end of the shaft 84 is preferably rotatively supported by bearings carried by each auger support arm 86. Of course, the auger 78 and its shaft 84 may be mounted to the frame 54 in another manner.
To rotate the auger 78 during machine operation, there is an electric motor 88 connected to one end of the auger shaft 84. The auger drive motor 88 is shown in FIG. 3 connected to the shaft 84 adjacent the outlet end 64. The auger drive motor 88 is an electric motor having a power input lead 90, only a portion of which is shown in FIG. 3, that extends outwardly from the motor 88 and which is connected to the drive motor control box 46. During operation, electrical power is communicated from the power supply 48 through the control box 46 to the auger drive motor 88 to cause the motor 88 to rotate the auger 78. The control box 46 preferably is equipped with controls that enable an operator of the machine 40 to selectively vary the rotational speed of the auger 78 during operation.
Although the auger drive motor 88 is shown in FIG. 3 directly coupled to the auger shaft 84, it preferably can be connected to the shaft 84 by a gear reducer that can be an axially in-line gear reducer 92 or a right-angled gear reducer for communicating more torque to the shaft 84 to ensure auger rotation particularly when the auger 78 is relatively heavily loaded by food product in the chamber 76. So that the auger drive motor 88 can rotate the auger 78, the motor 88 is immovably anchored to the frame 54, such as by being anchored to the auger support arm 86. If a gear reducer is used, the gear reducer, is immovably anchored also immovably anchoring the motor 88.
The auger 78 is shown in FIG. 3 extending the full longitudinal length of the peeling and cleaning machine 40. If desired, the auger 78 can be shorter than that shown and used alone or in combination with a gate (not shown) to urge and control food product flow through the machine 40. If desired, the machine 40 can be used without an auger 78 if the machine is equipped with another mechanism for urging food product through the chamber 76. One example is a mechanism for tilting the machine 40 downwardly from its inlet end 60 toward its outlet end 64. An example of such a mechanism is support legs of different lengths or which are length adjustable such that the legs 56 adjacent the inlet end 60 are longer than the legs 56 adjacent the outlet end 64 downwardly tilting the machine 40 from its inlet end 60 toward its outlet end 64. With or without an auger 78, the machine 40 can be downwardly tilted from its inlet end 60 toward its outlet end 64.
Each abrasive roller 42 is journalled for rotation at one end in an end plate 118 of the frame 54 of the peeling and cleaning machine 40 adjacent the outlet end 64 and at its other end in another end plate 120 of the frame 54 adjacent the inlet end 60. Referring additionally to FIG. 7, each abrasive roller 42 consists of an elongate cylindrical core 94 that has an abrasive exterior 96. Examples of suitable abrasive roller exteriors 96 include nylon or elastomeric brushes that extend radially outwardly from the core 94, axially spaced apart flexible rubber discs carried on the core 94, axially and circumferentially spaced flexible elastomeric fingers carried on the core 94, and abrasive grit applied directly to the exterior of the core 94 or on a substrate carried by the core 94.
The core 94 preferably has a hollow 98 at each end for receiving a mandrel 100 and 102 of a roller support assembly 104 and 106. At the driven end of the roller 42, the mandrel 100 has a female recess 108 for receiving a complementary male drive shaft coupling 110 that is operably connected to an output shaft 52 of the motor 44. If desired, the coupling 110 or mandrel 100 can also include a bearing (not shown) journalled to the frame 54 of the machine 40 for helping to rotatively support the roller 42. The coupling 110 has a generally square box-shaped head 112 that is received in a complementary box-shaped recess 108 in the mandrel 100. The coupling 110 preferably has a hollow shank 111 with at least one radially outwardly extending key inside the hollow 113 of the shank 111 that mates with a complementary slot or keyway 115 in the drive motor output shaft 52 or 122 when the shank 111 is telescoped over the output shaft.
At the non-driven end of the roller 42, the mandrel 102 mates with a bearing 114 and a stub support shaft 116. The bearing 114 and stub shaft 116 preferably are journalled to the frame 54 of the machine 40 to rotatively support the roller 42 opposite its driven end.
Each abrasive roller drive motor 44 is an electric motor 44 that is a direct current or alternating current electric motor 44 having a horsepower rating of at least about one-eighth (1/8) horsepower. In a preferred embodiment, each roller drive motor 44 is an alternating current motor 44 that preferably is of three phase construction having a horsepower rating of about one-half (1/2) horsepower.
To provide the necessary output torque to turn an abrasive roller 42 at a rotational speed of as low as about 100 revolutions per minute (rpm) and as fast as about 600 rpm or faster while the roller 42 is experiencing full load conditions, the motor 44 preferably is a gear motor 126 that utilizes some form of gear reduction 50 to step down the speed of the electric motor output shaft 52 to another output shaft 122 having a rotational speed falling between about 100 rpm and about 600 rpm thereby providing greater torque. Typically, for most peeling and cleaning applications, the rollers 42 are each driven at a rotational speed of between about 300 rpm and about 400 rpm. Preferably, the motor 44 includes a gear reducer 50 mounted to its output shaft 52 with the gear reducer 50 having an output shaft 122 coupled to the abrasive roller 42.
While the gear reducer 50 can be helical gear gear reducer (not shown) it preferably is a cycloidal gear reducer 124, such as the cycloidal gear reducer 124 shown in FIG. 9. The cycloidal gear reducer 124 has an outer ring gear housing 128 with a plurality of ring gear rollers and pins 130 disposed between the housing 128 and a pair of axially spaced cycloid discs 132 and 134 each of which has a plurality of circumferentially spaced apart bores 136 of oversized construction for each bore receiving a slightly smaller slow speed shaft roller and pin 138 therein coupling the cycloid discs 130 and 132 to a power transfer disc 140. Each cycloid disc 130 and 132 is supported by an eccentric roller assembly upon separate eccentric cams 142 and 144 that are both carried by a gear reducer input shaft 146 that preferably is the output shaft 52 of the motor 44 or directly coupled to the output shaft 52 of the motor 44 for rotation in unison therewith. The bores 136 are larger in size than the diameter of the slow speed shaft rollers 138 to accommodate the radial outward movement of each cycloidal disc 132 and 134 riding on the eccentric cams 142 and 144 rotated by the input shaft 146 while also being engaged by the sidewalls of the bores 136 to displace the slow speed shaft rollers 138 in a circumferential direction thereby transmitting torque from the cycloid discs 132 and 134 to the power transfer disc 140 and output shaft 122.
The input shaft 146 is rotatively supported by a first bearing 148 carried by the gear reducer housing 128 and a second bearing 150 axially adjacent the power transfer disc 140. The power transfer disc 140 is directly coupled to the output shaft 122 of the gear reducer 50 for rotation in unison therewith. The input shaft 146 terminates within the housing 128 axially adjacent the output shaft 122. The cycloid discs 132 and 134 have a periphery made up of generally wavy or sinusoidally shaped teeth 152 which are in rolling contact with one or more of the ring gear rollers and pins 130 during operation. Although a pair of cycloidal discs 132 and 134 are shown in FIG. 9, the gear reducer 124 can have more than two cycloidal discs.
Preferably, the lobe or thickest part of both eccentric cams 142 and 144 are at least slightly out of phase relative to each other so that rotation of the input shaft 146 urges one of the cycloidal discs radially outwardly relative to the other of the cycloidal discs during each rotation causing the slow speed shaft rollers and pins 138 to rotate or orbit about the input shaft 146. As a result, rotation of the input shaft 146 is transmitted via the cams 142 and 144 to the cycloid discs 132 and 134 where the slow speed shaft rollers and pins 138 communicate the motion to the power transfer disc 140 which in turn causes the gear reducer output shaft 122 to rotate. As the gear reducer output shaft 122 rotates, the abrasive roller 42 coupled to the output shaft 122 also rotates, preferably in unison. During operation, the input shaft 146 of the gear reducer 124 is rotated by the output shaft 52 of the motor 44 causing the output shaft 122 to rotate at a speed slower than the speed of the input shaft 146 for providing greater torque output to the abrasive roller 42 enabling the electric motor 44 to drive the roller 42 at a sufficient speed and with great enough torque to handle the load of fruits, vegetables and any other food products coming into contact with the roller 42 during peeling or cleaning.
