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Патент USA US2406606

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Aug- 27, 1946.
G. w. JACKSON ’
'
2,406,606
EDGING MACHINE
'
?led May 21, 1943
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7 Sheets-Sheet‘?
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IN VENT 'OR
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Aug. 27, 1946.
' G. W. JACKSON
2,406,606
EDGING MACHINE
Filed May 21, 1945
7 Sheets-Sheet s
\.
Aug. 27, 1946.}
G._W. JACKSON
2,406,606
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EDGING MACHINE
Filed ‘May 21, 1943
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INVENTOR
GEORGE W JACKSON
'
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Aug. 27, 1946.
2,406,606‘
G. w. JACKSON
EDGING MACHINE
Filed May 21, 1945 '
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INVENTOH
GEORGE W. JACKSON
2,406,606
Patented Aug. 27, 1946 '
UNITED STATES PATENT OFFICE
2,406,606
EDGING MACHINE
George W. Jackson, Southbridge, Mass, assignor
to American Optical Company, Southbridge,
Mass, a voluntary association of Massachusetts
Application May 21, 1943, Serial No. 487,907
' 9 Claims.
(Cl. 51-101)
1
2
This invention relates to improvements in ma
Fig. 1 is a side elevation of the 'device embody
chines for edging articles ‘to controlled contour '
ing the invention;
character having automatically functioning parts
and method of obtaining said functions.
‘
Fig. 2 is a front elevational view of said device;
Fig. Sis a plan view of said device;
shape and more particularly to machines of this
‘ Fig. 4 is a sectional view taken as on line 4—4
5.
of Fig. 6 and looking in the direction indicated by
'the arrows;
One of the principal objects of the invention is
to rotate an article relative to an abrading wheel
Fig. 5 is a fragmentary sectional view taken as
for reducing the article to a given contour shape
on line 5--5 of Fig. 6 and looking in the direc
and size whereby the said article is reduced to the
contour shape and size desired throughout sub 10 tion indicated by the arrows;
Fig. 6 is a sectional view taken as on line 6—6
stantially one complete cycle of movement of
of Fig. 1 through the operating head of the de
said article relative to the abrading wheel with
said cycle of movement being hydraulically con
Fig. 7 is‘ a fragmentary sectional view taken as
trolled.
Another object of the invention is to provide 15 on line 'l-1 of Fig. 1 through the stone oscillat
ing mechanism of the device;
a device for edging articles ‘to given contour
Fig. 8 is an enlarged fragmentary sectional
shapes and sizes whereby the article may be hy
view taken as on line 8—-8 of Fig. '7 and looking
draulically clamped into working position or re
in the direction indicated by the arrows;
leased with the clamping device being rotatable
Fig. 9 is an enlarged fragmentary sectional
with the article under hydraulic control as to its
view taken as on line 9—9 of Fig. 3 and looking
extent and speed of rotation relative to the
in- the direction indicated by'the arrows;
abrading wheel for removing the required amount
Fig.‘ 10 is a sectional view taken as on line
of material from the article and with the abrad
Ill-l 0 of Fig. 9 and looking in the direction indi
ing wheel hydraulically oscillated in a direction
transversely of the article with the extent of the 25 cated by the arrows;
Fig. 11 is an enlarged fragmentary sectional
transverse movement or oscillation of the abrad
vice;
ing wheel being variable.
'
‘
,
'
.
in the direction indicated by the arrows; and
Fig. 12 is a schematic view illustrating the hy
trolled holding means for a device of the charac
draulically operating system of the device.
Devices for reducing articles to given contour
"
Another object is to provide hydraulically. oper
shapes and sizes are not new in the art, partic
ated means of the above character intercom
nected with an oil feed system having the oil
pressure of said system controlled by a variable
displacement pump.
-
View taken as on line I l-l l of Fig. 3 and looking
’
Another object is to provide hydraulicallycon
ter described.
.
ularly, devices for reducing ophthalmic lenses to
‘desired contour shape and size.
35 '
-
Many attempts have been made to provide de
vices for reducing a lens to a given contour
Another object is to provide a hydraulically
operated power unit for rotating 'the‘article at
least throughout one complete cycle of movement
and having associated therewith speed reduction
means for transferring the power from‘said hy 40
shape and size through one complete cycle of
movement of the lens relative to the abrading
wheel but in most instances in the past such
draulic power unit to the article.
for accomplishing the desired results. Most prior
'
'
Other objects and advantages of the invention
will become apparent from the following descrip
tion taken in connection with‘ the accompanying
devices embodied mechanical or electrical means
art devices of this nature were of such charac
teras to have relatively positively operating parts
with no intermediate variable as to the function
drawings and it will be apparent that many 45 of said parts. In most instances, the control
was mainly directed to means for completing the
changes may be made in the details of construce
cycle of movement of the article relative to the
tion, arrangement of parts and methods shown
abrading wheel with the article held in a ?xed
and described Without departing‘ from the spirit
position until a given amount of material was
of the invention as expressed in the accompany
ing claims, I, therefore, do notwish't'o be lim 50 removed therefrom whereby a contact was made,
in. the instance of electrically operated means,
ited to the exact details of construction, arrange
ment of parts and methods shown and described
"with a switch or a similar device which closed .
as the preferred forms only have been given by
the circuit to a motor or electrically operated
clutch Which imparted a given rotary movement
way of illustration.
.
55 to the article. There is no intermediate variable
Referring to the drawings:
2,406,606
3
as to this operation and in most instances did
not produce an article having the desired edge
?nish. The remaining parts of the device op
erated in a similar manner to other known de
vices. It, therefore, is one of the primary objects
of this invention to overcome the above di?icul
ties with such prior art devices through the pro‘
vision of hydraulically operated means with in
termediate controls for clamping the article in
operating position, for rotating the article rela
tive to the abrading wheel throughout one com-7
plete cycle of movement with intermediate con~
trols for insuring the reduction of said article to
proper contour shape and size and to proper edge
?nish, for controlling the surface shape of the
stone during said edging operation and for im~
parting an oscillatory movement to the stone dur
ing said edging.
Referring more particularly to the drawings
wherein like characters of reference designate
like parts throughout the several views, the de
4
tioning as stopper means for closing one end of
said bore.
The bushing 35 is preferably provided With a
scalloped contour forming oil ports 5.! between
the inner wall of the bore 23 and said bushing.
The spring 38 is preferably provided with a plu
rality of openings 42. The valve stem 34 is pro
vided with an opening 43 communicating with
the internal bore 40 of said stem and with the
v space between the stem and the bore 23 of the
shaft l5. The shaft :5 is provided with an
opening 44 communicating with the bore 23 and
with a hollow chamber 45 internally of the bear
ing member 46. The bearing member 46 is con
nected through a port 41 with an oil line 43.
