us 2677288
TRANSCRIPT
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2 , 6 7 7 , 2 8 8
ay
,
1954 A . GNAHRICH
SPEED REDUCING TRANSMISSION MECHANISM
4 Sheets-Sheet
1
i l e d J u l y
6 , 1 9 5 1
I ?
I N V E N T O R .
41mm
G / V / I E H R / C ?
BY
_
m
Q 9
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2 , 6 7 7 , 2 8 8
ay 4 , 1954 A . GNAHRICH
SPEED REDUCING TRANSMISSION
MECHANISM
4 Sh e e t s - S h e e t 3
iled July 6 , 1 9 5 1
INVENTOR.
A Z F R f D G / V A H I R / C / l
B Y
022M
.
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May
, 1954
A . GNAHRICH 2 , 6 7 7 , 2 8 8
SPEED REDUCING TRANSMISSION
MECHANISM
Filed
July 6 ,
1 9 5 1 4
Sheets-Sheet
4
F 7 6 5
INVENTOR.
A l f / K 0 Owl/RICH
B Y
m
W
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P a t e n t e d May
,
1 9 5 4
TED
2 , 6 7 7 , 2 8 8
2 , 6 7 7 , 2 8 8
SPEED
REDUCING TRANSMISSION
MECHANISM
A l f r e d
G n a h r i c h , M u l h o u s e , F r a n c e
A p p l i c a t i o n J u l y 6 , 1 9 5 1 , S e r i a l N o . 2 3 5 , 4 7 8
( C l . 74-804)
Claims.
1
T h e
present
invention
r e l a t e s
t o
a
mechanism
f o r the
c o a x i a l t r a n s m i s s i o n
o f uniform
r o t a r y
m o t i o n t o a
place
of use w i th d etermi nabl e c o n
stant
reduction
r a t i o s w h ich
are
produced
an d
e q u a l i z e d by members t o which a planetary mo
t i o n i s imparted.
T h e b a s i s
o f the
mo t io n
according t o
the
p r e s
ent in venti on s
structures known
as “cam i s k s . ”
In the known structures
o f t h i s
name u s e d i n
e c c e n t r i c d r i v e s
o f
v a r i o u s d e s i g n s and o p e r a t i o n ,
the te rm
“cam
d i s k s ” i s
commo nly used
t o d e? n e
p a r t s , the
outer
or i nne r peri p he ry o f
wh ic h
con
s i s t s
o f r a d i i o f comput e d
o r geometrically
d e v e l
o p e d shape,
w h i c h r u n i n t o
o r
m e r g e
with each
o t h e r , s u c h r a d i i
g e n e r a l l y
b e i n g c y c l o i d s ,
hypo
c y c l o i d s ,
or
c i r c u l a r
a r c s .
Cam
i s k s o f t h i s
type
have
i n common
the
disadvantages o f c o s t l y
manufacture d u e t o the n e c e s s a r i l y n a r r o w manu
f a c t u r i n g and o p e r a t i n g
t o l e r a n c e s i n connection
with
the blank
a n d
the t o o l ,
as w e l l as
the d i s
advantage o f low e ? i c i e n c y due
t o high f r i c t i o n
v a l u e s , i nasmuch a s i n the c l a s s i c a l
application
o f cam
d i s k s
o f t h i s c o n s t r u c t i o n ,
uniformly
r e
duced
r o t a r y
moti o n within d r i v e s
o f
t h i s kind
can o n l y be
p r o d uc ed by s l i d i n g
o n a
mating
curve,
a n d the number
f
curves d e t e rm i n i n g the
a c t i o n
i s
l i m i t e d
by
t h e s l i d i n g
a n g l e a t
t h e
mat
i n g c u r v e , t h e
r e s i s t a n c e
t o
s l i d i n g ,
and t h e t o o l s
e m p l o y e d .
