US3098512A - Debarking machine - Google Patents

Description

July 23, 1963 c. w. KENDRlCK 3,098,512

DEBARKING MACHINE Filed Sept. 4, 1959 4 Sheets-Sheet 1 326 560 ava J 5 INVENTOR July 23, 1963 c. w. KENDRICK 3,09

DEBARKING MACHINE Filed Sept. 4, 1959 4 Sheets-Sheet 2 IIHIIIIIIIIIIHHII 3/ INVENTOR ATTORNEYS I. f? I y 3, 1963 c. w. KENDRICK 3,

DEBARKING MACHINE Filed Sept. 4, 1959 4 Sheets-Sheet 3 IN V EN TOR. 64a ///@/me/a July 23, 1963 c. w. KENDRICK 3,

DEBARKING MACHINE Filed Sept. 4, 1959 4 Sheets-Sheet 4 INVENTOR (5/21 ///1%me/a wzww ATTORNEYJ m 4 /2 m M The present invention relates to improvements in post debarking machines of the kind having a rotatable drum with bark peeling members pivotally carried adjacent the periphery of the drum. 'It more particularly relates to a specific drum support and drive arrangement, blade mounting and actuating mechanism and the portable nature of the complete debarking machine.

Although peeling type debarking machines have been previously used, generally they require some relatively expensive or complex drive arrangement and the means for engaging and driving the post through the drum usually involves providing substantial pressure between the feed rolls and the logs which is not always compensated properly relative to the size and weight of the logs being peeled which, of course, effects the feed action of the feed rollers. Previously known devices have utilized centrifugally responsive Weights which tend to vary the force of the bark peeling blades against a log being driven through the knife assembly drum. Insofar as is known, most of such centrifugally responsive devices utilize a resilient connection between the centrifugal weight and the blade member and, in some cases, this resilient connection is adjustable. Nevertheless, whether it is adjustable or not, the presence of such a resilient connection in a machine which is subjected to rugged, hard usage is just one other factor requiring shutdown and replacement. The more simple centrifugally responsive peeling blade construction of the present invention is an improvement over such prior art assemblies.

Although portability is normally merely a matter of reducing the size of an item and placing it on wheels or in some manner providing for its adaptability to easy transportation from location to location, in this instance portability has been found to be a very definite asset even within a mill yard, inasmuch as the debarking machine may be hauled by a tractor within the mill yard from pile to pile of unbarked posts and pulp logs, the tractor power in such case being readily available to furnish the power from one of its power takeofis to drive the peeling drum and feed rollers of the portable debarking machine. Furthermore, the portable machine of this invention can be easily pulled by a small vehicle into a forest and the posts and poles clebarked at the site of the cutting, leaving the bark chips spread on the forest floor to help replenish the forest land. Disadvantages of prior art debarking machines often resided in the complex drive trains which in many cases have utilized chain or belt drives in close proximity to the peeling drum. The primary disadvantage of chain and belt drives close to the peeling drum is that during operation bark chips fly and fall in the area immediately around the drum, often jamming in the chains or belts and causing machine breakdowns or shutdowns.

Previously known machines for debarking posts and poles, insofar as applicant is aware, generally cannot completely clean the post of the cellular membrane between bark and wood. Since this membrane is impervious to materials used in treating such posts, whenever the debarked post is to be treated the post must be subjected to a further operation to assure that all of the impervious membrane is removed. The machine of the present invention effectively removes all of the bark and the impervious membrane with negligible, if any, destruction of the wood under that layer.

Accordingly, a primary object or" the present inven- 3,ll98,5l2 Patented July 23, 1963 tion resides in the provision of a novel relatively simple yet extremely rugged post debarking machine.

A further object resides in the provision of a novel simple post debarking machine having common drive means to the peeling drum and feed rolls together with provision for independently controlling the transmission ratio to the peeling drum and to the feed rolls and having an input connection adapted to be connected to the power drive device.

A further object resides in a novel combination rotatable mounting and power transmission device for a debarking peeling drum assembly.

Still another object resides in the provision of a novel debarking peeling drum assembly with input and output feed roller devices mounted for self adjustment to the size of a post being fed into the machine. In conjunction with this object, it is a further object to provide multiple drive paths to the input and output feed rollers operable through a common transfer gear housing.

Another object resides in the provision of a novel drum type of post deba'rker in which the drum is rotatably mounted with resilient give in both an axial and radial sense relative to a normal axial and radial position.

A still further object in conjunction with the preceding objects resides in the provision of an equilateral rubbertired drive wheel arrangement providing a position and rotatable mounting for a channel shaped annular rim on a debarking peeling drum assembly and wherein at least one of the rubber-tired wheels is drive connected through a transmission mechanism having an input connection adapted to be connected to a power driven device Still another object resides in providing a rotatable knife drum assembly having at least one bark peeling member movable toward and away from the surface of the log, the bark peeling member being centrifugally pressed against the log in response to centrifugal forces developed by rotation of the drum and having a counterbalance weight having a positive connection with the bark peeling member. In connection with this object, it is a further object to provide'an abutment stop device on the drum for. each of the bark peeling members adjacent their respective pivots and adapted to be abutted by an associated peeling member to prevent radial inward swinging movement of the bark peeling member to the axis of the drum so that a plurality of such bark peeling members cannot move into engagement with each other.

In connection with the preceding object, it is a further object to provide a curved blade, bark peeling member having one end pivoted on a dog leg shaft, one leg which is p votally mounted on the inner periphery of a peeling drum rim parallel to the drum axis and its other leg extending transversely to a radius through the axis of the drum and having a counterweight slipped over and maintained in selectively adjust-able position on the second dog leg, and an abutment plate member rigidly secured to the dog leg shaft and adapted to engage the outer side of and bias the peeling member inwardly when the drum is rotated and the counterweight develops centrifugal force.

A still further object resides in the provision of a novel preliminary infeed centering and guiding mechanism for posts being introduced to the primary infeed and guiding rollers, which adapts the debarking machine to an automated operation wherein a conveyor belt can feed logs into the machine.

