U.S. patent number 3,832,808 [Application Number 05/377,826] was granted by the patent office on 1974-09-03 for abrasive belt-type lumber planing machine.
This patent grant is currently assigned to Timesavers, Inc.. Invention is credited to Fred W. Kiser.
United States Patent |
3,832,808 |
Kiser |
September 3, 1974 |
ABRASIVE BELT-TYPE LUMBER PLANING MACHINE
Abstract
An abrasive belt-type lumber planing and dressing machine in
which the workpiece is fed horizontally through the machine by the
top stretch of an endless conveyor belt, to have its upwardly
facing surface acted upon by a contact drum-supported endless
abrasive belt traveling at high speed, and in which a downwardly
biased infeed pressure shoe holds the workpiece down on the
conveyor belt along a transversely extending area just ahead of the
zone of contact between the workpiece and the abrasive belt, the
pressure shoe being mounted in the machine by a parallelogram
linkage which maintains the toe of the pressure shoe at
substantially the same distance from the zone of contact between
the workpiece and the abrasive belt despite changes in the
elevation of the pressure shoe caused by variations in workpiece
thickness.
Inventors: |
Kiser; Fred W. (Hopkins,
MN) |
Assignee: |
Timesavers, Inc. (Minneapolis,
MN)
|
Family
ID: |
23490669 |
Appl.
No.: |
05/377,826 |
Filed: |
July 9, 1973 |
Current U.S.
Class: |
451/300 |
Current CPC
Class: |
B24B
21/12 (20130101) |
Current International
Class: |
B24B
21/04 (20060101); B24B 21/12 (20060101); B24b
021/08 () |
Field of
Search: |
;51/135R,137,138,139,141 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Smith; Al Lawrence
Assistant Examiner: Godici; Nicholas P.
Claims
The invention is defined by the following claims:
1. In an abrasive belt-type lumber planing machine wherein
workpieces to be sized are fed horizontally through the machine by
the platen-supported top stretch of a conveyor belt mounted in the
frame of the machine, with the top surface of the workpiece in
contact with the underside of a contact drum-supported abrasive
belt, and wherein a downwardly biased pressure shoe has a toe
portion that engages the workpiece and holds it down on the
platen-supported stretch of the conveyor belt along a zone that
extends transversely across the workpiece closely adjacent to the
zone of contact between the workpiece and the abrasive belt, the
improvement whereby upon up and down movement of the pressure shoe
resulting from variations in workpiece thickness, the toe of the
pressure shoe moves in an arc substantially concentric to the
contact drum, so that the pressure shoe exerts downward pressure
upon the workpiece at substantially the same distance from said
zone of contact regardless of variations in workpiece thickness,
and which improvement comprises
a parallelogram linkage mounting and connecting the pressure shoe
with the frame of the machine, two of the four axes of said linkage
being fixed with respect to the machine frame and the other two
being fixed with respect to the pressure shoe, and all of said axes
being parallel with the contact drum axis.
2. In an abrasive belt-type lumber planing machine, the improvement
defined in claim 1 wherein said parallelogram linkage by which the
pressure shoe is mounted comprises:
A. a first cross shaft extending transversely across the
machine;
B. coaxial bearings fixed with respect to the frame of the machine
and having the end portions of said first cross shaft journalled
therein;
C. a first pair of spaced apart parallel links fixed to said first
cross shaft and projecting radially therefrom in the same
direction, to have their free ends swing in an arc about the axis
of said first cross shaft;
D. a second cross shaft extending transversely across the machine
in parallel spaced relation to said first cross shaft,
said second cross shaft having its end portions connected to the
free ends of said pair of links;
E. bearing means on the pressure shoe having said second cross
shaft journalled therein;
F. a second pair of parallel links;
G. first coaxial pivot means rockably connecting the same end of
each of said second pair of links with the machine frame; and
H. second coaxial pivot means rockably connecting the other end of
each of said second pair of links with the pressure shoe.