In
contradistincticn
t o
t h i s ,
the cam i s k
used
i n
accordance wit h
t h i s
i n venti on
c o n s t i t u t e s
a
c o n s i d e r a b l y l e s s p r e c i s e
a r t i c l e ,
t h e o u t e r c i r
cumference
o f which
i s n o t
pro v i d ed with r a d i i
which
r u n i n t o
or m e r g e w i t h each
o t h e r ,
but
i s r a t h e r p r o v i d e d , by m i l l i n g by t h e g e n e r a t i o n
p r o c e s s
without
c o r r e c t i o n ,
with
r a d i i w h ich are
independent o f each o t h e r .
The milled
curv e has
a
circumference
of
more
than
9 0 °
an d l e s s than 1 8 0 ° . T h e p i t c h
c o r r e
s p o n d s
t o
the standard m o d u l e
o r p i t c h
s e r i e s .
This ma n n e r o f production makes
i t
p o s s i b l e t o
use
pre~forged
or
p r e - s tam pe d
blanks
with
a
mi n imum c u t t i n g l o s s ,
and
t o
g e t a l o n g
with
t h e
ordinary operating
means. T h e
shaping, i n ac
cordance with t h i s i n v e n t i o n , makes i t p o s s i b l e
t o
use
c u t t e r
s t e e l s o f
a
strength
o f
l e s s
than
50
i r g m s . pe r
s q . i nasmuc h a s ,
except for
an
nealing
t o
r e m o v e s t r e s s e s ,
there i s
n o n e c e s s i t y
f o r any heat treatment a f t e r
the forging or m i l l
i n g .
r i ’ h e cam d i s k i s journaled
c e n t r a l l y
o n the
crankpi n
o f
a crankshaft which i s
a l s o
journaled
i n
t h e c e n t e r
l i n e o r the g e a r i n g . Th e
c u r v i l i n e a r
periphery o f
the
e a r n d i s k b e a r s ,
i n t h i s e c c e n t r i c
p o s i t i o n , a g a i n s t c y l i n d r i c a l r o l l e r s ,
t h e
diameter
’
10
30
4 0
45
50
2
o f
which
s
congruent
with t h e
r a d i i o f
c u r v a t u r e
o f the
cam i s k ,
wh ic h
r o l l e r s
are ?xed,
concen
t r i c a l l y t o the center l i n e o f the
g e a r i n g ,
i n a
separate
cage
w h ich
s
i n s e r t e d i n the gear ho u s
i n g ,
and t h e
n u m be r
o f which, which
a l s o s e r v e s
t o determine t h e
reduction
r a t i o , has been e s t a b
l i s h e d w h e n l a y i n g out
t h e g e a r i n g
i n
accordance
with t h e p r e s e n t i n v e n t i o n .
From
h i s
i t
follows
that the number f curves
o f
the
cam disk
m u s t
be smaller t ha n the num
ber
o f r o l l e r s
in the
r o l l e r
cage to
n
extent
w h ich
corresponds
t o the crank radius o f the
c r a n k s h a f t .
T h e
reduction
r a t i o i s
d e r i v e d
an d
c a l c u l a t e d
fr om
t h i s d i ? e r e n c e .
When the crankshaft i s t u r n e d , the cam d i s k
i s
caused
t o
s w i n g
i n
a
c i r c l e .
In
the course
o f
360°
o f t h i s motion, a l l the
curves
o f the cam
d i s k
come
i n t o
engagement
with a l l ‘
the
r o l l e r s o f
the
r o l l e r
c a g e . Inasmuch, however, a s there
i s
a d i f f e r e n c e
b e t w e e n
the
n u m b e r o f
curves a n d
the
n u m b e r o f r o l l e r s , the
same
number f curves
o f the cam disk
w i l l
come twice i n t o e n g a g e m e n t
i n
the
course o f
o n e s w i n g
as the number o f
curves of the cam isk subtracted f r o m the
num
ber o f r o l l e r s o f the r o l l e r c a g e . Therefore the
cam
disks
w i l l
rotate o n
the
crankpin i n a direc
t i o n o p p o s i t e
the
d i r e c t i o n
o f
swing o f
the cam
d i s k , 1 . e . the
d i r e c t i o n o f
r o t a t i o n
o f
the
crank
s h a f t .