The bearing I4 has an oil chamber 43 inter
nally thereof and is provided with stop means 50
internally thereof having a portion 5! extending
The web I‘! is provided with an integral
outwardly of the bearing to which a part is piv
otally attached as will be described later herein.
The base l3 adjacent the end of the shaft I5
having the gear 24 thereon is provided with ad
vjustable stop means 52 extending internally of
the bore v23. The stop means 52 is provided with
a threaded portion 53 threadedly supported with~
in a sleeve 54. The sleeve 54 is rotatably sup
ported in a bearing 55 formed in the base [3 and
flange 25 on one side thereof which overlie one
has a hand wheel 53 attached by a set screw or
side surface of the stone [6 and with a clamp
the like 51. A suitable key plate 53 secured in
ternally of the base [3 and having a tongue 53
?tting within a longitudinal slot 60 in the stop
member v52 is adapted to retain said stop mem
ber against rotation when the sleeve 5%, which
is threadedly connected with the stop member
52,, is rotated through manipulation of the hand
vice embodying the invention comprises a base
l3 having spaced bearings [4 in which the stone
supporting shaft 15 is rotatably supported. The
stone [3 is carried by a web I‘! having a hub l8
secured to the shaft [5 by a set screw or the'like
89.
ring 2| secured to the web by .screws or the like .
22 for supporting the stone in operating position
‘on said web.
The shaft [5 has. a hollow bore 23 longitudi
nally thereof. The said shaft [5 is provided ad
jacent one end thereof with a spiral gear .24 .
meshing with a spiral gear 25, said spiral gear
wheel 56. This provides means for varying the
25 is in turn connected with a spiral gear 26 car
ried by a stud shaft 2-1. The stud shaft 2‘! is
position of the stop means 52 in a direction longi
abrading wheel or stone IS with the ratio of the
said gearing being such as to give you the proper
speed of rotation of the stone.
The spiral gear 25, which is set forth above as
being driven by a spiral gear 23, meshing with
oscillatory movement to the abrading wheel or
stone IS. The function of said device is as fol
tudinally of the bore 23.
‘ Suitable sealing members or the like 3! and
supported within suitable spaced bearings '28
and 29. The stud shaft in turn is provided with 40 62 are provided in the respective bearings M
which are adapted to prevent oil leakage from
a worm gear 30 in mesh with a worm 3| .carried
the bearings and to simultaneously prevent abra_
by the'driven shaft of a suitable motor or the
sive particles from entering the hearing.
like 32,
The device set forth above is for imparting an
The above provides the power for rotating the
the gear 24 for imparting a rotary movement to "
the shaft I5 is so designed that when the said
gear 25 rotates, a rotary movement will be im
parted to the gear 24 and _simultaneous to said
lows:
'
It is ?rst pointed out that the chamber 49
contains oil built up to a given pressure as will
be hereinafter described more in detail. When
the spiral gear 25 is rotated the gear 24 rotates
It is herein .pointed out that the helix angle of
the spiral gear 25 is such as to simultaneously
causing said gear 24 to move in a direction lon- - I
urge the gear 24 in the direction of the arrow
33. This causes the shaft 15 and the stone car
gitudinally of the spiral gear 25 causing the shaft
ried thereby to be urged in said direction simul
l5 and stone carried thereby to be moved in the
direction indicated by the arrow 33. Internally
of the hollow bore 23 of the shaft l5 there is a
taneous to being rotated. As the shaft l5 moves
in the direction of the arrow 33 the valve stem
34 is simultaneously moved in said direction. As
the shaft I5 and stem 34 move in said direction,
oil in the chamber 49 is forced through the per
forations 42 through the port 43 into the hollow
bore .40 of ‘the stem. The said oil travels lon
gitudinally of said stem and is exhausted from
the end 63 thereof where upon the said oil will
?ow through the open end 54 of the bore 23
back down into the sump internally of the base
13. This permits the stone to be moved in the
direction of the arrow 33. Movement is contin
ued in said direction until the member 31 engages
the stop means 50 whereupon pressure will be
exerted on the end 31 of an amount suf?cient
to cause the spring 38 to be moved from its
cupped position, as illustrated in Fig. '7, ‘to a re
versely cupped position. This causes a Valve stem
rotary movement a thrust action will take place
valve stem 34 supported by spaced bushing like
members 35 and 3E. The bushing 36 is secured
in ?xed position internally of the bore 23 and
the bushing 35 is ?xedly secured to the valve
stem 34. The end 31 of the valve stem 34 op
posed to the gear 24 is provided with a spring
washer 38 secured throughout the periphery
thereof as illustrated at 33 to the adjacent end
of the shaft I5. The washer 38 is cupped and
is adapted to have its cupping characteristics re~
versed by snapping to one side or the other of -
a plane extending through the peripheral edges
thereof.
The valve ‘stem 34 is provided with a hollow
bore 40 with the connecting means 3] for se
curing the spring washer 38 to the stem func~ '
2,406,606
5
6
34 to be' simultaneously moved in‘ a longtiudinal
direction, relative to the shaft l5, by an amount
equal to the reverse cupping of the spring 38.
positions in spaced relation with each other about
the axis of the pump shaft ‘H. As the‘ wabble
plate 15 is rotated the said wabble plate will
cause said pistons 93 to be reciprocated ‘in their
cylinders 95; Oil is fed internally of the housing
10 by means of an intake pipe line $3 which is
This movement of the valve stem 34 causes the
port 43 to be moved to a position underlying the
bushing 36 thereby closing said port. Simulta
neously to this movement the bushing 35 carried .
by the valve stem 34 will be moved in the direc
tion indicated by the arrow 65 by an amount
sufficient to cause theport 44 to communicate 10
with the bore 23 of the shaft [5. Oil forced under
connected with a suitable ?lter 91, as shown in
Fig. '7. The oil is merely fed from the sump
through the ?lter 97, into the pipe line 96 and,
in turn, inwardly of the housing ‘ill of the vari
able displacement pump 59. The oil from the
pipe line 96 ?ows inwardly of a chamber 98, as
pressure through the inlet 48 and ?owing through
the respective pistons 93 are reciprocated by the
the port 41 into the chamber 45 will thereby
wabble plate 15, whereby oil will be drawn in
travel vthrough the port 44 into the hollow bore
wardly of the pipe line {93 into the chamber 98.