Further novel features and other objects of this invention will become apparent from the following detailed description, discussion and the appended claims taken in conjunction with the accompanying drawings showing a preferred structure and embodiment, in which:

FIGURE 1 is a perspective view illustrating an embodiment of the portable debarking machine hitched to the rear end of a tractor, a part of which can be seen;

FIGURE 2 is a simplified side elevation view of the peeling drum and the three rubber rimmed mounting wheels, one of which is a drive wheel;

FIGURE 3 is a section view taken on line 3-3 of FIGURE 2;

FIGURE 4 is an enlarged detail view illustrating the input feed rollers in front of the peeling drum assembly, the weights being deleted trom the drum for clarity;

FIGURE 5 is an enlarged detail view of the peeling drum assembly as seen from the front with the centrifugally responsive weights and peeling member actuators shown;

FIGURE 6 is a section taken on line 66 of FIGURE 5 illustrating the mounting of a bark peeling or removing member on the drum rim;

FIGURE 7 is a detail exploded perspective showing part of the peeling wheel, one blade and the associated centrifugal weight;

FIGURE 8 is a schematic view or the drive train illustrated in FIGURE 1;

FIGURE 9 (on sheet 2) is a section view through a weight illustrating its components and the manner in which it is assembled on a jig plate;

FIGURE 10 is a schematic illustrating the relationship between the blade peeling end and a post being peeled;

FIGURE 11 is an enlarged view of the blade peeling end to show the desired edge curvature;

FIGURE 12 is a schematic side view illustrating a sec ond embodiment of the debarking machine in which a preliminary post centering mechanism is utilized ahead of the inlet feed and guide rollers, and in which leaf springs are used in lieu of coil springs to bias the feed rolls against the posts;

FIGURE 13 is a front detail view illustrating the preliminary feed roll, guide roll, trough land equalizer linkage; and v FIGURE 14 is a schematic view somewhat like FIG- URE 8 illustrating the use of a small self contained en gine on the portable machine and also illustrating a means to provide an additional drive takeofi for the preliminary centering feed roll.

Machine Chassis and Frame With reference to the drawings, the portable debarking machine 10 is best illustrated in FIGURE 1 wherein the machine is illustrated as having its draw bar 12 coupled to the hitch (not shown) of a tractor 14. Drive power for the debarking machine is furnished from a power takeoff at the rear of tractor 14 through a drive shaft 16 universally coupled by coupling 18 to an input stub shaft 2i on the portable machine 10.

Debarlcing machine 10 consists of a base chassis 22 constructed of a series of longitudinal channel beams 24, 26, 27, diagonal front end braces 28 and 29 and cross braces 30 and 31. The middle longitudinal channel 12 extends completely through the chassis and its forward end constitutes the draw bar 12 for the portable debarker. Secured in a conventional manner under the chassis 22 is a straight axle (not shown) which rotatably journals ground engaging wheels 34.

The front of the debarking machine is the side which faces the viewer in FIGURE 1 and is disposed at the right hand side of the machine chassis 22. Extending in spaced apart and vertical relationship from the chassis channel 26 are two heavy channel members 36 and 38. A pair of spaced apart intermediate vertical channel members 40 and 42 are vertically disposed on the middle chassis beam 24 and secured rigidly thereto as by welding. A rear set of spaced apart vertical channel beams 44 and 46 are rigidly welded to the rear longitudinal chassis channel 27 in alignment behind the front vertical channels 36 and 38.

Peeling Mounting Assembly A debarking peeling drum 50 is mounted with its axis horizontally disposed normal to the longitudinal chassis beams 24, 26 and 27 and spaced essentially midway of the height of the vertical support beams 36-46. The axis of drum "50 is located to extend midway between the spaced apart sets of vertical channel beams, and the drum 5%) is ro-tatably maintained in a fixed position by cooperation between its channel rim and three equi laterally arranged rubber- tired wheels 52, 54 and 56. The drum 50 and the three wheels 52, S4 and 56 are essentially co-planar and disposed in the space between the front vertical channels 36 and 38 and the intermediate set of vertical channels 40 and 42. Wheel 52, near the front of chassis 22, constitutes a powered drive wheel and accordingly has its hub 53 secured in a conventional manner to the drive flange of a driving axle, to be later described. The other lower wheel 54 is an idler wheel rotatably mounted by conventional wheel bearings (not shown) on a non-driving lame which can be rigidly secured on top of and transverse to the center longitudinal chassis channel 24 by welding or by any conventional clamping device.

As can be seen in FIGURE 1, the peeling drum 5%) has its annular periphery formed with a channel shaped cross section which fits over the treads of both the driving tire on and the tire 62 on idler wheel 54. The upper idler wheel 56 is rotatably mounted on a fixed axle 64 which extends laterally midway between the intermediate vertical channels 4d and 42 and rear vertical channels 44 and 46. Axle 64- is rigidly secured as by welding to support blocks '66 and to cross channels 68, 69 and 713. The two cross channels 68 and 69 are firmly clamped in a horizontal disposition to the intermediate set of vertical channels it? and 42 by bolts 72, whereas the rear horizontal cross channel 70 is secured by bolts 74 to the front flanges of the rear set of vertical channels 44 and 46. These bolts can be secured in slots cut in the front flange of channels 44 and 46, permitting vertical adjustment of the rear horizontal cross beam 78. The two front cross beams 68 and 69 can be vertically adjusted by loosening the bolts 72. In this manner, axle 64- of the upper idler wheel 56 can be vertically adjusted to provide pressure of its tire 76 against the drum 50 which equaliz/es again-st the driving wheel 52 and lower idler wheel 54. Cooperation between the tires and the peeling drum rim maintains the drum in both axial and radial positions.

As illustrated, wheels 52, 54 and 56 are conventional truck wheels carrying pneumatically inflated tires. It is to be understood that, in lieu of the tires 60, 62 and 76, solid rubber rims could be utilized on all three of the equilaterally arranged drum supporting and driving wheels. However, in such case the cushioning effect of the pneumatic tires on the peeling drum, in both an axial and a radial direction, would not be present. Specific details of the debarking drum and its plurality of peeling blade members will be described hereinafter, it being apparent at this point of the description that a log to be debarked is introduced coaxial through the drum 56 from the front of the machine shown in FIGURE 1.