Preferably, the cycloidal gear reducer 124 is constructed substantially in accordance with at least one of the gear reducers or gearmotors disclosed in catalog no. 04.301.50.007 of Sumitomo Machinery Corporation of America entitled SMCyclo® Speed Reducers & Gearmotors 3000 Series and U.S. Pat. No. 5,484,345 assigned to Sumitomo Heavy Industries, Ltd., the disclosures of both of which are hereby expressly incorporated by reference. Cycloidal gear reducers 124 are particularly well suited for the application at hand because of their ability to withstand rather large shock loads without damage, similar to what can be encountered when fruits or vegetables being peeled or cleaned come into contact with a rotating abrasive roller 42.
Preferably, the abrasive roller drive motor 44 is a three phase alternating current one-half (1/2) horsepower Leeson Waterduck Forty-two frame motor, manufactured by Leeson Electric Corporation of Waterford, Wis., having a C-face connector to which a Sumitomo model CN-FJS-4085Y-6:1 cycloidal gear reducer 124 is mounted. If desired, the abrasive roller drive motor 44 can be a gearmotor 126 having an integral cycloidal gear reducer 124. Preferably, the gearmotor 126 is a Sumitomo SM-Cyclo® gearmotor model no. 3085 having an integral cycloidal gear reducer 124 of single reduction construction and possessing a horsepower output rating of one-half (1/2) horsepower.
FIGS. 5 and 6 show the roller drive motor 44 mounted to a motor mounting plate 154 that is attached to the frame 54 outwardly of the inlet end plate 120. As is shown in FIG. 5, each motor 44 has at least two or more mounting tabs 156 that each cooperate with a fastener 158 to secure the motor 44 to the mounting plate 154. One or more mounting tabs 156 of adjacent motors 44 can share a common fastener 158 for enabling the motors 44 to be mounted in close proximity to each other. As is shown in phantom in FIG. 6, the mandrel 100 of the driven end of the roll 42 is rotatively received in a collar 160 having a radially outwardly extending flange 162 mounted by a fastener 164 to the inlet end plate 120.
In a preferred embodiment of the peeling and cleaning machine 40 shown in FIG. 2, the machine 40 has a drive motor power supply 48 that supplies electrical power to a drive motor control box 46 that distributes electrical power to each of the drive motors 44. Together, the control box 46 and power supply 48 form a motor control system 166 that supplies electrical power to each of the drive motors 44 to cause them to rotate the rollers 42 at a rotational speed suitable for cleaning food product, peeling food product or otherwise abrasively processing food product. Preferably, the control system 166 is capable of supplying electrical power to each motor 44 in a manner where the speed of each motor 44 and roller 42 can be varied and controlled independently relative to each of the other motors 44 and rollers 42, or all of motors 44 and rollers 42 can be driven at about the same speed. Preferably, the motor control system 166 is constructed and arranged such that the direction of rotation of the motors 44 and rollers 42 can be reversed during operation, if necessary.
The drive motors 44 can be controlled by the control system 166 such that alternating current electrical power from an external power source, such as a three phase alternating current power source from an electric utility, is directed through the control system 166 which processes the electrical power signal to controllably deliver three phase alternating current to each motor 44 in a manner such that the rotational speed of the output shaft 52 of each motor 44 can be controlled to relatively accurately control the rotational speed of each abrasive roller 42. If a gear reducer 50 is used, the rotational speed of the gear reducer output shaft 122 preferably will be less than the rotational speed of the motor output shaft 52.
The control system 166 includes at least one motor controller 168 that can be of programmable construction and which is represented in FIG. 2 by box 48 that has an output (not shown) leading to the control box 46 which, in turn, serves as a junction box to deliver power to the power input lead 170 of each motor 44. Preferably, the motor controller 168 is a variable frequency alternating current drive 172 that can be a Danfoss model no. 7.5 horsepower inverter model VLT3008, 175H1745 along with NEMA kit no. 175H7707 manufactured by Danfoss, Inc. of Rockford, Ill. Preferably, the auger drive motor 88 is also controlled by the motor controller 168, which preferably is a separate motor controller, such as a Danfoss VLT 2020, 195H3301 along with NEMA kit 175H7707, in a similar fashion to relatively accurately control the rotational speed of the auger 78.
Each power input lead 90 of the auger motor 88 and each power input lead 170 of each drive motor 44 are of four wire construction having three wires for each carrying one phase of the alternating current supplied to the motors and another wire that is a ground wire. Preferably, each lead 90 and 170 can be of shielded construction for minimizing the impact of electrical interference on motor operation.
FIG. 10 illustrates a second preferred embodiment of a motor control system 166' that combines auger control and roller drive motor control into a single cabinet 174 that replaces the drive motor control box 46 and drive motor power supply 48 shown in FIG. 2. The cabinet 174 has a recessed enclosure 176 with a door 178 that serves as a control panel 180 that controls operation of both the auger 78 and the abrasive rollers 42. One side of the control panel door 178 is attached to the recessed enclosure 176 by a hinge 182 and the other side of the door 178 is releasably secured to the enclosure 176 by a latch 184. When unlatched, the door 178 can be swung about the hinge 182 to reveal the components inside the enclosure 176.
On the face of the control panel 180 are controls dedicated to controlling the operation of the peeling and cleaning machine 40. The control panel 180 includes a push button electrical switch 186 for starting the abrasive roller drive motors 44 and another push button electrical switch 188 for starting the auger drive motor 88. The control panel 180 also has a push button electrical switch 190 for stopping the auger drive 88 and another push button electrical switch 192 for stopping the abrasive roller drive motors 44. As a result of the arrangement of these controls, the auger 78 and abrasive rollers 42 can be started and stopped independently of each other. To stop both the abrasive rollers 42 and auger 78 at the same time, the control panel 180 also has an emergency stop push-pull button electrical switch 198.
To control the speed of the abrasive rollers 42, the control panel 180 includes a rotary switch 194 that preferably is a variable resistor or potentiometer which can be selectively manually turned or rotated by an operator of the machine 40 to selectively speed up or slow down the rollers 42. The rotational speed of the abrasive rollers 42 preferably is reflected by a display 196 that can be an LED or LCD display which preferably displays the rotational speed of the rollers 42 in revolutions per minute.
An exemplary speed range of 10, 30, 60, and 100 is shown adjacent the abrasive roller speed control 194. The printed range shown preferably is indicative of the percentage of maximum output frequency of the variable frequency electric motor drive 172. Preferably, the output frequency of the drive can be varied between about twelve Hertz and about sixty Hertz and can be operated at a frequency as high as one hundred and twenty Hertz for controlling the speed of the abrasive roller drive motors 44 and abrasive rollers 42. The output frequency of the variable frequency drive 172 preferably is directly proportional to the rotational speed of each of the drive rollers 42.
To control the speed of the auger 78, the control panel 180 includes a rotary switch 200 that preferably is a variable resistor or potentiometer which can be selectively manually turned or rotated by an operator of the machine 40 to selectively speed up or slow down the auger 78. The rotational speed of the auger 78 preferably is reflected by a display 202 that can be an LED or LCD display which preferably displays the rotational speed of the auger 78 in revolutions per minute.