23. The oil will then travel through the ports
This takes place when the respective‘valve ports
4| formed in the periphery of the bushing 36
99 are in communicating relation with the oil
and will thereby travel through the openings 42
chamber =98 and the respective cylinders 95.
in thevspring washer 38 and build up a pressure
Continued rotation of the shaft 1! will cause the
in the oil chamber 49 of an amount sufficient to
overcome the thrust imparted to the gear 24 by 20 valve port I00 formed in said shaft adjacent the
valve port 39 to communicate with the exhaust
the spiral gear 25 and thereby cause the shaft S5
chamber 68 whereupon compression of there
to move in the direction of the arrows 65. Re
spective piston 93 whose port is in communication
peated operations of this nature impart oscilla
with the exhaust chamber 68 will cause the oil
tory movement to the stone l6.‘
_
’ The oil inlet 48 is connected through a pipe 25 to be forced outwardly of the cylinder through
Line 66 to a pipe line 61 which, in turn, is con
the supply line 61.
This causes a pressure to
be built up through said supply line into the parts
connected with said supply line, the only part so
far described is the stone reciprocating mecha
placement pump comprises a housing 10 having
a pump shaft ‘H supported therein by suitable 30 nism.
The wabble plate ‘#5 is provided with a bear
bearings 12, 13 and ‘I4. The pump shaft ‘H has
ing plate it! supported by the balls' I02 where
a wabble plate 15 pivotally attached thereto at
by the wabble plate 15 is rotated relative to the
16. The pump shaft 1| is provided with a sprock
plate Nil which, in'turn, has a bearing contact
et ‘I1 connected through a sprocket chain 18 to a
sprocket 19 carried by the stud shaft 21. As the 35 with the respective pistons 93. The reciprocat
ing pistons 33 function as pump means for build
shaft 21 is rotated 'by the vmotor 32 the pump
ing up a pressure in the line 61.
shaft ‘H is simultaneously rotated. This causes
As shown in Figs. 1, 2 and 6, there is pivotally
the wabble plate ‘I5 to be simultaneously rotated.
attached to the base 53 a work supporting head
Rotatably supported in the bearing 12 and keyed’
to the pump shaft ‘H there is provided asleeve 40 M33. The work supporting head is pivotally sup
ported by the pivot bar M34 as best illustrated in
80 having a bearing projection Bl thereon adapt
Fig. 6. The head it3'is provided with spaced
ed to contact an engagement member 82 carried
bearings I95 and i536. The bearings I06 rotat
by the wabble plate 15; The key connection of
ably support a shaft IE1‘! having a bearing pad
the sleeve 80 with the shaft ‘H is such as to per
I08 adjacent one end thereof for engaging the
mit the bushing to be moved longitudinally of the
work its and ‘a hand wheel H0 adjacent the op
shaft. It is to be understood that the bearing
posed end thereof by which ‘the said shaft may
12 also moves with said bushing; the bearing 12
be manually rotated. The bearings Hi5 support
being carried'by a plunger 83 which is slidably
supported in a bearing 84. The plunger 83, in v a tubular shaft l i I in which is slidably supported
a clamp spindle H2. The clamp spindle H2 is
turn, engages a bellows 85 ‘which, in turn, is con- *
provided with a key pin H3 which extends
nected with an oil line 85. The bellows 85 is
through diametrically opposed longitudinal slots
supported by a threaded cap Bl which is thread
H4 formed in the hollow shaft iii. The key pin
edly attached to the ‘housing 70. The oil line 86
H3'is also‘adapted to secure a piston H5 to said
is connected with a T 88 see' Fig; 11 which; in‘
hollow shaft. Internally of the hollow shaft there
turn, is connected with a pressure relief valve 89
is provided a coil spring H6 which'is adapted
and 'a pipe line ‘93. The pipe line Bllis, in ‘turn,
to normally urge the spindle H2 in a direction
connected through the T 95 to the main oilsup~
outwardly of said hollow shaft. The said clamp
ply line see Fig. 8. It is'to be understood that
spindle H2 is ‘provided with-a bearing pad II‘!
oil is forced under pressure thr-riugh the supply
adapted to engage the side of the work 138 op
line into the pipe line ‘90 and, in turn, through
pos'ite'the bearing pad I88. The hollow shaft H I
the oil line '86. This causes a pressure to be
on‘its end opposed'to the clamp spindle H2 is
built up in the bellows 85. As the pressure is
provided with a suitable former H8. The former
built up internally of the bellows 85 the said bel
H8 is adapted to contact a former shoe H9 in
lows will expand and simultaneously move the
plunger 83, hearing 12 and bushing 80 in the 65 amanner similar to other prior art devices and
is the means for controlling the contour shape
direction indicated by the arrow 92. This causes
to which the article is edged. The work support
the wabble plate 15 to be tilted about its pivot
ing'head I33, between‘ the spaced bearings I05, is
16. The amount of said pivot being controlled
provided with an‘oil chamber I2!) in which the
by the amount of pressure which is permitted to
piston-H5 is adapted to reciprocate. The oil
be built up internally of the bellows 85.
chamber I25 has openings IZI and I22 on the
Internally of the housing ‘I0 there is slidably
opposed sides of the piston l l 5. Oil coming from
supported a plurality of pistons 93 having con
the‘ main variable displacement supply pump 69
tact with the wabble plate by spring means 94.
through the feed line 61 is directed to the T 9|;
The plurality of pistons 93 may be three or more
The T 91 is connected by a pipe line I39, as illus
in number and are disposed at given meridional
nected ‘with the exhaust chamber 68 of a vari
able displacement pump 69. The variable dis
2,406,606
trated' in Fig. '7 to the‘ T‘ HE, see Fig. 6. The T
I23 is connected to the pipe line I24 which, in
M5’. The shaft I41 has rigidly attached thereto
a plate I50 disposed at. a given angle and adapt
ed to be engaged by the respective plungers WI.
turn, is connected to a ?exible hose line I25
This plate I50 has a face plate I5! carried there
which is, in turn, attached to a casing I'Z'é. The
casing I25‘ has a port‘ 52's’. leading into an open Ca by adapted to be immediately engaged by the
chamber I23. This chamber communicates with
a passageway I29 formed in the side portion I30
plungers I413 so as to permit rotation of the plate
550 independently of rotation of the plate I5I.
of the head IE3. The passageway I29 communi
The shaft I41 has a valve port I52 formed there
in which, upon rotation of the shaft I41, is adapt
dates with a valve member ISI rotatably sup
ported in said portion I30. There is also com
municati-ng with said‘ valve member a passage
ed to‘ cause oil in the chamber IM to be directed
communicates with a passageway I53. The mem
through the respective ports “It and oil passage
ways III-5 progressively and successively as the
said shaft M1‘ is rotated. Simultaneously to this
function an additional valve port I55, formed
ber I25 also has. an additional oil chamber I34
on the’ side of the shaft I51 opposed to the valve
therein spaced from the chamber I28. This
chamber communicates with the opening I22
adjacent the upper end thereof as illustrated
port I52 and in slightly staggered relation there
with, is provided for successively and progressive
lv causing the plungers IM to be compressed
in communicating relation with suitable exhaust
way I 32 connected with the opening IZI leading
into the oil chamber I20. The valve member also
best
. Fig. 4 and communicates with a passage
way I35 leading into the valve 53!. Oil forced 20 openings I53 formed in the periphery of the'bear
ing I48 whereby oil will ?ow from the plunger
under pressure through the hose line I25, into the
cylinders through said exhaust openings I53 as
chamber I25, when the parts are in the position
indicated by the arrow I54.