3. In an abrasive belt-type lumber planing machine, the improvement
set forth in claim 2, further characterized in that
1. the axes of said first cross shaft and of said first coaxial
pivot means lie in a substantially horizontal plane spaced upwardly
of the pressure shoe, and
2. the axes of said second cross shaft and of said second coaxial
pivot means lie in a substantially horizontal plane spaced
downwardly from said other substantially horizontal plane.
4. The abrasive belt-type lumber planing machine of claim 3,
wherein the toe of the pressure shoe lies in a plane spaced a short
distance below said plane containing the axes of the second cross
shaft and the second coaxial pivot means.
5. The abrasive belt-type lumber planing machine of claim 4,
wherein all of said links are at all times substantially parallel
to one another and project downwardly from the axes of their
connections with the machine frame at an inclination away from the
toe of the pressure shoe and at an angle to the vertical that is
less than 45.degree., so that the pivotal connections of the links
with the pressure shoe move along arcuate paths having both a
vertical and a horizontal component as the elevation of the
pressure shoe changes, and
wherein the means by which the pressure shoe is biased downward
comprises a compression spring reacting between the machine frame
and the pressure shoe and arranged to urge the pressure shoe
horizontally towards the contact zone between the contact
drum-supported abrasive belt and the workpiece.
6. In an abrasive belt-type lumber planing machine, the improvement
set forth in claim 5, further characterized by stop means to limit
the spring produced movement of the pressure shoe.
7. In an abrasive belt-type lumber planing machine, the improvement
set forth in claim 6, further characterized by other stop means to
adjustably limit spring opposed movement of the pressure shoe.
8. In an abrasive belt-type lumber planing machine, the improvement
set forth in claim 5, wherein near each end of the pressure shoe
there is a substantially vertical wall fixed with respect to the
machine frame,
wherein the pressure shoe has an endwise projecting rigid arm on
each end thereof located between said vertical wall and the contact
zone,
wherein two compression springs reacting through the parallelogram
linkage hold the toe of the pressure shoe down on the workpiece,
and
wherein said compression springs react between said substantially
vertical wall and the endwise projecting rigid arm at each end of
the pressure shoe.
9. In an endless belt-type sanding machine having a sanding head
with an endless power driven sanding belt and conveyor means to
carry workpieces horizontally through the machine with the top
surface thereof in engagement with the sanding belt of the sanding
head, and a pressure shoe to hold workpieces down on the conveyor
means, the improvement which comprises:
A. linkage means pivotally connected with the pressure shoe and
with the frame of the machine, the latter connection being at an
elevation above the pressure shoe,
said linkage means mounting the pressure shoe in the machine and
constraining the shoe to movement in an arcuate path having both a
horizontal and a vertical component, the former being greater than
the latter; and
B. spring means reacting along a substantially horizontal line
between the pressure shoe and the frame of the machine and applying
a force on the pressure shoe urging the workpiece engaging portion
thereof horizontally towards the zone of engagement between the
workpiece and the sanding belt,
whereby the resultant downward component of the arcuate movement to
which the pressure shoe is constrained presses the toe of the
pressure shoe solidly against a workpiece on the conveyor means.
Description
This invention relates generally to abrasive belt type sanding
machines, and refers more particularly to machines of this kind
that are especially designed for the planing and sizing of rough
lumber.
These machines have a sanding or abrading head which comprises an
endless abrasive belt trained over vertically spaced parallel
rolls, the lower one being usually referred to as a contact drum
since it supports the abrasive belt against the thrust of the
workpiece as the workpiece moves through the machine. Usually it is
the contact drum that is driven to impart high speed orbital motion
to the abrasive belt.
The workpieces are carried horizontally through the machine with
their top surface in contact with the drum-supported abrasive belt,
by a conveyor unit vertically adjustably mounted in the machine
below its sanding or abrading head. The conveyor unit has an
endless power driven conveyor belt, the top stretch of which slides
across and is supported -- especially directly below the contact
drum -- by a smooth surfaced horizontally disposed platen. By
adjusting the elevation of the conveyor unit, the machine is
adapted to workpieces of different thicknesses.