Feed and Guide Mechanism When a log is introduced into the debarking machine, an operator places the log on support roller 80 which has a channel shaped circumference tending to center any log placed thereon and headed in toward the peeling drum 50. Support roller 80 is rotatably journaled on a stub axle 82 fixed in the end of a pivotally mounted lever arm 84 made of heavy channel beam. The rear end of arm 84 has a small plate 86 secured thereto as by bolts, plate 86 having an aperture therein which is pivotally disposed over the end of an equalizer shaft 88, the equalizer shaft 88 in turn being pivotally mounted horizontally across the front flanges of the front set of vertical channel members 36 and 38 in pillow block bearings 90 and 92 bolted to the vertical channels 36 and 38. Plate 86 is maintained on the end of shaft 88 by a collar 94 which is secured as by a set screw to the equalizer shaft 88. The support roller 80 and its mounting lever 84 are resiliently supported by a heavy coil tension spring 96, one end of which is hooked into a spring anchor 98 secured on the outside of vertical beam 36. The other end of spring '96 hooks into a length of a chain use having an end anchored in the support roller lever 84 adjacent its front end. When light weight logs are placed on the support roller 80 and rolled horizontally toward the debarking drum Sit, they should be essentially coaxial with the deb-arking drum 50. When heavier logs are placed on the support roller 80, the spring force of coil spring 96 should be such as to permit a downward movement of lever 84 due to the weight of the log just enough so the heavier log will be maintained in a horizontal position essentially coaxial with the debarking drum 50. Although this type of preliminary support is inexpensive, the preferred preliminary infeed support is as shown in FIGURES 12 and 13, which will be later described.

As the leading end of a log is moved toward the debarking drum 50 it will engage between two lateral guiding rollers 192 and 104 having a concave cross section periphery. These two rollers 102 and 16'4- are spring loaded to the position illustrated in FIGURE 1 and the end of a log introduced between the two rollers will shift both of the rollers equally about an offset vertical support axis to permit passage of the log, while the force of the spring loading on rollers 102 and 104 and an equalizing linkage 1115 will tend to maintain lateral centering of the log. As the log passes between these lateral guide rollers, the rollers move toward a position intermediate the toothed feed rollers (see FIGURE 3).

The support and spring loading mechanism for both of the two rollers 102 and 164 are identical and only one set will be described. Roller 1112 is rotatably mounted on a vertical short stub shaft 106 which projects upwardly at the free end of a pivotally mounted lateral plate 198. Roller 162 is maintained on the stub shaft by means of a washer and a nut 110 The pivoted end of lateral plate 11. 8 includes a vertical mounting shaft 112, the ends of which project through bearing collars (or pillow block bearings) 114 and 11-6 Welded or bolted on the inside of the associated vertical beam 36. Shaft 112 is maintained axially in journaling position in the collars 114- and 116 by suitable collars 118 rigidly fastened to the projecting ends of the shaft 112 as by set screws.

Resilient biasing of the roller 1132 is provided by a wire spring 121) which has two legs encircling upper and lower portions of shaft 112, a bight which engages the rear side of lateral plate 11 58, and two free legs which are disposed under a T-anchor 122 which is welded or otherwise secured to the front flange of vertical channel 36. As before noted, the roller 104 is mounted in an identical manner on the inside of the right hand front vertical channel 318. It is herein noted that an identical set of lateral guide rollers 124 and 126 are disposed between the intermediate vertical channels 41 and 42 providing lateral guide on the outlet side of the debarking drum these two lateral guide outlet rollers 124 and 126 being mounted in a manner as described for roller 1112. The equalizer linkage 165 (FIGURE 2) consists of horizontal bars 127 and 128 welded to the upper ends of lateral guide roller support shafts and having their adjacent ends articulatively connected by link plates 129.

Disposed behind the lateral inlet guide rollers 1112 and 164, on horizontal axes midway between the front set of vertical channels 36 and 38 and the inlet side of the debarking drum 50, are two inlet feed and log gripping rollers 130 and 132, preferably of cylindrical shape. Each of these feed rollers 135i} and 132 hasplural rows of sharp steel teeth 134 rigidly secured in their periphery intermediate the ends of the rollers. The horizontal axes of each of the rollers 130 and 132 are respectively disposed equidistances above .and below the axis of the debarking drum 50 and the rollers are journaled in an equalizing assembly, as will now be described. i

The equalizing support for the input feed rollers and 132 includes the aforenoted lower equalizer shaft 88 and an upper equalizer shaft 14% having its ends projected through and pivotally mounted in pillow blocks 142 and 144 secured to the front flanges of vertical channels 36 and 38 above the lower equalizer shaft pillow blocks 90 and 92. Two lever arms 1146 and 148 are rigidly secured to the lower equalizer shaft 3% as by welding and extend rearwardly toward the deba-rking drum 50. The ends of these two lever arms 146 and 148 journal a horizontal lower input feed roll shaft 150 which is axially maintained in position by collars 152 and 154 disposed on the inner sides of lever arms 146 and 148 and secured as by set screws to the shaft 150. Intermediate the two lever arms 146 and 148, the feed wheel 132 is non-rotatably secured as by a spline disposed in the keyway 156. Feed r-oll 132 can be axially secured on shaft 150' by suitable set screw arrangements. As seen in FIGURE 4, the right hand end of feed roll drive shaft 150 projects beyond the vertical beam 38 and carries one half of a universal fitting, the other half 162 being secured to the end of :a driven shaft 164, as will be more fully described hereinafter.

The upper equalizer shaft 140 also has two rearwardly projected lever arms 168 and 170 rigidly secured thereto as by welding. The extremities of these two lever arms 168 and 170 rotatably carry the driving shaft 172 for the upper input feed roll 130, which shaft is axially maintained in the lever arms 168 and 170 in a manner similar to that previously described for the lower feed roll shaft 159. As seen in FIGURE 4, the right hand end of upper feed roll shaft 172 also terminates in one half 174 of a universal fitting, the other half 176 of which is secured to the end of a driven stub shaft 178. Rotation of the two shafts 164 and 178 in opposite directions results in opposite directional rotation of the two input feed rolls 132 and 130 and the feed roll teeth 134 will grip and drive a log, the end of which is introduced into abutment with the input side of the feed rolls. The teeth of these feed rolls also firmly grip the log and prevent rotation of the log as it enters the debarking drum 50.

As the log is drawn between the two feed rolls 130 and 132, the rolls must spread apart in order to accommodate varying diameters of logs which are being debarked. To accommodate this spreading apart of the two feed rolls, and still maintain a vertical relationship of the path of the log so the log will be introduced coaxially through the debarking drum 50, equalizing linkages interconnect between the two equalizing shafts 88 and 140. These linkages can be clearly seen in FIGURES 1 and 3, a set of these equalizers being disposed adjacent each set of ends of the two equalizer shaifts. The equalizer set has one lever arm 1S2 rigidly secured to the end of the upper equalizer shaft 140 and depending downwardly and a second lever arm 184 rigidly secured to the end of lower equalizer shaft 8t: and extending upwardly. The adjacent free ends of the two lever arms 182 and 184 are articulatively interconnected by a set of short link members 186 pivotally connected to the ends of the lever arms 1&2 and 184 by pins 188 and 190 respectively. Each equalizer set is identical to the one just described and will so interconnect the equalizing shafts 88 and 140 that any movement upwardly of the upper feed roll 130 must result in a similar downward movement of the lower feed roll 132.