as illustrated
Fig. 6, will‘ be directed through
As shown in Fig. 6, oil entering the line I40
the passageway I25 into the valve I3I and, as
will pass‘ through the lower port I45, through
indicated by the arrow I35, will be directed
the chamber I05 and will build up and exert a
through said valve member into the passageway
pressure on the lower plunger I44. This will cause
53?’. and thereby flow into the oil chamber I23
said plunger to exert a pressure on the‘ face plate
through. the opening I2 5. This will cause a pres
sure to' be‘ built up in said chamber between the
adjacent wall and the piston I I5 forcing said pis
I5I which, due to the particular angle of said
30 face plate, will cause the plate I50 to be rotated.
This causes the shaft I51 to be rotated and due
to the provision of a plurality‘ of said plungers
Due to the fact that the piston is attached to the
clamp spindle I212 it will force said clamp spindle
its will cause successive plungers to be com
pressed and others to‘ be exhausted and thereby
against the compression of the spring I It in the
provide a power drive for rotating the shaft I41.
direction’ of said arrow I51 thereby releasing pres
As shown in Fig. 6, the angle of the plate I50
sure‘. of the pad I I1 on the work I58. Simultane
is 90° out of phase with the“ actual position at
ous to this function, oil on the opposite side of
the plunger II 5 will flow through the opening
which it will be related with the valve ports I52
in order to be diagrammatically illus
522,. through the small chamber I34, outwardly
and
through the valve I I, as illustrated by the arrow 40 trated. In actual practice, the angle of the- plate
I55, relative to the valve ports I52 and I55 will
I38 through the exhaust line I53. This, there
be rotated approximately 90° from said illus
fore‘. relieves the pressure on the side of the pis
ton i=5 opposed to that being built up through the
trated position. The shaft I51 is provided with
an eccentric protrusion I55 on which a pair of
opening I'M. When the valve is rotated through
adjacent gears I51 and I58 are rotatably sup
out substantially a 90° cycle of movement‘ the oil
will flow through the passageway I29, through
ported. The‘ gear I58 meshes with an internal
gear I59 which normally is free to rotate within
the valve I35, into the smaller of the oil cham
itel
from said oi'l chamber through the
the'be'aring‘ I60, see Fig. 5, formed in the head
I03. The head I03 adjacent the internal gear
opening I 22 into the oil chamber I20 and cause
I59 is» provided with a locking cam IB'I, pivotally
the pressure to' be built up on that side of the
supported at I62, having an external manually
piston 555‘. When this function takes place the
operable portion I63 by which the cam I5I may
line‘ I52 functions as the exhaust line whereby
be moved to exert a binding pressure on the
the; oil pressure will be relieved by the flow of the
oil through the opening I2I, through the line
periphery of the internal gear I59. This cam
member IIi'I thereby locks the gear I59 against
I32, valve Iii-i and outwardly through the ex
This provides hydraulic means for
rotation or will release said gear for rotation,
haust
clamping or releasing‘ the work between the pads
as desired. The gear I51 meshes with an adja
cent internal‘ gear I64, see Fig. 6, which is rigidly
I05 and H1. It is to be understood that the ten
supported in a hub I65 rotatably carried by the
sion of the spring I I 5’ is such that it can be easily
compressed through the building up of the pres 60 stud I55. The stud I55 is threadedly connected,
sure in the oil chamber I20 through the opening
as‘ illustrated at I51, to the main frame of the
52 I‘ and is adapted to normally retain the work in
head I 03. Mounted on said hub I65 there is a
clamped relation between the bearing pads when
gear I68 which meshes with a gear I69 carried
no oil? pressure is built up in said chamber I20.
by the shaft Ill'l.
On the opposed side of the head, the pipe line
The gear I51 has one tooth more than the gear
ton in the direction indicated by the arrow I31.
I24‘ is connected through a hose line I40 to an
oil chamber IAII formed in said head. The oil
chamber I M contains‘ an oil operated motor Hill.
This motor comprises a block I 53 in which is sup
ported a plurality of longitudinally movable
plungers I154‘, The plungers communicate with
anoil chamber I45 which, in turn, communicates
with the‘ chamber Ill! through the ports I05.
Centrally of the block I53 there is a rotatable
shaft‘ M1. supported by spaced bearings I48‘ and
I50 and the internal’ gear I55 has one tooth more
than the internal gear I59. The purpose of this
arrangement is to provide a speed reduction as
to the rotation of the shaft I01.v This causes
the shaft I41 to rotate approximately 1000 to 1
revolutions of the gear I54 thereby causing said
gear" I154, through the gears I68 and I60, to im
part the? desired speed of rotation to the shaft I01.
The gear I53 has‘ a, gear I10 meshing there
75 with. The gear I10 is carried by a stud shaft I11
2,406,606
rotatably supported in‘ spaced bearings I12 and
I13 formed in a part carried by the head. Ad
jacent the opposed end of said shaft I1I there
10’
' the size of the article'will be accordingly con
trolled. vInternally ofthe pipe 1111690 there is
provided a disc I95 having a restricted opening
therein. This disc I 95'is to retard the‘ speed
idler gear I15 which, in turn, meshes with they GI of ?ow of-the oil through the line 90 leading into
gear I15 which is, in turn; carried by the hollow
the pipe line 86 and valve member 89 and it is
is supported a gear I14.