An exemplary speed range of 0, 30, 60, and 100 is shown adjacent the auger speed control 200. The printed range shown preferably is indicative of the percentage of maximum output frequency of a variable frequency electric motor drive dedicated to driving the auger motor 88. Preferably, the output frequency of the drive can be varied between about twelve Hertz and about sixty Hertz and can be operated at a frequency as high as one hundred and twenty Hertz to control the speed of the auger drive motor 88 and auger 78. The output frequency of the variable frequency auger drive preferably is directly proportional to the rotational speed of the auger 78.
FIG. 11 illustrates the motor control system enclosure 176 with its door 178 open or removed exposing the components inside the enclosure 176. Within the enclosure 176 is a power supply block 204 for bringing electrical power from an external power source, such as an electric utility or the like, to the motor control system 166'. Preferably, three phase (3φ) electrical power having a voltage of about 480 volts and able to provide an amperage of up to at least thirty amps is supplied by the external power source to the power supply block 204. Although not shown in FIG. 11, the power supply block 204 preferably also includes a disconnect switch 240 (FIG. 12) for disconnecting electrical power to the entire motor control system 166', a fuse block 242 (FIG. 12) that preferably is a 600 volt fuse block containing at least three sixty amp 600 volt fuses for preventing power spikes from damaging the control system 166', and a power distribution block to which one or more of the components further discussed herein are ultimately connected.
Referring additionally to FIGS. 12 and 13, electrical power from the power distribution block of the power supply block 204 is communicated to a step down transformer 206 that outputs electrical power at a voltage of 120 volts at its output terminals. Part of its output is supplied to a variable frequency motor drive 208 that controls operation of the auger drive motor 88 and another part of its output is supplied to a variable frequency motor drive 210 that controls operation of all of the abrasive roller drive motors 44.
Preferably, the variable frequency auger motor drive 208 is an Allen-Bradley model no. 1305 adjustable frequency AC drive (series C) manufactured by Allen-Bradley of Milwaukee, Wis., that is constructed, arranged and operates substantially as described in its user manual entitled 1305 Adjustable Frequency AC Drive (Series C) and subtitled 0.37-4 kW (0.5-5 HP), FRN 6.01 and Up, the disclosure of which is hereby expressly incorporated by reference herein. Preferably, the variable frequency abrasive roller motor drive 210 is an Allen-Bradley model no. 1336 adjustable frequency AC drive manufactured by Allen-Bradley of Milwaukee, Wis., that is constructed, arranged and operates substantially as described in its user manual entitled 1336 PLUS Adjustable Frequency AC Drive and subtitled 0.37-448 kW (0.5-600 HP), the disclosure of which is hereby expressly incorporated by reference herein.
To energize the auger drive motor 88 to start the motor 88 when the auger drive start push button 186 is pressed, the enclosure 176 has a an IEC contactor 212 that is a motor starter which causes current to be supplied to the motor 88 when the button 186 is pressed. Likewise, to energize the abrasive roller drive motors 44, the enclosure 176 has another IEC contactor/motor starter 214 that causes current to be supplied to the motors 44 when the abrasive roller drive start push button 188 is pressed. Although the motor starters 212 and 214 are of IEC construction, NEMA-type motor starters can be used. To stop both the auger drive motor 88 and the roller drive motors 44 should an emergency occur, there is a master control relay (MCR) 222 connected to the emergency stop push button switch 198.
To protect the auger motor control and drive circuitry from damage due to power transients during operation, there is a fuse block containing fuses 216. To protect various components of the roller motor control and drive circuitry from power transients, there is a pair of fuse banks 218 and 220. To further protect the circuitry, there is a fusible terminal block 224 of preferably 600 volt construction adjacent a relay 226 that controls the start and stop of the abrasive roller drive motors 44. To protect each motor 44 from overload, there is a normally closed overload protection relay 228 in electrical communication with each motor 44.
To distribute electrical power from the abrasive roller variable frequency motor drive 210 to each of the abrasive roller motors 44, the enclosure 176 has an elongate terminal block 230 having a voltage rating of 600 volts and a plurality of terminals. To cool the abrasive roller variable frequency motor drive 210 during operation, there is a fan 232 mounted by a bracket in the enclosure 176 with the fan 232 aimed at the drive 210 such that its exhaust impinges against the drive 210 when the fan 232 is operating. To admit air into the enclosure 176 when the door 178 is closed, a bottom sidewall 234 of the enclosure has a through opening with a filter 236 for removing particulate matter from air entering the enclosure 176 that covers the opening and a grill 238 attached to the enclosure 176 which captures the filter 236.
The motor control circuitry is further presented in a ladder diagram control schematic shown in FIGS. 12 and 13. As is shown in FIG. 12, two branches 1L2 and 1L3 of the inputted three phase power are directed to step down transformer 206 where the voltage preferably is stepped down to about 120 volts to supply electrical power to each of the variable frequency motor drives 208 and 210, the motor starters 212 and 214, and the auger and roller drive motor speed displays 196 and 202. Each input of the transformer 206 preferably has a fuse 244 and 246 for protecting the transformer 206. Each fuse 244 and 246 preferably is a four amp fuse. At least one of the two output legs of the transformer 206 is also equipped with another fuse 248 that preferably is a five amp fuse.
The two output legs of the transformer 206 provide electrical power to a control circuit 254 that controls operation of both the auger drive motor 88 and roller drive motors 44. Wired to both of the output legs of the transformer 206 is a fuse 250, preferably of two amp construction, a 120 volt power outlet 252, and the power input terminals of both the auger and roller drive speed displays 196 and 202. The legs of the transformer output communicate electrical power to a first branch 256 and a second branch 258 of the control circuit 254.
The emergency stop circuitry consists of the push-to-stop, pull-to-start push button switch 198, that is of double circuit construction, with the switch 198 shown in FIG. 12 in a normally closed position in an emergency stop circuit branch 260 and normally open in an emergency stop indicating circuit branch 262. When the upper portion of the switch 198 is in its normally closed position, current flows through a jumper 264 and a coil 266 of the MCR 222 which in turn energizes a relay 268 in series in branch one 256 of the control circuit 254 causing power to be supplied to the rest of the circuit 254. The jumper 264 can be removed and replaced with one or more series wired emergency stop switches (not shown) of like or similar configuration to switch 198 for enabling operation of the peeling and cleaning machine 40 to be interrupted at locations remote from the control panel 180. When the emergency stop button 198 is pushed, it closes the emergency stop indicating circuit 262 causing an indicator light 270 in the face of the button 198 to light up thereby providing a visual indication that the emergency stop button 198 has indeed been pushed.
With the emergency stop button 198 in its normal operating position (shown in FIG. 12) such that the emergency stop circuit 260 is closed, current flow through the circuit branch 260 energizes the MCR coil 266 causing the MCR relay 268 to close which, in turn, causes electrical power to be supplied to the rest of the control circuit, including the cooling fan 232, the auger drive motor and roller drive motor starters 212 and 214, and the roller drive motor variable frequency drive 210. Preferably, there is a one amp fuse 272 wired in series with the fan 232.
With the MCR relay 268 closed, electrical power is supplied to a coil 274 of the auger motor starter 212 thereby closing corresponding normally-open relays 276 (FIG. 13) of the motor starter 212 thereby enabling the auger drive motor 88 to be driven by its variable frequency drive 208. When the auger motor starter coil 274 is energized by application of electrical current, it closes a relay 276 in each of the circuit branches communicating one phase of three phase electrical power to and through the variable frequency auger motor drive 208. Likewise, when the MCR relay 268 is closed, power is supplied to a coil 278 of the roller drive motor starter 214 closing corresponding relays 280 (FIG. 13) of the motor starter 214 enabling the roller drive motors 44 to be driven by its variable frequency drive 210.