To provide a strong resilient bias on the equalizing linkage tending to maintain the feed rolls biased toward each other with sufficient force to maintain a grip sufficient to force a log through the peeling drum 50, and also maintain the log against rotation, each of the upper lever arms 168 and has forward extensions 192 and 194 rigidly secured thereto by welding, the extensions being bridged by a heavy plate 196 which is interconnected as by a chain 198 to the forwardly extended end 260' of a heavy coil spring 202. The rear end of the heavy coil spring 202 has one of the coils clamped between two anchor plates 26/4 and 206 supported on a cross bar 208 having its ends rigidly secured to the upper ends of the front set of vertical channel beams 36 and 38, as by welding. The heavy nature of coil spring 20-2 tends to resiliently resist any downward bending deflection which will be caused if a log spreads the feed rolls 130 and 132 apart. Thus the teeth 134 of the two feed rolls will be firmly pressed into engagement with a log being fed into the debarking drum 50 by the resilient bias of coil spring 202. An alternative leaf spring biasing arrangement as shown in FIGURE ll2 can be utilized if desired.

A similar biasing and equalizing arrangement is provided for a set of upper and lower outfeed rolls 212 and 214- which include drive shafts 216 and 218 respectively, connected through universal fittings to driven stub shafts 220 and 222 respectively. These two shafts 22d and 222 also have opposite directions of rotation arranged so that a log coming out of the rear of the debarking drum 50 and passing between the upper and lower outfeed rolls 212 and 214 will be engaged and driven between the intermediate vertical channel members 40 and 42. The log passes onto a support tray 224 which is mounted for limited pivotal movement on a rocking shaft 226 having its ends journaled in pillow block-s 228 rigidly secured as by bolts to the rear flanges of the rear set of vertical support channels 44 and 46. As a log is ejected from the rear of the debarking machine and slides over the tray 224, an operator will receive the completely debarked log and carry it to an appropriate stacking pile.

Drive Mechanism As was briefly noted in the preceding description, one of the debarking drum mounting wheels 52 is power driven and the four input stub shafts 164, 178, 220 and 222 to the log feed and gripping rolls 130, 132, 212 and 214 are also power driven. To this end, a double transmission arrangement is provided as an integral part of the portable debarking machine. The aforenoted input stub shaft 2%] to the debarking machine is a part of this power transmission and, as has been described, is connected, through universal fittings and drive shaft 16, to a power takeoff shaft on the rear end of tractor 14. It is to be understod that an engine or other power source (see FIGURE 14) could be mounted on the portable chassis, if desired, but so long as a tractor is used to move the machine, the tractor power takeolfs are readily available and reduce the cost of the debarking machine itself. On the other hand, if a small 4-cylinder gasoline engine is provided on the portable machine, it could be hauled into forests with small automotive vehicles which do not have auxiliary power takeoffs.

Referring to FIGURES 1 and 8, input drive shaft 29 is the input member to a primary change speed transmission 236 which can provide a straight through drive, neutral and several step down speed ratios to an output shaft 238. Output shaft 238 terminates in a pinion gear 240 which meshes with a ring gear 242 mounted coaxial with and drivingly connected to drive axle 244 for the peeling drum drive wheel 52. Ring gear 242 can be directly non-rotatably fastened on axle 244 or, as in the prototype of this machine, can be the ring gear on a conventional automotive differential in which one of the two axle drive gears is locked out and the other is splined to the drive wheel axle 244. In any event, the primary transmission 236 will directly control the speed of rotation of the peeling drum 50.

Primary transmission 236 will also indirectly control the speed of the log feed rolls 130, 132 and 212, 214 through a drive V-belt 246 which connects between a small diameter pulley 248, non-rotatably mounted on primary transmission output shaft 238, and a large diameter pulley 250 non-rotatably secured to shaft 252. Shaft 252 is the input shaft to a secondary transmission 254, which can also provide a straight through drive, several step down drive speed ratios, neutral and reverse to the feed mechanism. The secondary transmission output shaft 256 non-rotatably carries a chain drive sprocket wheel 253 which, through an endless chain 260, drives a sprocket Wheel 262 secured on an input shaft 264 of a series of drive transfer gears which are mounted in a case 266. This second transmission enables reduced feed speeds and also permits reverse of the feed in the event the large end of a post jams the debarking drum. Note: the maximum rate of feed should be correlated with the drum rotaton so the feed distance which occurs during one revolution of the drum does not exceed the width of the blade peeling edge multiplied by the number of peeling blades.

The transfer case input shaft 264 projects through the case 266 and its other end 268 constitutes a drive connection for the lower input feed roll 132, connected through a universal coupling and shaft 270 to the stub shaft 164. Shafts 270 and 164- interconnect in a slidable splined fit. A gear 272 non-rotatable on transfer case input shaft 264 meshes with an identical gear 274 on a second output shaft 276 which is connected through a universal coupling to shaft 278. Shafts 27S and 178 interconnect in a sl-idable splined fit to provide a drive for upper input vfeed roll 130. The universal couplings and slidable fittings in the drive connections between transfer gear case 266 and the input feed rolls 139 and 132 permit the vertical shifting movement of the feed rolls to accommodate variations in sizes of logs being peeled. An idler gear 282 in transfer case 266 meshes with gear 274 and a third drive gear 284 which in turn meshes with a fourth drive gear 286. Gears 284 and 286 are identical in size and tooth number with transfer gears 272 and 274. Gear 284 is secured on an output shaft 288 to drive outlet feed roll 212 and gear 286 is secured on an output shaft 290 to drive outlet feed roll 214. The connections between shaft 288 and roll 2 12 and shaft 290 and roll 214 include universal couplings and slidable splined connections, as has been described for the input feed roll drive connections, to permit shifting of the outlet feed roll axes as they accommodate the changing diameters of the logs. Note, all feed rolls 130, 132, 212 and .214 will rotate at the same speed since the four gears 272, 274, 284 and 286 are identical, and the speed of the feed can be varied independently of the peeling drum speed by means of the secondary transmission 254. By using cylindrical feed rolls, the varia tions in diameters of posts being debarked will not effect the feed rate desired. Of course, it will be understood that the overall input drive speed can be varied by the speed at which the tractor engine is operated.