This meshes with an
primarily for the purpose of avoiding‘an ex- '
shaft III. This causes the hollow shaft III to
cessive ?ow of oil through the valve. The valve
be rotated simultaneous to the shaft I01 and
through the lock pin II3 imparts a simultaneous
member, in addition to the ball valve member
rotation to the clamp I I2. Due to the fact, that 10' I19; is provided with an exhaust opening I96
the former I I8 is carried by the shaft III, the
which, if oil'is forced through the port I91 at
said former is simultaneously rotated. When it_
a pressure suf?cient to force the ball rearwardly
is desired to impart a rotary movement to the,
and to allow oil to ?ow through said port I91,
gear I64, the gear I59 is clamped against rotation
the saidnoil will then be exhausted through the
by the cam member“ I9I. If it is desired to check 15 exhaust port I96 and thereby regulatethe'pres
the rotation of the gear I64 and thereby stop
sure of the ‘oil through the line 89. The line 86,
rotation of the shaft I01 the gear I59 is released
as shown in Fig. 8, is connected with the bellows
by the cam member I6I whereupon it is free to
85 and is for the purpose of regulating the
rotate and thereby prevent the gear I64 from ro
pressure
said bellows 85. This pressure is
tating. When the gear I59 is released byerthe 20' varied (by the mechanism illustrated in Fig. 11
cam member I9I the said shaft I01 may be ro
and functions substantially as follows:
tated by the manually operable means IIO.' This
>As the article I09 is being rotated in engage
permits the article I09 to be rotated forrgauge
purposes. Suitable resiliently urged stop mem
ment with the abrading wheel and the material
is being removed from the contour of saidarticle
bers I11 areprovided for engaging indentures
the former I I8 is initially held out of engage~
ment with thecontact shoe II9. This is due to
the fact that the article I09, of course, is initial
1y larger in diameter than the ?nished size de
E18 formed in the lower extremities of the piv
oted portions of the head to limit the outward
movement of the head in a direction away from
the abrading wheel.
7
I
-,
a
v
Referring to Fig. 11, the oil line '90- is con-v
nected with the T 9|, ‘as illustrated intFig. 8,
as previously described above, which receivesits
sired‘. At this stage the article I09 rotates very
slowly and remains in a substantially ?xed po
sition relative to " the "stone until’ a suf?cient
?ow of oil under pressure from a variable dis-_
placement pump 69. It has been previouslyde
amount of’ the engaged edge of the article I09
is removed to permit the former II8 to engage
the contact shoe II9. Continued removal of the
scribed that the oil forced through the line 90
passes through the pipe line 86 to the bellows
be exerted on the former shoe II9 through en
material of the article I09 causes a pressure to
95, as illustrated in Fig. 8. The T 88 also icon-V
nects said pipe line 90 to a relief valve 89 having
gagemerit of the former shoe II8 therewith.
This pressure, through frictional contact of the
a ball valve member I19 internally thereof. The
former II8 with the contact II9, causes the bell
ball member is urged into closed position by 40 crank I83 to be tilted about its pivot 5 I. Through
means of a coil spring I90; The spring is com
the engagement of the bell crank I83, through
pressed by a plunger I8I slidably supported in.
the contact I82, this tilting movement Will im
the member 89. The plunger I8I is provided
part a pressure on said contact and will cause
with a contact I82 adapted to engage a bell
the plunger I8I to, in turn, impart a pressure
crank I83. The bell crank I83 is‘pivotally ;sup-.
on the coil spring I80. The coil spring I80 will,
ported by the stud 5|, see Fig. '7. ‘For ease of.
in turn, increase the‘ pressure on the ball valve
operation, the member I83 is connected through
I19 and resist the incoming pressure of the oil
a ball bearing I84 to said stud. The bell crank
by an amount determined by the extent of rock
I83 is provided with a hollow arm I85 in which
ing movement ofvthe bell crank I 83; This in¢
is slidably supported a rack member I86 carry 50. creased pressure on the ball valve I19 thereby
ing adjacent its outer end the former II9. In
causesthe oil which would normally flow through
order to permit the rack to be moved longitudi
the port I 91 outwardly. of the exhaust port I96
nally of the hollow arm I85 and to seal said arm
to be directedthrough the oil line 86'to the
against the entry of dirt, dust and so forth, out~
bellows 85. As the pressure is increased in the
wardly of the hollow member there is provided
bellows 85, the said bellows will be accordingly
a bellows I81 having a sealed connection I98
cause'd'to expand ‘and in turn force the plunger
member 83 in the direction of the arrow 92.
with the rack member and a sealed connection
I89 with the hollow arm I85. The rack I86
The extent of said movement of the plunger 83
depends upon the amount of pressure built‘up
meshes with an idler gear I90 which, in turn,
meshes with a gear I9I carried by a manually 60 in the bellows 85. Movement of the plunger 83
rotatable member I92.
Therotatable member
‘ in'said direction will cause the bearing member
I92 is calibrated on the face I93 thereof and
said calibration is registered with a suitable
8I_ to rock the wabble plate 15 an amount equal
to the extent of the, movement of the plunger
pointer I94 which, through rotation of the mem-
83. This tilting of the wabble plate 15 will cause
65, an increased stroke vof the respective pistons 93
ber I92, causes the rack I86 to be adjusted in
wardly . or outwardly of the hollow arm I85;
This adjustmentis to move the former contact
shoe II9 rearwardly or forwardly with respect
to the plane of the portion of the abrading wheel
which is engaged by vthe articleto be edged and
provides means for controlling the size to- which
the article is to be edged. It is .quiteappare'nt
that as the former contact shoe H9 is- adjusted
and will increase the speed of ?ow or pumping
of the oil through the port 68 of the pipe line 61.
The pipe line 61 is connected with the T 9!
which, in turn,'is connected through a pipe line,
not shown, to the T I23 and will thereby direct
said pumped oil from the line 61 to the‘ pipe
line I24 and from ‘said pipe line I24 to the’ re
silient ?exible' hose line I40 and to the oil cham
rearwardly more of the material ‘of the article
ber .MI thereby accordingly increasing the pres
will Ice-removed from the contour thereof and 75 sure in said chamber I4! and, in turn‘. increasing
‘
£406,606
11
12
the pressure on the respective'plungers I44 which
are operated by said oil as previously set forth
through the ?lter 9‘! before returning to the
variable displacement pump 69.
above.
~- -~I‘tv is to be understood that during the rotation
of the work I I39, as set forth above, the stone
or abrading wheel I6 is oscillated by the mecha
nism shown in Fig. 7 and which has been previ
ously described above. As shown in Figs. 8, 9
and 10, during the oscillation of the abrading
This causes the speed of rotation of the
shaft M7 to be increased, with the amount of
increase depending upon the extent of increase
of stroke of the pistons 93 of the pump member
59. This, therefore, causes the speed of rota
tion of the article I69 to be increased» and will
wheel I6, there is in constant engagement with
more rapidly bring a new and progressive por
tion of the edge of the article to the abrading 10 said abrading wheel a truing tool I98. The
truing tool or hone I99 is carried by a block I99
wheel for removal. Keeping in mind that the
having a pair of bar members 2% attached
article initially is of a greater size than that de
thereto. The bar members 299 are slidably sup~
sired of the ?nished article, this will cause the
ported. in suitable slideways 29! carried by the
newly presented portion of said article to the
abrading wheel to again lift the former I I8 away 15 base of the machine.‘ The block I99 is engaged
by a bellows 202 connected through the pipe line
from the contact shoe I I9, thereby relieving pres
sure on the coil spring I99 whereby the inherent
203 to a hone control valve 294.