A downwardly biased infeed shoe holds the workpiece down on the
conveyor belt as it enters the abrading zone and comes into contact
with the drum-supported abrasive belt, and an outfeed shoe holds
the workpiece down as it leaves the abrading zone.
It has long been known that to meet close tolerances in the sizing
of workpieces it is necessary that the toe of the infeed pressure
shoe press down on the workpiece just as close as possible to the
zone of action, or in other words very close to the bottom of the
drum-supported abrasive belt. If that close juxtaposition is not
maintained, the leading edge or end of a workpiece approaching the
abrasive belt could be lifted off the platen supported conveyor
belt by strains and stresses in the workpiece caused by warpage,
and when that occurs the cut taken by the abrasive belt is greater
than it should be to maintain uniform flatness of the abraded
surface and the desired thickness dimension.
For finish sanding the conventional manner of mounting the infeed
pressure shoe is entirely adequate because workpiece thicknesses
are practically invariably uniform, but in planing and sizing rough
lumber the conventional way of mounting the infeed pressure shoe
creates intolerable consequences.
An example of the conventional way of mounting the infeed shoe may
be found in the copending application Ser. No. 249,175, filed May
1, 1972 now U.S. Pat. No. 3,782,044. As illustrated in that
application of Paul H. Olin, the conventional way of mounting the
pressure shoe constrained it to pivotal or rocking movement about a
fixed axis. With a view to applying downward pressure onto the
workpiece as close as possible to the zone of action, the axis
about which the shoe pivoted was so located that upon any
appreciable elevation of the pressure shoe by an increase in work
thickness, the toe of the shoe would collide with the abrasive
belt. The sparks resulting from such contact created a serious fire
hazard.
To eliminate that hazard, the shoe location was moved farther
upstream, at the expense of losing the hold-down pressure where it
was most needed. Such shifting of the pressure shoe location also
created a gap between the shoe and the surface of the sanding belt,
large enough to allow relatively big pieces or chunks of wood,
knots and so forth that broke loose from the rough lumber, to
collect between the shoe and the belt surface. When that happened,
the sudden elevation of the toe of the shoe by an incoming
over-thick piece of lumber often drove the knot or loose piece of
wood against the belt with such force that the belt would be torn
or cut, or at least severely damaged.
With a view to overcoming the objectionable consequences of the
conventional way of mounting the infeed hold-down shoe of belt-type
sanding and abrading machines, this invention has as its object to
so mount the infeed shoe that its toe at all times remains at
substantially the same short distance from the zone of contact
between the workpiece and the abrasive belt regardless of changes
in the elevation of the toe of the shoe resulting from variations
in the thickness of the workpieces.
With these observations and objectives in mind, the manner in which
the invention achieves its purpose will be appreciated from the
following description and the accompanying drawings, which
exemplify the invention, it being understood that changes may be
made in the specific apparatus disclosed herein without departing
from the essentials of the invention set forth in the appended
claims.
The accompanying drawings illustrate one complete example of the
embodiment of the invention constructed according to the best mode
so far devised for the practical application of the principles
thereof, and in which:
FIG. 1 is a more or less diagramatic side view of an abrasive
belt-type lumber planing machine embodying this invention;
FIG. 2 is a detail sectional view through the portion of the
machine at which the abrasive planing action takes place;
FIG. 3 is a cross-sectional view through FIG. 6 on the planes of
the line 3--3, illustrating the relationship between the infeed
hold-down shoe and the contact drum-supported abrasive belt, and
the mounting structure for the shoe;
FIG. 4 is a diagrammatic view illustrating in an exaggerated way,
the retention of substantially constant positional relationship
between the toe of the infeed shoe and the surface of the abrasive
belt despite changes in elevation of the shoe;
FIG. 5 is a perspective view of one end portion of the shoe and the
adjacent shoe mounting structure; and
FIG. 6 is a top view of the structure shown in FIG. 5.