Peeling Drum The peeling drum 50 is a unitary subassembly which, as has been described, is supported solely between the three rubber- tired wheels 52, 54 and 56 (FIGURES 1 and 2) of which wheel 52 is positively driven through the primary transmission 236. Sufficient pressure of the drive wheel tire 69 on the rim of drum 50 to assure a positive driving engagement can be provided by the aforedescribed vertical adjustment of the upper idler wheel 56.

Drum 50 is essentially a heavy steel rim 3%, having its external peripheral surface provided with an annular channel 3&2 which receives the tread of the three rubbertired wheels 52, 54 and 56, providing a confining track which cooperates with the wheels to maintain the peeling drum in an axial position between the input and outlet feed rolls.

Carried on the inner periphery of the drum rim. 3th is a group of bark removing members or peeling blades 304. Peeling can be accomplished with one blade. However, it is preferable to have three or more equi-angularly spaced blades to aid in keeping the log centered in the s,oss,512

drum and for purposes of balance of the drum, the disclosed drum 5t} including five such blades MP4. Of course, it will be understood that, as the number of blades is increased, the feed rate can be increased without increasing drum rotation. FIGURES 5, 6 and 7 illustrate the peeling blades 3%, their mounting arrangement and the coaction of the centrifugally responsive weight assemblies with each blade, and FIGURES l and 11 show further blade details.

Each blade 394- is pivotally secured at one end to the inner periphery of rim Still and to provide such mounting, a pair of axially spaced apart, apertured, steel plate ears 3% and 308 are secured by welding to the inner side of rim 3th? for each blade 304. The apertures 310 and 312 (FIGURE 7) respectively, in the two ears 3% and 3% are aligned and the axis of alignrnent is parallel to the drum axis. Blade 3% is a curved tempered steel strip, the blades in the prototype being made from leaf spring material, with a pivot mounting eye 31 rolled in its outer end and has a width dimension at the pivoted end enabling a free close fit of the eye 314 between the ears 306 and 3% where it is pivoted on one leg 316 of a 90 dog leg shaft Ealfi. Leg 316 projects through aperture 316; in the front ear 3%, through the blade eye 314 and through the aperture 312 in rear ear 3%.

Shaft le g 316 is axially positioned in the ears 3% and 3% by engagement of a blade abutment fitting 32%, which is welded on leg 316 adjacent the bend of shaft 318, with the front side of ear 3%. A nut 322 and lock nut 32% (FIGURE 6), threaded on the end of shaft leg 316 maintain the shaft in a free fitting pivotal disposition in the two ears. Blade abutment fitting 3% extends transverse to the shaft leg 316 to a position adjacent the peeling blade 3% and terminates in a lug 3 26 which projects behind the outer side of the blade 304, as best shown in FIGURES and 6.

In the non-operating position of the peeling blades 304-, their peeling end edges 339 may be disposed approximate but not quite on the drum axis (FIGURE 5). This limit position is deter-mined by a small curved strip of steel plate 332 (FIGURE 7) welded to the ears 3% and 308 and having an abutment edge 334 adapted to engage the inner surface of blades 3% adjacent its eye 314 when the blades 3% reach their inner position, as in FIGURE 5. These stops 332 prevent the peeling end edges from engaging and possibly locking and becoming dulled when no log is passing through the drum 5%. In this non-peeling position of the blades 394, the other leg 336 of dog leg shaft 318 is inclined approximately thirty (30) degrees outwardly of tangency to the rim 3% with the blade abutment lug 326 in engagement with the blade 394. Disposed on the dog-leg shaft leg 336 is an apertured weight member 338 whose position relative to the pivot leg 316 can be varied by adjusting a nut 34% and lock nut 34% threaded on the end of leg 336. With such an arrangement, rotation of the drum 59 causes centrifugal force to act on weights 333, tending to pivot the dog leg shafts 313 counterclockwise, and biasing the blades 3M- inwardly by engagement between the abutment lugs 326 and blades 3524. When a log has been inserted into the drum 5t and the blades 3% pivot outwardly, the weights 338, depending upon the size of the log, will be swung inwardly to a point preferably where the shaft leg 336 is approximately tangent to the rim, at which location essentially all of the centrifugal force developed by the weights about the shaft pivot leg 316 will be applied through the moment arm provided by the dog le-g lever to force the blades 3% inwardly. The structural correlation between the dog leg arm 336 and the blade engaging lug 326 should not be such as to permit the weight to swing inward beyond a position where it would be overbalanced by the centrifugal forces on the blade 304, and to this end, an adjustable fitting can be provided between the abutment member 329 and shaft I0 leg 31o so the relationship can be varied tfor use with batches of different sized logs being debarked.

Peeling blade 3% has its inner end 330 formed with a bevel 343 terminated in edge 344 (see FIGURE 11) which is disposed substantially parallel with the drum axis and is narrower than the width of blade 304 at its eye 314. The blade 3% is curved from peeling end 330 toward the eye 314 in the direction of drum rotation (see FIGURE 5) and the curvature is such that the inside portion of each blade 304 immediately adjacent the peeling edge 331i forms an angle at (FIGURE 10) and is approximately radial to the axis of drum 50 when the blades are in a position to peel a post approximately 3-4 inches in diameter. This relationship becomes slightly inclined toward the direction of rotation when larger diameter logs are being peeled. However, for the most satisfactory operation, the angle or should not be obtuse and should be as close to 90 as practicable, although larger diameter logs have been satisfactorily peeled when the angle a approximates 60. The rear edge 346 of blade 334 is straight (FIGURE 6), whereas the front edge 358 inclines from end edge 33% toward the front of drum 541 in the direction of rotation and is beveled as shown in FIGURE 6. This inclination and beveling of the front edges 3% of blades 304 is not necessary but may aid somewhat in a more rapid climbing of the blades 3% to the periphery of a post when rotating in the non-operative position of FIGURE 5 and the end of a log is introduced into abutment against the front edges of the blades.

FIGURE 11 illustrates, in enlarged detail, the nature of the actual peeling edge 344 of blade 304. It is not a knife edge, which would tend to scrape and splinter the wood cells of the post, but is ground to a small curvature permitting the blade to ride smoothly over the wood cells yet, at the same time, peeling and scraping all bark and all portions of the impervious membrane layer away from adjacent the wood cells. As an example, in the prototype machine, blades 304 were made from automotive leaf spring approximately 4 inch in thickness, the bevel 34-3 was approximately forty-five degrees and the radius of curvature of edge 344 was approximately inch.