The hone con
trol valve comprises a passageway 295 to which
resiliency of the coil spring will return the bell
the pipe line 293 is directly connected. The said
crank to its initial position. This, of course, re
lieves pressure on the ball H9 and permits the 20. hone control‘ valve has an inlet port 296 to which
pressure built up in the line 85 to be relieved
the pipe line 6? is connected by means of a suit
I91 and the exhaust port I95 and function as
bleeder means for said line 86. This will reduce
the pressure in the line 86 and, in turn, reduce
the pressure in the bellows 85 and reduce the
stroke of the pistons 93. As the material of the
article I99 is reduced by abrading and the former
I I8 is again permitted to engage the contact shoe
able three-way ?tting 261', as illustrated in Fig.
8. A disc 298 having a restricted ori?ce therein
is positioned in the pipe line 6? adjacent the
hone control valve 264 to regulate the flow of
oil inwardly of said valve. The inlet port 299
communicates with a valve bore 29!) in which
the valve stem 2I9 is rotatably supported. In~
ternally of the hone control valve, there is pro
H9, a repetitive operation will be performed,
vided a network of passageways interconnected
whereby oil will flow outwardly through the port
with each other and with the valve bore 209.
which operation, slows down the rotation of the
This is best seen in Figs. 9 and 10 and comprises
article during the initial abrading and speeds
a passageway 2 II communicating with the valve
up the rotation of the article when reduced sub‘
bore and connected by a passageway 2 I2 to an
stantially to its ?nal size.
t no time during
this operation does the article I99 completely 35 other passageway 2I3 also communicating with
the valve bore 299. ‘The passageway 2 I2 extends
stop but through the use of the gearings I51,
transversely from the passageway 2II through
I58, I59 and IE4 respectively, the speed‘of rota—
the passageway 2| 3 and communicates with a
tion will be reduced to such a state where there
ball valve 2M mounted in a passageway 2E5
is an e?ective substantial stopping of rotation of
the article I99 when a high spot on. said article 40 communicating with an additional passageway
2H5 also communicating with the valve bore.
is being removed by the abrading wheel.
Opposed to the passageway 2! I there is provided
With the above arrangement there will be no
a passageway 2 I? which is adapted to communi
abrupt change in the speed of rotation of the
cate with the passageway 2“ through an open
article but there will be a smooth rhythmic ‘in
creasing of speed of rotation as the material of 45 ing 2I8 when said opening 2H3 is aligned with
said respective passageways 2H and 22?. The
the lens is continually being removed by the
passageway 2I‘I communicates with a passage
abrading wheel. If, however, there is a hard
way -2I9 which, in turn, communicates with a
spot in the article which is not removedv as
passageway 229 leading into the valve bore 299
quickly as the other portions of the edge of the
article there will be a relatively abrupt change 50 and also communicating with a spring pressed
ball valve 22I supported in a passageway 222
or decreasing of the speed of rotation of the
communicating with a transversely extending
article through the mechanism described above,
passageway 223 which also communicates with
but under ordinary circumstances the change of
the valve bore 2&9. The passageway 2 il, in ad
speed resulting through the above described
dition to communicating with the passageway
mechanism will be relatively smooth in function
2I9, also communicates with an additional pas~
resulting in the contour edge of the article hav
sageway 224 which, in turn, communicates with
ing a relative continuous and smooth edge ?n
an additional spring pressed ball valve member
ish. If the article is to be reduced in size con
225 mounted in a passageway 226. The passage
siderably and the speed of removal of the edge‘
of the article is relatively slow the said article 60 way 226 communicates with a substantially nor
may move throughout more than one complete
mally disposed passageway 22‘! which, in turn,
cycle of movement but the speed of rotation of
communicates with a passageway 228 communi
The oil which is exhausted through the several
exhaust ports mentioned above will ?ow down
wardly under the action of gravity into the sump
vide drainage means. rThe valve stem 2 iii in sub
stantial alignment with the passageways 223 and
2I6 is reduced in diameter to provide a clear
in the base of- the machine and will be drawn
anée 232- communicating with the longitudinal
eating with a passageway 229 leading to the
the article will be relatively slow during said
valve bore 209. The valve stem H9 is provided
movement and in most instances will permit the
with a longitudinally disposed groove 23! formed
article to be reduced to size in’ substantially one 65 in the side of the valve stem 2H] and adapted
complete cycle of movement. The function,
to communicate with the passageway 229 in one
however, of the device is such that when the
position of adjustment with the said longitudinal
article is progressively reduced to size the speed
slot 23I extending from said point of communi
of rotation of the article will synchronously be
cation with the passageway 229 downwardly
70
increased.
'
throughout the length of the valve stem to pro
2,400,606
141'
slot 23| whereby oil- may ‘drain fromlsaid‘ pas-i
passageway 220 and will be directed-from has-1
sageways 2|B and 223 into- the passageway 23|.‘
The valve stem 2|0'is provided with a flattened
side area 233 intermediate its ends adapted to
sageway 220into the passageway 2 | 9 and into the
respective passageways 2|‘! and 224. Keeping in
mind, therefore, that the pressure on‘ the ball
valve 22| is much greater than on the ball valve
bring about selective communication between the
main port 205 and'the respective passageways 2 l3
and 220. The main valvestem is=provided with‘
an eccentrically operated knob 234 having a
pointer portion 235 communicating with a plate
236 having suitable indications thereon‘indicat
‘mg the off, dress and hone position of adjust- '
10'
225 the pressure of the oil will cause the ball valve
225 to again open and cause oil to flow along the‘
passageway 226 through the pipe line 203 and‘
into the bellows 202. It is to be noted that the
ball valve 22| now comes into play and is designed
to resist a greater pressure than the ball valve ‘
2| 4 and thereby permits a greater pressure to
be built up in the pipe 1ine'203 and into the bel
~Oil is forced through the line 61 into the pas
lows 202 and will permit a greater pressure to
sageway 206. As shown in Fig. 10, the valve stem
2|0 is in off position. If the face 233 is rotated 15 be imparted on the truing tool I98 and to thereby
remove and more positively true the face of the
to the position indicated by the dash lines 231 the
oil passingthrough the port 206' will ?ow into the ' abrading wheel I6. The resisting pressure of the
valve member 22| is so controlled that when the
passageway 2'|3~, 'down‘throug'h the communicat
proper amount of pressure is built up in the ‘bel
ing passageway 2 l2, into the passageway 2| | andv
ment of the hone operating mechanism.
through the transversely extending opening 2 | 8 in 20 lows 202, to properly hone the abrading wheel,
the valve stem 2|0 which in this ‘position of ad
justment‘is' aligned with the respective passage
ways 2|| and 2". ‘This thereby permits the oil
to flow into'the' respective'passageways »2|9,' 220
and 224. The pressure on the ball 22| is so con
trolled as to be greater than on the ball ‘225'
whereby the oil entering the respective passage-'
pressure beyond that amount will-cause the ball
valve 22| to open permitting the oil to flow»
through the passageway 222, into the passageway
223 and from said passageway 223 into the spaced
area 232 communicating with the longitudinal
_ groove 23| and thereby flow outwardly thereof.