Referring to the accompanying drawings the numeral 7 indicates
generally a lumber planing machine of the type to which this
invention appertains. As is customary such machines have a conveyor
bed 8 by which the workpieces are carried or fed horizontally
through the machine with their top surface in engagement with the
endless abrasive belt 9 of a sanding head 10. The sanding head is
fixedly mounted in the frame of the machine and comprises an
abrasive belt 9 trained about a contact drum 12 and an idler roll
13, the former being power driven to impart highspeed orbital
motion to the belt.
Although not necessary for an understanding of this invention, it
should be noted that the abrasive belt 9 is maintained under
tension by an upward biasing force acting upon the idler roll 13
and that the manner in which the idler roll and the contact drum
are mounted enables removal and replacement of the abrasive belt.
For a disclosure of that sanding head structure reference may be
had to the copending Bernu application Ser. No. 240,683 now U.S.
Pat. No. 3,777,442, which is assigned to the assignee of the
present invention. As explained in that application, in the
operative condition of the sanding head its contact drum is solidly
held against any displacement from a predetermined position with
its axis accurately horizontal and the bottom-most part of the
abrasive belt directly above a platen 14 which forms a part of the
work feed conveyor bed 8.
The conveyor bed comprises a rigid horizontally disposed frame
designated generally by the numeral 15 with driven and idler rolls
16 and 17 respectively journaled in its opposite ends and a
conveyor belt 8 trained over these rolls. The top stretch of the
conveyor belt is supported by the platen 14 and a plurality of
idler rolls 19 which collectively maintain the top stretch of the
belt accurately horizontal. The drive for the conveyor belt,
indicated generally by the numeral 20, is conventional and
comprises a motor and a suitable speed reducer.
To enable the machine to handle workpieces of different
thicknesses, the conveyor bed is vertically adjustable in the
conventional manner which involves imparting simultaneous actuation
of a plurality of nut and jack screw supports (not shown) by which
the conveyor bed is mounted in the frame of the machine. A hand
wheel 21 at the side of the machine and appropriately connected
with the nuts on the jack screws provides the means for adjusting
the elevation of the conveyor bed.
Since the distance between the underside of the contact
drum-supported abrasive belt and the platen determines the amount
of stock removed from the top side of the workpieces, it is
important that the workpieces be firmly held down on the platen
supported conveyor belt not only at the zone of action but also as
the workpieces approach that zone. For that purpose an infeed
hold-down shoe 22 is provided. There is also an outfeed hold-down
shoe 23 which holds the workpieces down on the platen-supported
conveyor belt as they leave the zone of action, and both upstream
and down stream of the zone of action there are pinch rolls 24 that
coact with the idler rolls 19 of the conveyor bed to hold the
workpieces in contact with the conveyor belt and assure their
advance through the machine.
As explained hereinbefore, the planing and sizing of rough lumber
with an abrasive belt-type machine poses a problem that is not
encountered in finish sanding. This stems from the fact that rough
lumber is often warped by internal stresses and its surfaces are
anything but uniformly flat. Accordingly, unless the infeed shoe
holds the workpiece down directly adjacent to the zone of action,
the leading edge or end of the advancing workpiece may be lifted
off the platen-supported conveyor belt as it approaches initial
contact with the abrasive belt. If that occurs, more than the
desired amount of stock will be removed making it impossible to
meet close thickness tolerances.
The need for having the infeed shoe exert its hold-down pressure as
close as possible to the zone of action, has always been
appreciated, but with the conventional way of mounting the shoes,
which simply provided for rocking movement of the shoe about a
fixed axis, the greater variations in thickness and the uneveness
of the surfaces of rough lumber, often lifted the toe of the shoe
into contact with the abrasive belt. This was inevitable since the
mounting of the shoe constrained it to pivotal movement about a
fixed axis so located that the toe of the shoe traveled in an arc
that intersected the circumference of the contact drum.
The obvious solution to that problem, namely moving the pivot axis
of the infeed shoe farther upstream, not only objectionably
withdrew the location of the hold-down pressure from its desired
close proximity to the zone of action, but also created a space
between the toe of the shoe and the surface of the
contact-drum-supported abrasive belt that was large enough to allow
knots and chunks of wood to accumulate therein, with the devasting
potentiality of having the same forcefully driven against the
abrasive belt by elevation of the toe of the shoe.