To control the starting and stopping of the abrasive roller drive motors 44, there are a plurality of normally-closed overload relays 282 in series with the roller drive motor stop push button switch 192, the roller drive motor start push button switch 186, and a motor start coil 284. A motor startup relay 286 is wired in parallel with the start switch 186 and is closed due to the coil 284 being energized when the start switch 186 is pressed. When the start button 186 is pressed, the start coil 284 also energizes another relay 290 which provides a start input to the roller motor variable frequency drive 210. The relay 286 remains closed after the start switch 186 is released causing power to be supplied to the roll drive motors 44 until the stop switch 192 is pressed breaking the circuit.
There is an overload relay 282 for each roll drive motor 44. For each drive motor 44 there is a current overload sensor 288 in series with the power supplied to the motor 44 for sensing current flow along each phase of the three phase current delivered to the motor 44 during operation and communicating with the overload relay 282 if current rises above a certain threshold. Should the current flow to a motor 44 along any phase branch become too great indicating that the motor 44 may be overheating, the overload sensor 288 will open its relay 282 stopping all of the roller drive motors 44 by stopping electrical power flow to all of the motors 44 thereby preventing motor damage.
Power is provided to inputs 20, 24, 30 and 21 of the roller motor drive 210 and to a variable frequency drive start input 19 when start relay 290 is closed by the pressing of the start switch 186. The stop button 192 preferably is of double circuit construction. When the stop button 192 is pressed, it opens the start circuit and deenergizes the start relay 286 while also stopping power to stop input 20 of the variable frequency drive 210. When no power is applied to stop input 20, the variable frequency drive 210 ceases to supply three phase power to the roller drive motors 44. When power to variable frequency drive input 20 is ceased, a stop/fault reset is executed by the variable frequency drive 210 causing it to block power flow to the motors 44.
To control roller motor speed and hence control abrasive roller speed, the drive roller speed control 194 is a potentiometer connected to inputs 1, 2 and 3 of the variable frequency drive 210. The leads from the potentiometer speed control 194 are preferably shielded. As the potentiometer 194 is rotated in one direction, it causes the variable frequency drive 210 to increase both the voltage and frequency of the three phase power supplied to each of the roller motors 44 thereby increasing their speed. As the potentiometer 194 is rotated in the opposite direction, the variable frequency drive 210 reduces both the voltage and output frequency of the three phase power supplied to the motors 44 thereby slowing their speed.
Outputs 9 and 14 of the variable frequency drive 210 are in electrical communication with the roller speed display 196 and communicates to the display 196 a signal that is preferably representative of or proportional to the rotational speed of the rolls 42. The electrical leads communicating the signal from the variable frequency drive to the display preferably is shielded.
The auger start button is connected to inputs 6, 7 and 8 of the auger motor variable frequency drive 208. When pressed, it provides a start up signal to the drive 208 causing the drive 208 to start the auger drive motor 88. When the auger stop button 190 is pressed to stop the auger 78, it breaks the circuit between input 7 and 8 of the drive 208 causing a stop/fault reset condition to occur which, in turn, causes the drive 208 to cease power flow to the auger drive motor 88. The auger variable frequency drive 208 is internally powered by the 480 volt three phase power supply.
To control the speed of the auger 78, the auger speed control 200 is a potentiometer connected to inputs 1, 2 and 3 of the drive 208. A signal representative of or proportional to the auger speed is transmitted from outputs 5 and 3 to the auger speed display 202.
Referring to FIG. 13, each phase of the 480 volt three phase power supply is connected to the R, S and three phase motor power inputs of the variable frequency drives 208 and 210. There is a fuse 292 before each three phase motor power supply input. A phase is outputted from each of the U, V and W outputs of the variable frequency drives. Preferably, each output also has a fuse 294.
Each of the roller motors 44 is wired in parallel to the outputs U, V and W of the roller motor variable frequency drive 210 such that all of the motors 44 are driven by the drive 210. If it is desired to drive each motor 44 separately, a variable frequency drive 210 can be used for each roller motor 44 with a corresponding set of controls 186, 192, and 194 for each drive 210 used. For example, if it is desired to have four rollers 42 independently controlled relative to the other five rollers 42, a bank of four roller drive motors 44 can be driven by one drive 210 along with a set of controls 186, 192 and 194 and the other bank of five roller drive motors 44 can be driven by another drive 210 along with a set of controls 186, 192 and 194 with the control circuitry for both drives 210 and banks of roller drive motors 44 constructed generally in accordance with that presented in FIGS. 10-13.
FIGS. 14-19 illustrate a rotating cage peeling and cleaning machine 40' of this invention having each of its abrasive rollers 42 driven by an electric motor 44. Preferably, the machine 40' has an auger 78 that is also driven by a motor 88, although the machine 40' can be constructed without an auger 78 providing the machine 40' is equipped with another mechanism or means for facilitating and controlling movement of food product 41 through the food product receiving chamber 76 of the machine 40'. Where an auger 78 is used to urge food product 41 through the machine 40', the abrasive roller drive motors 44 are controlled by a variable frequency drive and the auger drive motor 88 is controlled by another variable frequency drive in a manner described above and depicted generally in FIGS. 10-13.
As is shown in FIGS. 14 and 15, the rolls 42 are carried by an elongate and generally cylindrical cage 296 constructed and arranged such that the rollers 42 are journalled at each end in an end plate 118 and 120 that is rotatively carried by the frame 54 of the machine 40' and makes up the cage 296. Preferably, a plurality and at least about four rollers 42 are arranged to form the cage 296 while also forming an elongate and generally cylindrical product receiving chamber 76 inside the cage 296. Twelve motors 44 and rollers 42 are depicted in FIGS. 15 and 16. The cage 296 preferably also includes at least two elongate struts 298 that join the end plates 118 and 120 and which, along with the rollers 42, impart strength and structural rigidity to the cage 296. Preferably, the cage 296 has a plurality of circumferentially spaced apart struts 298 that extend about the periphery of the cage 296.
The abrasive rollers 42 are arranged generally in a circle defining an elongate and generally cylindrical food product receiving chamber 76 between them. The auger 78 is received in the chamber 76 and rotates during operation to urge food product 41 received in the chamber 76 from the inlet end 60 toward the outlet end 64. As is shown in FIG. 14, the auger drive motor 88 is coupled to the auger shaft 84 by a generally right angled gear reducer 300.
At the inlet end 60 of a preferred embodiment of the machine 40' shown in FIG. 14, the inlet end plate 120 has an axially outwardly extending flange 302 that defines a journal that bears against bearing rollers 304 carried by radially inwardly extending cage supporting arms 306 that are secured to or carried by the frame 54. The frame 54 remains stationary during operation. At the outlet end 64, adjacent the periphery of the outlet end plate 120 are a plurality of axially outwardly extending bearing rollers 308 that each ride on the radially inner surface of an outturned flange 310 of a cage support ring 312 that is secured to or carried by the frame 54.
At the inlet end 60, the inlet 62 comprises a stationary inlet chute 314 that funnels food product 41 that is to be processed into a rotating inlet chute 316 carried by the cage 296 which guides the product 41 into the chamber 76 where it is abraded by the rotating rollers 42 to clean the product 41 or clean and peel the product 41. Secured to and generally encircling the rotating inlet chute 316 is a generally cylindrical hub 318 that carries a sheave or pulley 320 which receives an endless flexible member 322 that is coupled to a pulley 324 on an output shaft 326 of another electric motor 328 for rotating the cage 296 about a longitudinal axis generally defined by the auger shaft 84.
The cage drive motor 328 is carried by or secured to the frame 54 of the peeling and cleaning machine 40'. The endless flexible member 322 preferably is a belt such as a cog belt or the like, but can be a chain, wire rope or another type of endless flexible member capable of transmitting rotary mechanical motion from the electric cage drive motor 328 to the cage 296 to rotate the cage 296.