The even angular spacing of the blades 364 tend to hold the log centered in the drum 5%) and the peeling edges 330 of the rotating blades 3M- will scrape all of the bark off the log with minimum damage to the wood as the input feed rollers and 13 2 force a log through the drum and outlet feed rollers 212 and 214 complete the feed movement. The resilient nature of the spring lea-f blades 3% prevents splintering and tearing of the wood cells around knots in a log, which destructive splintering does occur in debar-ker machines which use heavy and/or rigid blades. If the bark is hard to remove, depending upon the type of log and/or weather conditions, the speed of the drum can be increased by increasing the speed of the tractor engine or by changing the transmission 236, at the same time decreasing feed roll speed by means of the secondary transmission 254. If desired, springs can be added between the weights 338 and rim 3% to keep the blades inward when not rotating and also to aid the centrifugal forces on the weights.

Blade weights.It is quite important for smooth and trouble free operation of the debarking drum that the masses of the blades, the weights and their structural connections be accurately positioned for proper balance about the axis of the drum 5i and in this connection, a relatively simple method to make accurate weights 338 was devised. FIGURE 9 illustrates the use of a weight fabricating jig 35h vmade from a flat metal block with a machined annular depression 352 in one face providing a central pilot boss 354 and a concentric annular shoulder 3 56 at the outer edge of depression 352. A short length of a small diameter pipe 358 is spigoted snugly over the pilot boss .354 and a similar length of larger diameter pipe 36d spigoted within the annular shoulder 356. This arrangement assures substantial concentricity of pipes 358 and 56b and while so positioned in jig 359, the space between the two pipes is filled with molten lead 362. When the lead 362 hardens, the inner pipe 358 is reamed, or bored, to a desired accurate size permitting a slip fit of the weight 3 33 on the leg 336 of dog leg shaft 318.

Modified Feed and Power Mechanism FIGURES l2, 13 and 14 illustrate a modified form of the debarking machine in which the heavy overhead coil spring 2l2 (FIGURE- 3), used to bias the inlet feed rollers, has been replaced by a leaf spring 376 secured to the lower portion of the machine. The essential difference in the inlet feed roll equalizing linkage is that lower links 184' (corresponding to links 1'84) which are rigidly secured to lower feed roller pivot shaft 38, have extended lower arms 372 and a round rod 374 is rigidly secured to bridge the extremities of lower arms 372. Rod 374 constitutes an abutment for the free end of leaf spring 370 which is flexed to exert a force on the feed roller equalizing linkage tending to bias the upper and lower feed rollers 13b and 132 toward each other.

The fixed end of spring 379 is clamped between a block 376 and a flange 378 of a mounting bracket 38% rigidly secured to lower frame beam 31'. When larger diameter, and hence heavier, logs pass between the feed rollers 13% and 13-2 the movement of the equalizer linkage shifts the spring abutment rod 374 a greater distance against leaf spring 374% to deflect spring .370 a greater distance which increases the spring bias to affect the added weight of the log. One advantage of this modified spring arrangement is that the weight of the log, which is applied through the lower roller, is now applied directly through the lower roller support to the spring without going through the entire equalizer linkage.

A similar leaf spring arrangement is provided for the outlet feed rollers 21 2' and 214, wherein the lower lever arms 382 have rearward extrusions 384 bridged by a cross rod 386 which flexes a leaf spring 388 clamped to one of the rear vertical frame channels 46'.

This latter embodiment includes a preliminary post centering feed device in lieu of the support roller 80 used in the FIGURE 1 embodiment. As clearly illustrated in FIGURES 12 and 13, the centering device includes an upper toothed roller 4% and a lower spool shaped roller 401. The upper toothed roller 400 is non-rotatably secured to a driven shaft 4492 and journaled in the ends of forwardly extended lever arms 494 and 495 which are rigidly secured, as 'by welding, to a rock shaft 406, while the lower spool shaped roller 401 is rotatably journaled on a shaft 4438 which is rigidly secured in the ends of forwardly extended lever arms 410 and 411 which in turn are rigidly secured, as by welding, to rock shaft 412.

To provide pivot journalling for the two rock shafts 406 and 416, immediately ahead of the corresponding rock shafts for the inlet feed rollers 130 and 132', sets of double pillow block bearings 420, 422, 424 and 426 are provided on the front vertical columns 36' and 38 in lieu of the single pillow block bearings 142, 144, 9b and 22 shown in FIGURE 4. Each end of the rock shafts 406 and 412 are interconnected by equalizing linkages 430 and 432, offset outwardly from the vertical channels 36' and 33' a distance sufiicient to clear the equalizing linkage of the inlet feed rollers (omitted from FIGURE 13 for clarity). Equalizing linkages 430 and 432 operate in precisely the same manner as do the previously described feed roll equalizing linkages, assuring that the centering 'rolls 400 and 401 will move in conjunction to accommodate posts of varying diameters and maintain the axis of any size post in an essentially centered relationship relative to the debarking drum 50'. The two centering rollers are biased toward each other by a coil tension spring 434 having suflicient force to main- I2 tain the toothed roller 4% in at least a light drive engagement with a post inserted between rollers'40tl and 401.

Immediately ahead of the free spool shaped roller 401 is a V-shaped trough 438 having side flanges 440 and 442 welded to respective beams 444 and 446, which in turn are rigidly secured, as by welding, to the non-rotatable shaft 498. The trough 438 will thus shift downwardly upon separatory movement of the two preliminary centering rollers 4%" and 40-1 when any post is inserted therebetween.

As will be apparent from the showing of FIGURE 13, if the end of a post of any diameter capable of going through the debarking drum is placed into the trough 433, the side walls of the trough will center the end of the post relative to the center line of the debarker drum and as the post is shifted into the machine, it will be engaged by the center rows of steel drive teeth 450 and 452 of the upper roller 400. These two rows 450 and 452 of gripping teeth are spaced slightly further apart than the teeth. of the regular feed rollers and tend to maintain a later-ally centered relationship as the post is drawn between rollers 4% and 401 by powered rotation of upper roller 4%. As soon as the post enters between the two rollers 49%? and 401, they separate and in so doing the guide trough 438 is lowered away from engagement with the post so the post will roll on the lower spool roller 491.