This might be termed an oil bleeding process by
which the pressure in the pipe line 203 may be
ways 2| 1, 220 and 224 will?rst open the ball valve
controlled at the different positions of adjust
225 and will ?ow into the chamber 226 which, in
turn, communicateswith the passageways 205 and 30 ment of the valve ‘stem 2|0 set forth above,
vIt ‘is to be noted that the spring pressure on’v
221. Since the longitudinal groove 23| in the
valve member 2|0, when said valve member is _- thejresilient means engaging the ball valves 2M
and 22|, respectively have to be controlled quite
rotatedrto communicate the port 206‘with the
carefully in order to permit said bleeding to take
passageway 2 | 3, is out of alignment with the‘pas
place with the proper and desired honing opera
sageway-V 229 no ?ow of oil will be permitted
tions. The pressure on the springs for the re
through said longitudinal groove 23| and the ad
spective ball valves may be varied by adjustment
jacent side wall vof the valve stem will close the
of the various nut-like members 238 whereby the
opening 229 against'the ?ow of oil.therethrough.
suitable function of said valve members may be
Oil therefore will not flow through the passage»
obtained. It is to’ be noted that the pressure is
way 221 and will be permitted only to flow out
substantially continuous on the stone truing de—
wardly of the passageway 205 through‘ the pipe
vice |98either when in dressing or honing posi
203 to the bellows 202. This exerts 'a relatively
tion and the ball valve 225 functions to prevent
low pressure on the stone truing tool I98. This
backward flow of oil from the bellows during the
is brought about by reason of the fact that as the
pressure is builtl'up in the ‘bellows 202,‘ through 45 dressing or honing operation. This. provides,
means for more positively controlling thecontour
the newbies through- the pipe line 203 there will
shape of the abrading wheel l6.
.
be a simultaneous building up of pressure of oil
. Whenthe indicator. 235 is set to off position
in the various passageways-2| | and 2|2 which
the face 2330f the valve stem 2|0 will be in a
communicate with the ball valve 2“. The ball
valve 2“! is so controlled by the coil spring pres 50, position such as indicated in full line in Fig.v 10.
sure imparted thereon as to open when a prede-'
termined pressure of the oil is reached in said
passageways and will thereby allow the ball valve
2 M to open to permit oil to flow into the chamber
This will shunt the flow of oil through the feed,
line.6'|. The longitudinal slot 23| will now be
aligned with the passageways 229, 228 and 221
communicating with opening 226 and pipe line
2 | 5 and from said chamber outwardly of the pas 55. 203. This will allow the oil pressure built up in
the bellows 202 to be relieved,
. '
sageway 2|6 into the clearance space 232 and to
‘ From the foregoing description it will be seen
be exhausted from said clearance space into the
that hydraulically controlled means are provided
longitudinal slot 23|. This provides means for
‘ controlling the extent; of pressure on the stone
for oscillating the abrading wheel l6; for impart
truing tool I98 when the valve stem is adjusted 6,0 ingja rotary movement to the work >|09 under
variable speeds according to the above description,
for hydraulically clamping or releasing the work
between the clamp 'pads I08 and Ill and for hy~
draulically controlling the stone truing tool |90.
Having described my invention, I claim:
position whereby the port 206 will communicate 65
to said above described position. ‘ The indicator
235 is now in the dress position. When‘it is de
sired to hone or true the stone or abrading wheel
IS the face 233 of vthe valve stem is moved to a
1. In a lens edging machine the combination
of a base having spaced bearings, a hollow shaft
extending opening 2| 8 in the valve stem to be
moved out of communicating relation with the . rotatably supported in said bearings, an abrad—'
ing wheel attached to the shaft and a head piv
passageways 2| I and 2 H and thereby out of com
municating relation with the low pressure valve 70 otally attached to the base for supporting a lens
for movement toward and away from the abrad
2 | 4. This also moves the longitudinal groove 23|
ing wheel, said hollow shaft having a valve stem
out of alignment with the passagewayv 2-29 with
slidably supported internally thereof, spring
the solid wall of the valve stem 2|0 again func—
washerlike means secured to said valve stem and
tioning to close saidpassageway 229. Oil, there
with the ‘port-220. V This‘causes the transversely
fore, will ?ow, inwardly of the port 206 intothe 15 to the adjacent end or the hollow shaft for con:
16
trolling the position of adjustment of the valve
stem longitudinally of the hollow bore of the
shaft, said shaft having a gear member adja
cent its end opposed to the spring washerlike
means meshing with'a rotating spiral gear, said
bearing means adjacent the spring washerlike
means having an oil chamber therein, means for
means ‘having the contact shoe thereon, said con
duit means connecting the pump with the means
supporting the contact shoe having ?uid ?ow con
trol means associated therewith which when the
material of the work in engagement with the
abrading wheel has been removed by a predeter~
mined amount and the former exerts a pres
sure on the contact shoe said ?uid flow control
means will be automatically operated to cause
chamber for building up an oil pressure in said
oil chamber of an amount sufficient to cause the 10 the pump, through its conduit connection with
the means for rotating the work support and
hollow shaft and abrading wheel to move in one
work, to cause the speed of rotation of said means
direction with said spiral gear being adapted to
feeding oil through the hollow shaft into the oil
continuously tend to urge the hollow shaft and
for rotating the work to be varied according to
abrading wheel in the opposite direction.
the Variation of the pressure of the former on
2. In a lens edging machine the combination
of a base having spaced bearings, a hollow shaft
the contact shoe.