Referring to FIGS. 15, 16, 18 and 19, the cage 296 can also be rotatively secured to the frame 54 at each end by a bearing ring assembly 330 that has one ring 332 secured to the frame 54 and the other ring 334 secured to an end plate with a plurality of ball or roller bearings 336 captured between the rings 332 and 334 which preferably interlock with each other. Preferably, the outer ring 334 is secured by one or more fasteners to an inwardly extending mount 338 of the frame 54 on each side of the machine 40'. Preferably, the inner ring 332 of the cage bearing ring assembly 330 is secured by a plurality of fasteners or the like to an end plate. Each end plate 118 and 120 preferably is rotatively secured to the frame 54 of the machine 40' by such a cage bearing ring assembly 330.
Preferably, the inlet end plate 120 to which the abrasive roller motors 44 are mounted can include a motor mounting plate 154 spaced axially from the end plate 120. If a motor mounting plate 154 is used, the motors 44 can be mounted to the plate 154 and the rollers 42 rotatively mounted to the end plate 120, such as in the manner depicted in FIG. 6. If desired, the motor 44 and roll bearing assembly 104 can both be mounted to the end plate 120. Other motor and abrasive roller mounting methods and mechanism are contemplated.
Referring to FIGS. 14, 15 and 17, electrical power is transferred from the stationary motor control system 166" to each of the abrasive roller drive motors 44 via a slip ring or commutator ring 340 that is constructed and arranged to distribute power to each motor 44 to rotate each roller 42 while the cage 296 is also rotating during operation. Preferably, the commutator ring 340 is rotatively carried by the auger shaft 84 such that it allows the auger shaft 84 to rotate independently of the cage 296 and ring 340 while still being able to transfer electrical power from the motor control system 166" and distribute the power to each motor 44. The ring 340 is shown in FIG. 15 secured to inlet end plate 120 by spokes 342.
Referring to FIG. 17, an exemplary commutator ring 340 is shown. The ring 340 has an inner core 344 rotatively supported on the auger shaft 84 by bearings 346 to permit relative rotation therebetween. Rotatively supported on the inner core 344 by bearings 348 is an outer core 350 which has an electric lead 170' connected to the motor control system 166". Leads 170 from each motor 44 are connected to the outer core 350 with individual leads 352, 354 and 356 for three phase power transfer extending radially inwardly to a contact ring or brush 358 at the radially inward surface of the outer core 350 each of which engages an axially aligned contact ring or brush 360 carried on the periphery of the inner core 344. Each contact ring or brush 358 and 360 preferably extends circumferentially about the core it is mounted on for continuous power transfer substantially throughout each entire core revolution.
The commutator 340 shown in FIG. 17 is constructed and arranged for independently transferring three phase electrical power from the motor control system 166" to each abrasive roller motor 44 such that independent speed control of each abrasive roller drive motor relative to each other abrasive roller drive motor is possible. However, the commutator 340 can be modified from that shown in FIG. 17 such that only three or four power input lines can make up power input lead 170' and transfer power to each motor 44 such that all motors 44 are operated at the same speed during machine operation. Of course, the commutator ring 340 can be further modified from that shown in FIG. 17 so as to group the abrasive roller drive motors into two or three banks with the speed of each motor 44 in a bank being independently controlled of the speed of the motors in the other bank or banks.
Another electrical power transfer mechanism is shown in FIG. 18. In FIG. 18, a stationary outer power distribution ring 362 is attached to the frame 54 of the machine 40' and is in electrical communication with the control system 166". Each motor has a power transfer wheel 364 with electrical contacts that bear against contacts of the power distribution ring 362 when the cage 296 rotates during operation.
Referring once again to FIG. 15, to control the auger motor 88 if an auger 78 is used, the control panel 180' of the motor control system 166" preferably has an auger drive motor variable frequency drive 208 along with appropriate controls 188, 190, and 200 for controlling the startup and rotational speed of the auger 78 and its drive motor 88. To control each of the abrasive roller drive motors 44, the control panel 180' of the motor control system 166" preferably has at least one abrasive roller motor variable frequency drive 210 along with appropriate controls 186, 192 and 194 for controlling the startup and rotational speed of the abrasive roller motors 44.
Similarly, for controlling the speed of rotation of the cage 296, the cage drive motor 328 can be controlled by one of the aforementioned variable frequency motor drives 208 or 210 or can be controlled independently by its own variable frequency motor drive. If controlled by its own variable frequency drive, the control panel 180' preferably is equipped with a cage drive motor start switch 366, a cage drive motor stop switch 368, and a cage drive motor speed control 370. If desired, the control panel 180' can also be equipped with a cage speed indicator or display 372. If cage rotation is controlled by its own motor control 370, the auger speed and speed of the abrasive rollers 42 can be controlled and adjusted independently of each other and independently of the speed of rotation of the cage 296.
During operation, a peeling and cleaning machine 40 and 40' of the invention can be used to clean or clean and peel fruits and vegetables that can include, for example, potatoes, carrots, onions, radishes, beans, tomatoes, lettuce, apples, oranges, peaches, pears and other food products 41. A peeling and cleaning machine 40 and 40' of the invention can also be used to clean or otherwise abrasively engage non-edible things like plastic parts, metal components and the like.
During operation, product 41 is introduced into the chamber 76 through the inlet 62. When it reaches the chamber 76, the product 41 abrasively engages one or more of the rotating rollers 42 causing the abrasive action between the product 41 and a roller 42 to either clean, peel, or clean and peel the product 41. Relative rotation or relative movement between the product 41 and roller 42 helps to facilitate the abrasive action between the roller 42 and product 41. The speed of rotation can be increased or decreased simply by rotating the abrasive roller drive motor speed control 194.
To control how long the product remains in the chamber 76, auger rotation can be controlled. For example, residency time within the chamber 76 can be decreased by speeding the rotation of the auger 78 or can be increased by slowing the rotation of the auger 78. The auger 78 rotates relative to the frame 54 of the machine, can rotate relative to one or more of the rollers 42 and can be rotated in a direction that is opposite the direction of rotation of one or more of the rollers 42. The speed of rotation can be increased or decreased simply by rotating the auger drive motor speed control 200.
Where the machine is a rotating cage peeling and cleaning machine 40', the cage 296, composed of the rollers 42 and end plates 118 and 120, is rotated by the cage drive motor 328 about a longitudinal axis of the machine 40' preferably while each of the rollers 42 and the auger 78 are rotating. The speed of rotation of the cage 296 can be increased or decreased simply by rotating the cage drive motor speed control 370. In this manner, the amount of centrifugal force urging food product in the chamber 76 radially outwardly against the rollers 42 preferably can be controlled and adjusted for controlling and adjusting the processing of the product 41 within the chamber 76.
When the product 41 has traveled the length of the chamber 76 it is expelled from the machine 40 or 40' out the outlet 66.
It is understood that the invention is not confined to the particular construction and arrangement of parts herein illustrated and described, but embraces all such modified forms thereof as come within the scope of the following claims.
e) discharging each of the food products from the chamber out the outlet.
2. The method of claim 1 wherein each of the rollers comprise abrasive rollers and during step d) each of the food products are treated during contact between one of the rollers and each of the food products to remove matter from the food products by abrasion.
3. The method of claim 1 further comprising providing a motor controller that is electrically connected to the roller drive motors and during step c) controllably applying electrical power to each of the roller drive motors to selectively rotate each of the rollers at a rotational speed of between about 100 revolutions per minute and about 600 revolutions per minute.
4. The method of claim 3 wherein the motor controller further comprises a control for setting the rotational speed of the rollers and during step c) setting the rotational speed of the rollers such that each of the rollers rotate at a rotational speed of between about 100 revolutions per minute and about 600 revolutions per minute.
5. The method of claim 1 further comprising providing a motor controller that is electrically connected to the roller drive motors and during step c) controllably applying electrical power to each of the roller drive motors to selectively rotate each of the rollers at a rotational speed of between about 300 revolutions per minute and about 400 revolutions per minute.