Drive power is imparted to rotate the upper roller 40%) at the same rotational speed as the primary feed rollers are rotated, through universally connected drive fittings similar to those described for the feed rollers. FIGURE 14 illustrates one way in which drive power is imparted from shaft 264 through an auxiliary drive sprocket wheel 46%, sprocket chain 4532 and driven sprocket wheel 464. Sprocket wheel 464 is connected through universal fittings and a slip joint to roller shaft 402 in the manner described for each of the feed rolls illustrated in FIGURE 8.

This preliminary centering device offers several distinct advantages over the single support roll embodiment. It overcomes the need for an operator to force the post between the inlet lateral guide rollers. No effort is required on the part of an operator to guide the post into the feed rollers which are quite a distance from the support roller. It eliminates the need for the operator to continue to hold the post as it passes through the inlet feed rollers, the drum, and into engagement with the output feed rollers. Also, and of considerable importance, is the fact that such a preliminary centering and guide device enables the debarking machine to be used in an assembly line arrangement in which a conveyor belt can feed a post lengthwise into the centering trough 438 and the machine will automatically accept and debark the post.

Referring again to FIGURE 14, it will be noted that the primary change speed transmission 236 and input shaft 20 (of FIGURE 8) have been replaced by an auxiliary engine E, to illustrate schematically how such modification, which has been previously referred to, can be easily accomplished. In using an auxiliary engine modification, the primary change speed transmission can be omitted and variation in throttle control over the speed of the engine can be used to vary the speed of rotation of the peeling drum, the feed speed rate being varied by means of the previously referred to secondary transmission.

The foregoing description discloses an operative portable debarking machine with a relatively simple selectively variable drive train to the peeling drum and to the feed rolls. It also discloses a simple, reliable and extremely rugged combined drive and mounting arrangement for a peeling drum assembly and improved direct acting centrifugally responsive elements for creating debarking forces on the peeling blades of a peeling drum.

The invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiment is therefore to be considered in all respects as illustrative and 13 not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come the meaning and range of equivalency of the claims are therefore intended to be embraced therein.

What is claimed and desired to be secured by United States Letters Patent is:

1. A post debarker comprising: a frame structure; at least three wheels journalled on said frame structure disposed with their axes in spaced apart parallel relationship arranged substantially equilaterally with the Wheels in a co-plan'ar relationship; a bark peeling blade assembly comprising a channel rimmed drum rotatably supported and axially positioned solely by engagement of its rim with each of said plurality of wheels, a plurality of peeling blades pivotally mounted on the said drum and having centrifugally responsive means engaging each of said blades providing a centrifugal biasing force upon rotation of said drum tending to force said blades toward the center of said drum; means comprising portions of said wheels and said drum rim providing resilience in the axial and radial positioning of said drum; means including at least one of said wheels for rotating said drum; and means on said frame structure for guiding and driving a log through the center of said drum.

2. A portable post debarker comprising: a wheeled base frame; a vertical support structure; at least three rubber rimmed wheels disposed with their axes in spaced apart parallel relationship arranged substantially equilaterally with the wheels in a co-planar relationship; a bark peeling lade assembly comprising a flanged rim drum rotatably supported solely by engagement with each of said plurality of rubber rimmed wheels, a plurality of curve-d peeling blades with inclined leading edges having one end pivotally mounted adjacent the periphery of said blade assembly drum, and centrifugally responsive means engaging each of said blades and providing a centrifugal biasing force upon rotation of said drum tending to force said blades toward the center of said drum; log guide means foreand aft of said blade assembly; log driving means including equalizer means to automatically vertically center the log, fore and aft of said blade drum assembly; lateral log guiding rollers spring biased toward each other and adapted to engage a log as it enters the front of said rotating blade assembly and as it exits from the rear of said rotating blade assembly; transmission means mounted on said frame providing drive power to said leg driving means and to at least one of said wheels; and means on said transmission means adapted to be connected to a power source.

3. A post debarker comprising: a support; a rotating peeling drum assembly mounted on said support for rotation about a horizontal axis and having peeling blades with cooperating centrifugally responsive members tending to force said blades inwardly toward the center of said drum assembly; upper and lower toothed post driving polls on horizontal parallel axes disposed forwardly of said rotating drum assembly and adapted to guide a post essentially coaxially into said rotating drum assembly; a rear set of toothed post driving rolls on horizontal parallel axes disposed rearwardly of said rotating drum assembly and adapted to receive a post from said drum assembly essentially coaxial of said drum assembly; power transfer means on said support connected to and adapted to drive said fore and aft sets of rolls at a similar rate of speed; spring biased equalizing means mounting said rolls on said support whereby the two rolls of each set can be spread vertically apart to automatically accommodate various diarneter posts and still maintain a vertically centered relationship of said post to said drum assembly; at least two sets of concave guide rolls for lateral guiding of a post, a set disposed in front and a set dis osed in back of said .drum lassembly; spring means connecting and biasing the lateral guide rolls of each set toward each other; and equalizer means carried by said support and 14 mounting each said set of lateral guide rolls whereby the two rolls of each set can be spread laterally apart to automatically accommodate various diameter posts and still maintain a horizontally centered relationship of said post to said drum assembly.

4. A post debarker comprising: a frame structure; at least three pneumatically tired wheels journalled on said frame structure disposed with their axes in spaced apart parallel relationship arranged substantially equilaterally with the wheels in a co-planar relationship; a bark peeling blade assembly comprising a drum rotatably supported and axially positioned solely by engagement with each of said plurality of tired wheels, a plurality of peeling blades pivotally mounted on the said drum and having centrifugally responsive means engaging each of said blades providing a centrifugal biasing force upon rotation of said drum tending to force said blades toward the center of said drum; means on said frame structure for rotating said drum; and means on said frame structure for guiding and driving a post through the center of said drum, comprising toothed feed rollers in front of and behind said drum.

5. A post debarker as defined in claim 4 wherein a preliminary post centering means for guiding and forcing a post into said feed means is mounted on said frame structure in front of said peeling blade assembly and said means for guiding and driving a post through said drum.

6. A post debarker as defined in claim 5, wherein said preliminary centering means comprises a V-shaped trough to initially receive and center a post, equalized preliminary feed and support rollers and means to lower the trough from engagement with a post when the post end enters between the preliminary feed and support rollers.