T h e
accompanying
d rawi n g
shows s e v e r a l
em
bodiments
o f
the
s u b j e c t
matter
o f
the
i n v e n t i o n ,
o f which:
F i g . l
i s
a diagrammatic showing o f the
gener
a t i o n
o f the mo t io n
o f the
cam i s k ;
F i g . 2
i s
a
diagrammatic r e p r e s e n t a t i o n o f
the
d e v i c e f o r
e i i e c t i n g
the transmission of t h i s
mo
t i o n ;
F i g .
3 shows a
f i r s t embo diment o f t h e
s u b j e c t
matter
o f
the invention i n a l o n g i t u d i n a l s e c t i o n
c o r r e s p o n d i n g to Fig. 2;
F i g . 4
shows
a second embod im en t i n
l o n g i
t u d i n a l
s e c t i o n ;
F i g . 5 i s the same e m b o d i m e n t s h o w n i n trans
verse
s e c t i o n ;
F i g . 6
i s
a t h i r d embod im en t
o f
the
transmis
si o n
parts,
shown
i n
radial
s e c t i o n .
In
F i g . 1 ,
t h e
g e n e r a t i o n o f the motion o f t h e
cam d i s k
i s
represented s y m b o l i c a l l y :
Let
i t
be
assumed
that
I i n d i c a t e s
a
r a c k ,
the
teeth o f wh ic h
are in
the f o r m o f r o l l e r s
or
c y l i n d r i c a l b o d i e s
3 ,
and t h a t a w h e e l , 2 , which
i n
the
complete
s t r u c t u r e
w i l l c o n s t i t u t e a cam
d i s k , has
a
diameter y Z
a n d
i s adapted t o
r o l l
o v e r
t h e r a c k , d u r i n g which r o l l i n g motion i t ,
turns about
t s
a x i s
c c .
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a 3
Let
i t
a l s o
be
assumed t h a t
the l e n g t h
o f
the
rack
from Al
t o
A3
i s s l i g h t l y g r e a t e r
than t h e
periphery
o f
t h e wheel 2 , and t h a t A2 i s the cen
t e r
p o i n t
o f
the
rack
s o
that
the
l e n g t h s Ai—A2
an d
A2 A3
are
e q u a l .
I f the
p o r t i o n
A2—A3
o f the
rack i s
curved
u p w a r d l y into
the
f o r m of a semi-circle so as to
b r i n g t h e e nd
A3
i n t o
the
p o s i t i o n
s h o w n
a t A 4 ,
a n d
the
cam disk
2 continues t o r o l l
over
the u p
ward ly curved
p or ti on
o f the t r a c k , said
cam
isk
w i l l leave the horizontal
direction
o f translation
o f i t s c e n t e r a t p o i n t A2 a n d , f o l l o w i n g the
sym
b o l i c a l l y curved r a c k , w i l l mo v e
t o
p o i n t A l l . The
d i s t a n c e s
t o A3 and
A l l
a r e
e q u a l . During
t h i s
motion o f t h e cam i s k
2 ,
i t s c e n t e r l i n e s t a r t i n g
from p o i n t
A2 and f o l l o w i n g rack I has a l s o
moved
i n
a
semi-circle
o f
a
diameter 1 / 2 , a n d i t s
axis
a :
i s now at a distance
1 1 2
f r o m the p revi ou s
horizontal
direction
o f
translation.