6. The method of claim 1 further comprising providing at least four cycloidal gear reducers that each receive an output shaft of one of the roller drive motors and that each have an output shaft that is coupled to a single one of the rollers and during step c) the further step of reducing the rotational speed of each roller drive motor output shaft to rotate each of the rollers at a rotational speed that is less than the rotational speed of each roller drive motor output shaft.
7. The method of claim 1 further comprising providing an auger received in the chamber, an electric auger drive motor operably coupled to the auger, and during step c) rotating the auger to urge the food products received in the chamber toward the outlet.
8. The method of claim 7 further comprising providing a first motor controller electrically connected to at least one of the roller drive motors and a second motor controller electrically connected to the auger drive motor wherein during step c) the rotational speed of the auger is controlled independently of the rotational speed of the roller operably coupled to the at least one of the roller drive motors.
9. The method of claim 1 wherein during steps c) and d) at least one of the rollers is rotated at a rotational speed that is different than the rotational speed of another of the rollers.
f) discharging the food products from the chamber out the outlet.
11. The method of claim 10 wherein during steps d) and e) the rotational speed of the rollers is independently controlled relative to the rotational speed of the cage.
3) during step d) setting the control of the second motor controller to set the rotational speed of the cage.
3) rotating the auger to urge the products inside the chamber toward the outlet.
14. The method of claim 1 wherein each of the rollers have an abrasive exterior and during step d) each of the food products is treated by contact between at least one of the rollers and each of the food products to clean the products.
15. The method of claim 14 wherein the abrasive exterior of each of the rollers is comprised of an abrasive grit and during step d) each of the food products are cleaned by abrasive contact between the abrasive grit of at least one of the rollers and each of the food products.
16. The method of claim 15 wherein during step d) the abrasive contact removes a portion of the exterior of each of the food products.
17. The method of claim 16 wherein during step d) the abrasive contact peels at least a portion of the exterior of each of the food products.
18. The method of claim 1 further comprising providing a collection pan disposed generally below the rollers and the step further comprising collecting matter removed from the food products in step d).
19. The method of claim 1 wherein there is an electric roller drive motor for each one of the rollers and during at least step c) each roller is rotated by a single one of the electric roller drive motors.
20. The method of claim 19 wherein during at least step c) each roller is independently rotated relative to every other roller.
21. The method of claim 20 wherein the rotational speed of each roller is independently controllable during at least step c).
22. The method of claim 1 further comprising providing a pair of spaced apart end plates that rotatively carry the rollers.
23. The method of claim 1 wherein each of the electric roller drive motors comprises a three-phase electric motor, the electric power supply comprises a three-phase power supply, and during steps c) and d) three-phase electric power is applied to each of the electric roller drive motors.
24. The method of claim 23 wherein each of the electric roller drive motors has a horsepower rating of at least one-eighth horse.
25. The method of claim 24 wherein each of the electric roller drive motors has a horsepower rating of about one-half horse.
26. The method of claim 1 wherein the rollers are arranged to form a generally U-shaped food product-receiving chamber and during steps c) and d) the food product-receiving chamber remains substantially stationary while each of the rollers is rotated.
27. The method of claim 1 wherein the rollers are arranged to form a substantially enclosed food product-receiving chamber that has an axis of rotation, each of the rollers has a rotational axis, and the step further comprising urging each of the rollers about the axis of rotation of the food product-receiving chamber such that the rotational axis of each of the rollers rotates about the axis of rotation of the food product-receiving chamber during at least step d).
28. The method of claim 27 wherein the substantially enclosed food product-receiving chamber comprises a generally cylindrical food product-receiving chamber.
29. The method of claim 1 further comprising providing a plurality of gear reducers that operably couple one of the electric drive motors to at least one of the rollers and during steps c) and d) the further step of reducing the rotational speed of each electric roller drive motor to rotate the at least one of the rollers operably coupled to the electric drive roller motor at a rotational speed that is less than the rotational speed of the roller drive motor.
30. The method of claim 29 wherein each of the gear reducers comprises a cycloidal gear reducer.
31. The method of claim 30 wherein each one of the rollers is operably coupled by a single one of the cycloidal gear reducers to a single one of the electric drive roller motors.
32. The method of claim 1 wherein the inlet is disposed at one end of the food product-receiving chamber and the outlet is disposed at another end of the food product-receiving chamber and the food product-receiving chamber is disposed at an angle relative to a horizontal axis such that gravity urges food product in the chamber toward the outlet and during step d) gravity urges the food product toward the outlet.
33. The method of claim 1 wherein food products are substantially continuously introduced into the chamber and food products are substantially continuously discharged from the chamber.
34. The method of claim 10 wherein each of the rollers have an abrasive exterior and during at least step e) each of the food products are treated during contact between at least one of the rollers and each of the products to remove matter from the food products.
35. The method of claim 34 further comprising providing a collection pan disposed underneath the rollers and the step further comprising collecting matter removed from the food products in step e).
36. The method of claim 10 wherein each of the rollers have an abrasive exterior and during step e) each of the food products is treated during contact between at least one of the rollers and each of the food products to clean the food products.
37. The method of claim 36 wherein the abrasive exterior of each of the rollers is comprised of an abrasive grit and during step e) each of the food products are cleaned by abrasive contact between the abrasive grit of at least one of the rollers and each of the food products.
38. The method of claim 37 wherein during step e) the abrasive contact removes a portion of the exterior of each of the food products.
39. The method of claim 38 wherein during step e) the abrasive contact peels at least a portion of the exterior of each of the food products.
40. The method of claim 10 wherein there is an electric roller drive motor for each one of the rollers and during at least step c) each roller is rotated by a single one of the electric roller drive motors.
41. The method of claim 40 wherein during at least step c) each roller is independently rotated relative to every other roller.
42. The method of claim 41 wherein the rotational speed of each roller is independently controllable.
43. The method of claim 10 wherein each of the electric roller drive motors comprises a three-phase electric motor, the electric power supply comprises a three-phase power supply, and during at least steps c) and e) three-phase electric power is applied to each of the electric roller drive motors.
44. The method of claim 43 wherein each of the electric roller drive motors has a horsepower rating of at least one-eighth horse.
45. The method of claim 44 wherein each of the electric roller drive motors has a horsepower rating of about one-half horse.
46. The method of claim 10 wherein each of the gear reducers comprises a cycloidal gear reducer and during at least step c) each of the rollers is rotated at rotational speed that is less than the rotational speed of the roller drive motor operably coupled to the roller.
47. The method of claim 10 wherein food products are substantially continuously introduced into the chamber and food products are substantially continuously discharged from the chamber.
f) discharging the food products from the chamber.
NL2005769C (en) * 2010-11-28 2013-08-21 Finis Foodproc Equipment B V A treatment device, treatment element, treatment assembly and method.
NL8402721A (en) * 1984-09-06 1986-04-01 Inst Voor Bewaring Method and device for peeling onions.
NL1020743C2 (en) * 2002-06-03 2003-12-11 Schouten Landbouwwerktuigen B Bollenpelmachine.
EP0421991A1 (en) 1991-04-17 Device for processing meat.


Presentation at the 2015 Physics Teachers Conference in the Karaoke session by Dan O'Keeffe, AIP (Vic Branch) Education Committee.
See below for other articles on participation in physics.
"Multi-layered national curriculum design principles" is a paper prepared by Neil Champion, Williamstown High School. It was published in the May/June 2009 edition of 'Australian Physics'. If you wish to comment on the paper, please go to the Forum section of this website.
A personal perspective on physics course design and assessment by Dr Syd Boydell. The 17 page document considers how these aspects have changed and not changed over the last 50 years. He also looks at what has been lost and what has been gained.
Graphs of student participation in VCE science and maths subjects up to 2017. Analysis and explanation is in the 'Participation in VCE Sciences 1972 - 2017. Prepared by Dan O'Keeffe, Vicphysics Teachers' Network.