7. A rotating post peeling drum assembly adapted to be rotatably mounted and driven in a post deb-arking machine, comprising: a circular rim; a plurality of curved peeling blades having one end pivotally mounted adjacent the periphery of said rim and each of said blades curving inwardly opposite to the direction of rotation and terminating in a beveled dull edge essentially parallel to the axis of rotation of said rim; the leading edge of the curved portion of each blade being inclined from the front of the drum toward the rear and inwardly; and means adapted to engage each blade adjacent its pivot point comprising a plurality of centrifu-gally responsive means, each said centrifugally responsive means comprising an adjustable weight, a pivot shaft mounting said weight and pivotally connecting an associated one of said peeling blades to said rim, and a blade abutment member rigidly secured to said pivot shaft and adapted to transfer a biasing force from the pivot shaft to said associated blade tending to force the blade inwardly toward the axis of said rim upon development of centrifugal forces in said Weights during rotation of said rim.

8. A post debarker comprising: a support structure; a bark peeling blade assembly comprising a rotatable drum, a plurality of peeling members carried by said drum and means creating a biasing force tending to force said blades toward the center of said drum; resilient cushioning means for rotatably and axially positioning said drum; means for radially driving said drum; and means for non-rotatably driving a post through the center of said drum; said drum having a channel shaped rim and said drum positioning means and driving means comprising at least three co-planar, pneumatically tired, equilaterally spaced wheels journalled on said support structure surrounding said rim with the wheel tires frictionally engaging in the channel of said rim and axially and rotatably radially positioning said drum rim, with means to power rotate at least one of said wheels.

9. A post debarker comprising: a support structure; a bark peeling blade assembly comprising a rotatable drum, a plurality of peeling members carried by said drum and means for creating a biasing force on said peeling members tending to force said peeling members toward the center of said drum; resilient cushioning means carried by said support structure and rotatably mounting said drum with limited radially resilient give and limited axially resilient give of said d-rum relative to said support structure, said cushioning means engaging and radially and, axially positioning said drum at least at three equally spaced apart positions around said drum; means, carried by said support structure and engaging said drum for rotatably driving said drum; and means carried by said support structure for non-rotatably driving a post through the center of said drum; each of said peeling members being a blade made of leaf spring steel and constituting a spring leaf.

10. A post debarker comprising: a support structure; a bark peeling blade assembly comprising a rotatable drum, a plurality of peeling members carried by said drum and means for creating a biasing force on said peeling members tending to force said peeling members toward the center of said drum; resilient cushioning means carried by said support structure and rotatably mounting said drum with limited radially resilient give and limited axially resilient give of said drum relative to said support structure, said cushioning means engaging and radially and axially positioning said drum at least at three equally spaced apart positions around said drum; means carried by said support structure and engaging said drum for rotatably driving said drum; means carried by said support structure for non-rotatably driving a post through the center of said drum; and preliminary post centering means mounted on said support structure in front of said drum and said means for driving a post through said drum for guiding, centering and forcing a post into said post driving means.

11. A post debarker comprising: a support structure; a bark peeling blade assembly comprising a rotatable drum, a plurality of peeling members carried by said drum and means for creating a biasing force on said peeling members tending to force said peeling members toward the center of said drum; resilient cushioning means carried by said support structure rotatably mounting said drum and resiliently radially and resiliently axially positioning said drum; means carried by said support structure and engaging said drum for rotatably driving said drum; means carried by said support structure for non-rotatably 16 driving a post through the center of said drum comprising separable driven toothed rollers ahead of said drum and resiliently loaded equalizing means mounting said toothed rollers to permit equalized separation as a post feeds therebetween; and preliminary post centering means mounted on said support structure in front of said drum and said means for driving a post through said drum for guiding, centering and forcing a post into said post driving means comprising a set of separable rollers and a V-shaped trough disposed ahead of said feed rollers with at least one of said preliminary rollers being a driven toothed roller, and resiliently loaded equalizing means mounting said preliminary rollers to permit equalized separation of said rollers as a post passes therebetween.

References Cited in the file of this patent UNITED STATES PATENTS 1,406,047 Mikshel Feb. 7, 1922 1,436,373 Walk Nov. 21, 1922 1,887,908 Tidblad Nov. 15, 1932 2,283,863 Achterman May 19, 1942 2,505,168 Augustin Apr. 25, 1950 2,625,968 Eklund et a1 Jan. 20, 1953 2,646,092 Kolpe et al July 2-1, 1953 2,694,425 Sko-glund Nov. 16, 1954 2,779,363 Laughton J an. 29, 1957 2,794,466 Lefiler June 4, 1957 2,803,142 Kauffman Aug. 20, 1957 2,815,776 Annis et al Dec. 10, 1957 2,843,168 Lunn July 15, 1958 2,857,945 Brundell et al Oct. 28, 1958 2,861,446 Patterson et al Nov. 25, 1958 2,888,966 Mongan et al June 2, 1959 2,893,453 Brundell et al. June 7, 1959 2,958,350 Peyton Nov. 1, 1960 2,983,291 Dick May 9, 196-1 FOREIGN PATENTS 313,213 Great Britain June 10, 1929 215,700 Australia June 11, 1958 90,080 Germany Jan. 2, 1897 1,056,394 France Oct. 21, 1953 537,677 Canada Mar. 5, 1957

Claims (1)

1. A POST DEBARKER COMPRISING: A FRAME STRUCTURE; AT LEAST THREE WHEELS JOURNALLED ON SID FRAME STRUCTURE DISPOSED WITH THEIR AXES IN SPACED APART PARALLEL RELATIONSHIP ARRANGED SUBSTANTIALLY EQUILATERALLY WITH THE WHEELS IN A CO-PLANAR RELATIONSHIP; A BARK PEELING BLADE ASSEMBLY COMPRISING A CHANNEL RIMMED DRUM ROTATANLY SUPPORTED AND AXIALLY POSITIONED SOLELY BY ENGAGEMENT OF ITS RIM WITH EACH OF SAID PLURALITY OF WHEELS, A PLURALITY OF PEELING BLADES PIVOTALLY MOUNTED ON THE SAID DRUM AND HAVING CENTRIFUGALLY RESPONSIVE MEANS ENGAGING EACH OF SAID BLADES PROVIDING A CENTRIFUGAL BIASING FORCE UPON ROTATION OF SAID DRUM TENDING TO FORCE SAID BLADES TOWARD THE CENTER OF SAID DRUM; MEANS COMPRISING PORTIONS OF SAID WHEELS AND SAID DRUM RIM PROVIDING RESILIENCE IN THE AXIAL AND RADIAL POSITIONING OF SAID DRUM; MEANS INCLUDING AT LEAST ONE OF SAID WHEELS FOR ROTATING SAID DRUM; AND MEANS ON SAID FRAME STRUCTURE FOR GUIDING AND DRIVING A LOG THROUGH THE CENTER OF SAID DRUM.

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