rotatably supported in said bearings, an abrading
combination of an abrading wheel supported for
wheel attached to the shaft and a head pivot
ally attached to the base for supporting a lens for
movement toward and away from the abrading
wheel, said hollow shaft having a valve ‘stem
rotary and oscillatory movement, a work sup
slidably supported internally thereof, spring
I
5. In a device of the character described the
porting head pivotally supported for movement
toward and away from the abrading wheel, rotat
able clamp means onsaid head for supporting
the work and for supporting a former for simul»
taneous rotation with said work, means for sup
washerlike means secured to said Valve stem and
porting a contact shoe, a honing device for en
to the adjacent end of the hollow shaft for con
trolling the position of adjustment of the valve 25 gaging the abrading surface of the abrading
wheel, hydraulically operated means associated
stem longitudinally of the hollow bore of the
with the support for the abrading wheel for im
shaft, said shaft having a gear member adjacent
parting an oscillatory movement to said wheel,
its end opposed to the spring washerlike means
hydraulically ‘operated means functioning co
meshing with a rotating spiral gear, said bear
operatively with the clamp for supporting the
ing means adjacent the spring washerlike means
work, hydraulically operated means for rotating
having an oil chamber therein, means for feed
said clamp means and the former carried
ing oil through the hollow shaft into the oil cham~
thereby, hydraulically operated means for con
ber for building up an oil pressure in said oil
chamber of an amount sufficient to cause the
hollow shaft and abrading wheel to move in one
trolling the movement of the honing device to
ward and away from the abrading wheel, a ?uid
pump, means for connecting said ?uid pump with
direction with said spiral gear being adapted to
said various hydraulically operated means and
continuously tend to urge the hollow shaft and
means correlated with said various means con
abrading wheel in theopposite direction and
necting said ?uid pump with said hydraulically
means for automatically relieving the pressure in
operated means and with the former support for
the oil chamber at a given position of movement
effecting a cooperative function of said various
of the hollow shaft and abrading wheel against
hydraulically operated means whereby said by
the action of the spiral gear whereby the spiral
draulically operated means function in proper
gear will urge the hollow shaft and abrading
sequence,
withthe hydraulically operated means
wheel in the opposite direction to a given position
for rotating the work being responsive to vvary
whereby the oil pressure will again build up in the
ing pressure of the former on the contact shoe
oil chamber.
for varying the speed of rotation of the work
3. In a device of the character described the
relative to the abrading wheel according to the
combination of a rotatably supported abrading
amount of material to be removed from the work
wheel, a work supporting head mounted for move
immediately in engagement with the abrading
ment toward and away from the abrading wheel, 50 wheel.
means on said head for supporting workholder
6. In a device of the character described the
spindle means, ahydraulically operated power unit,
combination of a rotatably supported abrading
motion transfer means between said power unit
wheel, work support means embodying a pair of
and the workholder spindle means for causing
clamp spindles, a former carried by one of said
55
said workholder spindle means and work to be
clamp
spindles, a support having a contact shoe
continuously rotated, a former carried by said
for engaging the former, gear means carried by
spindle means adapted to engage a contact shoe,
the respective clamp spindles, a train of gears
a ?uid pressure line connected with said hy
draulic power unit and means in said fluid line
for interconnecting said gear means for simul
responsive to the movement on the contact shoe 60 taneous rotation thereof, a hydraulic motor em
bodying a plurality of plunger-s successively and
through engagement thereof by the former dur
progressively ‘moved under hydraulic pressure
ing the abrading of the work for regulating the
imparted
thereto, an angled disc-like member
speed of rotation of the hydraulically operated
adapted to be engaged by said plungers and to
power unit.
4. An edging machine comprising a rotating 65 be caused to rotate under the hydraulic pressure
of said plungers, reduction gear means intercon
abrading wheel, means for supporting work for
nected with said rotating disc and the train of
rotary movement relative to the abrading wheel,
former means on said work support for control
gears for imparting the rotary movement to
ling the path of movement of the work relative
to the wheel, means for causing said work support
the clamp spindles, ?uid pressure means asso
ciated with said ‘hydraulic motor and with the
means for supporting thev contact shoe with the
to be rotated, adjustable means having a contact
shoe for engagement with the former, a ?uid
pump, conduit means for connecting said ?uid
pump with said means for imparting a rotary
pressure of the fluid directed to said hydraulic
motor being controlled according to the pressure
of the former on the contact shoe whereby the
movement to the work support and with the 75 speed of rotation of the motor and therefore
2,406,606
'17
18
the speed of rotation of the work will be varied
according to the ‘varying degrees of pressure
trolling the output of said pump for simultane
ously regulating the magnitude of said driving
of the former on the contact shoe.
force in accordance with the amount of mate
7. An edging machine comprising a rotating
abrading wheel, means for supporting work for
rotary movement relative to the abrading wheel,
rial being removed from that portion of the
article in immediate engagement with the abrad
ing means, whereby the rotation of the article
former means on said work support for control
relative to the abrading means will be accord
ling the path of movement of the work relative
to the wheel, hydraulically operated power means
interconnected with the Work support for caus
ingly controlled.
ing said work support to be rotated, adjustable
tudinally slidable and rotatable shaft carried by
9. In a lens abrading machine the combina
tion of a base having spaced bearings, a longi
said bearings for rotatably supporting an abrad
means having a contact shoe for engagement
ing wheel, a source of power, a gear system adja—
with the former, a ?uid pump, conduit means for
cent one of said bearings connecting said shaft
connecting said ?uid pump with said means for
imparting a rotary movement to the work sup 15 with said source of power for rotating said shaft,
means for building up a hydraulic pressure in
port and with the means having the contact
shoe thereon and means responding to variation
the other of said bearing means, said gear sys
tem being so constructed as to cause said shaft
of pressure of the former on the contact shoe
to move longitudinally of the bearings in a
for varying the ?uid presure on the hydraulically
operated means and thereby varying the speed 20 direction toward the bearing having means for
building up a hydraulic pressure therein during
of rotation of the work relative to the abrading
wheel according to the amount of material to
the rotation of said shaft, means operably func
be removed from the work when in engagement
tioning to build up a hydraulic pressure in said
with the abrading wheel.
‘
~
latter bearing, upon the completion of a desired
8. A device for reducing an article to a desired 25 amount of longitudinal movement of said shaft,
contour shape and size comprising rotatably sup
of an amount su?icient to overcome the longi
ported abrading means, a head pivotally sup
tudinal movement of the shaft caused by the
gear system and for moving said shaft in a
ported on suitable means for movement toward
and away from the abrading means, rotatable
direction opposed to the movement introduced
clamp means carried by said head for clamp 30 by said gear system and means for relieving said
ingly supporting the article for engagement with
hydraulic pressure upon movement of said shaft
in said direction a controlled amount whereby the
the abrading means, means for imparting a driv
ing force to said clamp means for continuously
gear system will again move said shaft in said
rotating the article, means for oscillating the
?rst mentioned direction with the movements
head about its pivotal support in timed relation 35 of said shaft introducing an oscillatory movement
with the rotation of the clamp means, and means
to the abrading wheel in alternate and succes
including a variable displacement hydraulic
sive sequence.
pump and a hydraulic control valve for con
GEORGE W. JACKSON.
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