Graphs of the participation of male and female students in Year 12 of VCE Physics, Chemistry, Biology and Psychology. The method of determining the participation is described, there is some interpretation of the graphs. The physics graph covers 1958 - 2017. Prepared by Dan O'Keeffe, Vicphysics Teachers' Network.
The article analyses VTAC data of VCE Physics students from the years 1996, 2000 and 2004 It addresses the questions: i) What are the popular tertiary courses ii) How does the popularity of these courses vary with the students' Physics results iii) How do the selections of male and female students differ iv) Into what courses are the more able students accepted v) How do the Physics results of students selected for mainstream science courses compare with other students vi) How have the answers to the above questions changed overtime Prepared by Dan O'Keeffe, Vicphysics Teachers' Network.
The data from the 'Tertiary destinations' study has been used to analyse the physics study scores of male and female students. Prepared by Dan O'Keeffe, Vicphysics Teachers' Network.
An article analysing the student participation in VCE science subjects from the 1970's until the late 1990's. Published in LabTalk in 1999. Prepared by Dan O'Keeffe, Vicphysics Teachers' Network. More up to data without analysis is available in documents listed elsewhere in this list.


On 3rd January 2012, version 2 of the Mozilla Public License (MPL) was approved by the Open Source Initiative. It is also considered to be a Free Software licence by the Free Software Foundation. Like its predecessor, the Mozilla Public License v 1.1, it seeks to impose a moderate level of 'copyleft' restriction on adaptations of code that it covers. The licence can be read at http://www.opensource.org/licenses/MPL-2.0.
Twelve years after the creation of the original Mozilla Public License, the Mozilla Foundation decided that certain issues could be usefully addressed with that licence. In early 2010 they put in place a consultation process that - much in the same manner that they developed and released software - would invite input from interested members of the public and other organisations.
Among the issues that the Mozilla Foundation wanted to address were compatibility of MPL code with code under other popular Free and Open Source Software (FOSS) licences and the clarity and US-specificity of the MPL v1.1's language. Over the course of almost two years, three alpha releases, two beta releases and two release candidates, a large community of interested parties worked to improve and modernise the licence.
The MPL v2's copyleft provision is 'weak' - meaning that it covers a subset of works that are 'based upon' its covered code. Like its predecessor, the rule which governs whether a specific adaptation must bear the MPL v2 or not is based upon file divisions within the software. Adapted files must remain MPL v2, but entirely new files may bear a licence of the adaptor's choice. The MPL v2 also allows its covered code to be incorporated into projects under a specific set of other 'secondary' FOSS licences (GNU GPLv2, GNU LGPL v2.1, GNU Affero GPL v3 and all subsequent versions of those licences), thereby expanding compatibility of software it covers.
As software which was distributed under the MPL v1.1 can automatically be distributed under the MPL v2 (thanks to section 6.2 of the former licence) the new compatibility features raised an interesting question: what if the original owner does not want this expanded compatibility, with its attendant implication that their code could end up within a project under a different licence? The MPL v2 deals with this by providing an additional notice that can be added to software it covers, stating that the author does not wish the compatibility features of the licence to be used with their code. When 'upgrading' a piece of MPL v1.1 software to MPL v2, only the original owner of the code can decide that such a notice need not be applied. If anyone other than the original owner is upgrading the licence, the notice must be included.
Also to this end, the MPL v2 has amended conditions around patent licence termination. These bring the licence into compatibility with the Apache License v2, and therefore allow Apache License v2 code to be incorporated directly into MPL v2 covered files. For both these compatibility measures it is important to realise their limitations. They allow Apache License v2 code to be used in MPL v2 programs, and MPL v2 code to be used under certain conditions in programs under various versions of the GNU GPL. They do not allow code combination in the opposite direction; for example, including GNU GPLv3 code in an MPL v2-licensed program, or MPL v2-licensed code in an Apache License v2 program would still be impossible without additional permissions from the software's owners.
As well as expanded compatibility, the MPL v2 provides amended legal language to make it accord better with uses and enforcement outside the US. In rewriting, the licence has also been made shorter and clearer.
What makes the MPL 2 different from MPL 1.1?
The Mozilla Public Licence version 2 - An Overview by Rowan Wilson is licensed under a Creative Commons Attribution-ShareAlike 4.0 International License .


Controversial road restrictions costing tens of thousands of pounds will be ripped up and replaced – as campaigners celebrate a "victory for common sense".
Traffic islands and bollards installed in Drayton Park, Highbury, costing £80,000, will be removed and a new layout installed.
Islington Council has conceded that the scheme, which is designed to stop lorries using the street as a cut-through, is flawed and has launched a consultation on a new design.
The measure has united drivers, cyclists and pedestrians in opposition since it was implemented in May – and has already seen multiple accidents.
Caroline Russell, chairman of pedestrian group Islington Living Streets, said: "It's a fabulous victory for common sense, but I would much rather we had not had to run the campaign at all.
"It's a tragic waste of money and a shame they went ahead in the first place.
Last Tuesday a driver was stuck trying to navigate the layout, which squeezes cars up to the curb. The car had to be lifted away as police closed the lane.
Simon Jary, 45, a publisher of nearby Whistler Street, who photographed the scene, said: "The whole thing is an expensive mess and a danger to pedestrians, cyclists and motorists, and now they are changing it again.
A motorist flipped onto a bollard days after the scheme was completed in May.
The council said it didn't know how many accidents have happened, but it is not aware of any injuries. It also said the cost of the redesign is yet to be calculated.
Cllr Andy Hull, Labour member for Highbury West ward, said: "The way it was executed left a little to be desired, but it's good that we're open to people's feedback when we receive it.
Cllr James Murray, Islington Council's executive member for housing and development, said: "We are proposing to separate cyclists from the main traffic lanes, and introduce extra pedestrian crossings.


The ArtZone is located within Edmonton Green Shopping Centre opposite Edmonton Green British Rail Station connecting Liverpool Street via Seven Sisters BR and London Underground Station to the South and Enfield Town, Cheshunt and Broxbourne BR stations to the North; it has a modern Bus Terminal with many bus routes going across North London.
Once inside the Shopping Centre, head to the Market Square, take the lift or stairs to the 1st floor, then along the balcony to THE ARTZONE, which is located above SUPERDRUG.
BY CAR– 5 minutes from the North Circular Road (A406), from Great Cambridge Road (A10) or Mollison Avenue (A5005) to Fore Street.
BY TRAIN - Edmonton Green BR station - from Liverpool Street mainline station and Seven Sisters Station (Victoria Line Underground & BR) from the South and Broxbourne, Cheshunt and Enfield Town from the North.


The art of fusing glass dates back 4000 years to the Middle East. Each of the pieces designed by Beames Designs is cut and kiln fired in their studio in Kingston, NY. At a temperature of 1400˚F, the glass pieces fuse together, the edges round, and the surface takes on a brilliant gloss. Air bubbles and variations are both the nature of glass and the beauty of the handmade process.


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What a year it has been! We hope you and your families are staying safe during this pandemic. Even with COVID-19, Ripon continues to excel by holding hybrid classes and testing students. Congrats to the faculty and staff for being incredibly flexible and ingenious so that students could continue to thrive.
In mid-February you should have received the Ripon Magazine and if you look at page twelve and 15, you will see two of our classmates, NASIF ROGER '07 and ASHLEY NUTER RUSS '07, featured for their work. Way to represent Ripon and the Class of 2007! You can always stay up today on Ripon-related news by visiting ripon.edu/news.
If you haven't done so already, please consider making a donation to Ripon College. Any amount is impactful and our overall participation percentage is vital in so many ways for Ripon. In 2020 our class participation rate was 19.05%. Let's all work together to get this above 25% in 2021. Ripon's annual giving day, known as #OneDayRally, will be held on Wednesday, April 28.