With the improved manner of mounting the infeed shoe which this
invention provides, the desired location of the hold-down pressure
is maintained despite the inevitable less-than-ideal conditions
presented by rough lumber. This improved mounting features a
parallelogram linkage indicated generally by the numeral 25 by
which the shoe is connected with the frame of the machine. As
depicted in diagrammatic FIG. 4, the linkage makes it possible for
the toe 26 of the shoe to travel in an arcuate path delineated by
the broken line AP which is substantially concentric with the
cylindrical surface of the contact drum delineated by the arc CS.
As a result throughout the complete excursion of the toe of the
shoe as the shoe is lifted and descends with variations in the
elevation of the top surface of the workpiece, the hold-down
pressure is exerted at a location directly contiguous to the zone
of action. For clarity, FIG. 4 illustrates the hold-down shoe
traveling through a much greater distance than it does in
practice.
The parallelogram linkage 25, which is duplicated at opposite ends
of the infeed hold-down shoe, comprises a pair of links 27 and 28
mounted to swing about speed parallel horizontal axes fixed with
respect to the frame of the machine and lying in a horizontal
plane. The links project downwardly from the fixed axes about which
they swing, and have their lower end positions pivotally connected
with the shoe, the pivot axes of those connections being parallel
and horizontally spaced apart the same distance as the aforesaid
fixed axes.
Bearing in mind that the structure now being described is
duplicated at the end of the shoe not shown in the drawings, the
fixed axes about which the links 27 and 28 swing are defined by
bearings 29 in a bracket 30 that is suitably fixed to the main
frame of the machine. One of those bearings 29 has a stub shaft 31
journalled therein, the other rotatably mounts one end of a shaft
32 that extends across the machine to have its other end similarly
supported. The links 27 and 28 which are of the same length have
their upper ends respectively keyed and fixed to the stub shaft 31
and the cross shaft 32, and as best seen in FIG. 6, are laterally
spaced from one another so as not to collide during movement
thereof as the pressure shoe rises and falls.
The axes of the pivotal connections between the lower ends of the
links and the shoe, are defined by bearings 33 in an arm 34 fixed
to the shoe and projecting rearwardly from its heel. The rearmost
of these bearings 33 has one end portion of a stub shaft 35
journalled therein, the other end portion of which is keyed and
fixed to the lower end of the link 27; and the other of the two
bearings in the arm 34 freely rotatably receives a cross shaft 36
which, like the shaft 32 extends across the width of the machine.
The ends of the shaft 36 are keyed to and fixed in the lower ends
of the links 28.
A spring 37, one at each end of the pressure shoe, yieldingly urges
the shoe towards the contact drum and by virtue of the downward
component of the arcute travel of the pivotal connections of the
links 27 and 28 to the shoe which results from the approach of the
links towards vertical dispositions, the spring force exerts far
greater downward pressure on the shoe than would the case if the
same spring acted directly downwardly on the shoe.
The spring 37 reacts between an arm 38 fixed to and projecting from
the end of the shoe, and a nut 39 on a bolt 40 that passes slidably
through a hole in the arm 38 and is threaded in and fixed with
respect to a laterally projecting flange 41 on the bracket 30. The
spring surrounds the bolt and the head 42 of the bolt limits the
spring-produced motion of the shoe and thus defines the lowermost
limit of the up and down movement of the toe of the shoe.
Elevation of the shoe produced in any way in opposition to the
spring force is limited by an adjustable stop 43 in the form of a
bolt threaded into the flange 41 with its head positioned to be
engaged by the arm 38.
The shoe 23 at the downstream side of the zone of action, is
mounted in the conventional way by a cross shaft 44, since it does
not encounter changes in elevation of the top surface of the
workpiece passing through the machine.
Those skilled in the art will appreciate that the invention can be
embodied in forms other than as herein disclosed for purposes of
illustration.
* * * * *