Now it is time for some exciting updates from your classmates:
JODI RABAS BURNS '07 is are expecting baby #2 in May! She also just built an addition on to her office to be able to hire another doctor and take on an intern this fall. Jodi misses getting an "easy riser" for breakfast from The Pub!
MARA EVANS '07 of Grand Rapids, Michigan, is a Certified Nurse Midwife (CNM) at SpectrumHealth.
AMANDA LIETHEN GLASS '07 of Random Lake, Wisconsin, and her husband Michael are expecting an addition to their family in August, joining big brothers Matthew (14) and Theodore (2). To the disappointment of the boys, this addition is not expected to be either a puppy or a pirate. Amanda is the Associate Director of Advancement Services and Data Analyst at Ripon College and has been working remotely since March 2020. While grateful to not have a nearly three hour commute to the office, she misses seeing people outside of Zoom meetings.
KATIE BRAUN JOHNSTON '07 was the president of the Racine Lighthouse Brigade Band Boosters where she enjoyed over 100 kids flourishing in the marching band and competitions. She recently got out of social services and found a love for residential painting and furniture refurbishing. Also, she recently started selling cars at Frank Boucher and is hoping to help them study consumer psychology to better their training program. In 2013 she was bilaterally implanted with cochlear implants as she lost her hearing altogether. Her daughters will be 17 this coming July. Both have part-time jobs and are straight-A students. One wants to go into biomedical engineering and the other has a love for music but may go into law. Katie's husband continues to work into his 12th year as a sous chef for Benchmark Hospitality contracted with the Johnson Foundation. In her spare time, Katie and her family foster mastiffs and she volunteers with the dog rescue. Katie is beyond proud of her daughters!
PATRICK KERSTEIN '07 of Portland, Oregon, is currently a Postdoctoral Researcher at the Vollum Institute at Oregon Health and Science University in Portland, Oregon. His recent research has identified a new cell type involved in vision and was published in the journal Cell Reports.
BEN KONECNY '07 of Greeley, Colorado, transitioned to the head of staff role in December of 2020 at First Congregational Church in Greeley, Colorado.
ADAM KRUEGER '07 of Providence, Rhode Island, recently transitioned from Uber to Grubhub where he oversees logistics and restaurant operations. He still works with students and faculty at Harvard Business School. Besides work, Adam enjoys spoiling his niece and nephew, gardening, traveling, and theatre marathon weekends in NYC.
TRACY ENGELMANN LACANNE '07 started her own dental office in May of 2018. She started out only working two days per week but in three short years, she has gotten so busy that she is in the process of buying and remodeling a building to be able to continue expanding the practice.
TYLOR LOEST '07 and wife Katie added to their family with the birth of their son, Quincy Charles on October 15, 2020.
LIZ LEACH MORRELL '07 of Fond du Lac, Wisconsin, was a recipient of the Fond du Lac Young Professional's 2020 Future 5 Award. She is currently the Executive Director of The Arc Fond du Lac, a human service organization that empowers adults and youth with intellectual and developmental disabilities to become independent and integrated into the community through advocacy, education, training, and support.
MEGAN PIOTROWSKI MANIS '07 of Manitowoc, Wisconsin, is the Chief Customer Officer at Roydan Enterprises and has been working hard with her husband RYAN MANIS '08 to transition the business into an ESOP (Employee Stock Ownership Plan) company this spring. Other than working hard on the business, Megan and Ryan enjoy traveling with both kids for their competitive swim meets and spending more time at their cabin with a flexible work-from-home schedule.
TRACY MATTHIAS '07 of Green Lake, Wisconsin, is the owner of Lotus Root Yoga LLC (based in Ripon) and is approaching its fifth year! They are now offering online classes in addition to studio classes, special events, and retreats. Navigating the pandemic has been interesting and she is grateful that her small business is located in a tight-knit and supportive community like Ripon! Maintaining or developing a personal wellness practice like yoga has never felt more relevant.
ZACH NORTON '07 started a new position with Raymond James in November 2019 and Associates as a Senior Registered Client Service Associate. He also passed the FINRA supervisory level Series 9 and 10 examinations late last year. Zach is hoping to purchase a home and resume traveling in earnest later in the year.
CHRIS REED-WADDELL '07 and spouse, Yuliya, are finishing their tour of service in Shenyang, China in July with the U.S. State Department. They will then be returning to the U.S. for training before their next assignment in Moscow, Russia this fall.
ASHLEY NUTER RUSS '07 was featured in September on the photoblog Humans of New York and shared on social media. A snippet from a Ripon College news story states, "Russ shared her experience of growing up deaf and the isolation and rejection that she felt. She met her husband, STUART '07, at Ripon, and in her interview, she tells the poignant story of how they met and communicated by writing notes to each other."
JORDYN RUSH '07 of East Norriton, Pennsylvania, left the 9-5 world and now runs The Fussy Cutting Quilt Shop where she creates custom quilts and other sewn creations. Jordyn also serves as Operations Coordinator for Gateway Horseworks, a non-profit organization that provides Equine Assisted Psychotherapy services. She lives outside Philadelphia, Pennsylvania with her partner, Nick, and their puppy, Arlo.
JOLENE RUEDEN SCHATZINGER '07 of Ripon, Wisconsin, continues to work at the best College with the best alums, which of course is our alma mater, Ripon College, where she is the associate director of engagement. Since this past April, she has been serving on Ripon's City Council helping to strengthen town-gown relations. She is looking forward to our 15-year Class Reunion next summer, where she hopes as many of you as possible will make it back home to Ripon to celebrate together. Lastly, she is happy to have recently celebrated her spouse, Henrik's, American citizenship.
HILARY SMITH UYHELJI '07 is the co-author on the following publication: Davis, J.T. and H.A. Uyhelji. 2020. Aviation and the Microbiome. Aerospace Medicine and Human Performance 91: 651–661.
LINDSAY SPINDLER ANDERSON '07 of Saint Croix Falls, Wisconsin, recently took a position teaching 6th-grade math and public speaking at St. Croix Falls Middle School in St. Croix Falls, WI. She also coaches Forensics and is the director of the middle school plays/musicals.
We are not sure where the time has gone, but it is time to start planning our 15-year Class Reunion! After all, kids born in 2000 can now legally drink. YIKES! If you are interested in volunteering or have ideas for activities, please reach out to one of us. We are forming a Reunion Volunteer Committee, and we would love to have all interested classmates involved! Please contact one of us, your Class Agents, if you want to be involved. More information will be coming, but get excited for our Class Reunion in June 2022!
Good news regarding Alumni Weekend! Alumni Weekend 2021 will be unlike anything we've ever seen with two distinct summer weekends of Ripon alumni programming for us. No matter how you'd like to connect, virtually or in person, the Office of Constituent Engagement is developing a variety of activities to continue to follow CDC, Fond du Lac County and College guidelines in both June and August. Full schedules, lodging, and programming details will be posted soon to www.ripon.edu/alumni-weekend.
Thank you for all the updates, classmates! Please keep sending them to one of us at any time throughout the year. We are now very sad to share the news of the passing of one of our classmates who was taken from us much too soon.
MATTHEW R. "NIGEL" KENNY '07 of Orland Park, Illinois, died Jan. 29, 2021. At Ripon, he majored in politics and government and participated in Student Senate, football, and as president of Phi Delta Theta. He worked at Xtra Lease in Chicago and was a White Sox fan. He enjoyed political debates, yard work, and motorcycles. Survivors include his wife, Kate; one son and one daughter.
This sobering news helps us to realize how important keeping our connections strong really is. We do hope you can join us for next summer's 15th Class Reunion.
Be well, and we look forward to seeing you all very soon!
ADAM KRUEGER '07
LINDSEY KREYE HEIL '07
STACY KRUSA TEACHOUT '07
LIZ LEACH MORRELL '07

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