I f o n e
now
imagines
that the s t r e t c h f rom Al t o A2
i s l i k e
wise curved
u p w a r d
i n
the
shape
o f
a s e m i ~ c i r
c l e ,
s o
t h a t
Al c o i n c i d e s with A i l , then
i n
such
case the
horizontal d i r e c t i o n
o f translation o f
the a x i s o f the cam d i s k 2 w i l l change i n t o a
c i r c u l a r d i r e c t i o n o f t r a n s l a t i o n , t h e diameter o f
which
s e q u a l
t o
g 2 . I f
g 3 , t h e
diameter
produced
by
t h e c u r v i n g
t o g e t h e r
o f
r a c k l ,
i s c o n s t a n t ,
the diameter
y l o f
cam d i s k
2
determines the
diameter
1 1 2
o f
t h e c i r c u l a r m o t i o n .
Th e
c e n t e r
0 o f diameter 1 / 2 i s accordingly the c e n t e r o f
rack
and
the c e n t e r o f
t h e
g e a r i n g .
While t h e
cam d i s k 2 , w h e n
mo v ing
horizon
t a l l y , turns
aro u n d i t s c e n t e r a n u m b e r o f times
which
i s
equal t o the
r a t i o
o f i t s periphery t o
t h e d i s t a n c e
Al A3 f
rack
I , cam
d i s k 2 r o t a t e s
about i t s
c e n t e r
w h e n t h e
rack i s c l o s e d o n l y by
the
d i f f e r e n c e between i t s periphery a n d
the
c l o s e d r a c k ,
produced w h e n
Al and A4 c o i n c i d e .
Th e
r a t i o
o f
the reduction i s d e r i v e d
fr om
t h i s
d i s c o v e r y .
Referring t o F i g . 2 , 4 i n d i c a t e s a crankshaft
having
a crankpi n
3 0 w h ich
i s o f f s e t t o
r o t a t e i n
a c i r c l e
corresponding
t o the c i r c l e o f r o t a t i o n
g 2
in F i g . 1 ,
a n d
2
i s
a
cam disk m o u n t e d o n
said
crankpin
and bearing
i n the d i r e c t i o n
o f the o l f
s e t
o f
the crankshaft against
o n e o f
the ? x e d
r o l l e r s
3 carried by
a r o l l e r cage
5 wh ic h corre
sponds t o
t h e
c l o s e d
r a c k produced
by
b r i n g i n g
together
the
ends Al an d A l l
o f
the r ack 4 s h o w n
i n F i g . 1 .
s h a f t
3 0 , cam d i s k 2
i s
b o d i l y
returned
t o
i t s
s t a r t i n g p o s i t i o n ,
h a v i n g
however t u r n e d around
i t s a x i s
a
by
the
d i i l e r e n c e
o f
the
periphery
o f
y l
a s compared with y 3 i n F i g . 1 .
I f
t h e
designations,
p e r i p h e r y
and d i am e t e r are
now replaced b y , f o r
example,
4 0 r o l l e r s i n the
former rack
I
wh ic h has
now
been conv e rted
into
the r o l l e r
cage
5 , a n d by 36
curves
o r
indenta—
t i o n s 9 6
o f the
cam
d i s k , 2 , t h i s m ea n s that a
complete
rotation o f
the crankshaft d has
r e
t u r n e d the
cam disk 2 as
a
w h o l e t o
the
starting
p o s i t i o n ,
but that the
cam d i s k 2
i t s e l f
h a s , how
e v e r , rotated
an amount
equal t o fou r cu r ves
or
indentations
9 6 o n
the crankpin, the center
o f
wh ic h c o i n c i d e s w i t h the center o f the cam
i s k .
In
g e n e r a l ,
the
n u m b e r
o f
r e v o l u t i o n s m f
cam
d i s k 2 can
therefore
be determi ned
by
the f o r
mula:
H Z = T L 4 — _ ~ ( G E C )
i n which formula:
m
s
the
n u m b e r o f
r e v o l u t i o n s
o f
crankshaft
4
per
minute;
G
s
t h e n umb e r f r o l l e r s
3 ;
Upon a 360°
r otation
o f t h e c ra n k -
1 5
20
1 0 G I
30
7 0
7 5
4
C s the
n u m b e r
o f curves
o r
indentations 9 - 3
o n the
periphery
o f the cam
i s k
2 .
Of t h e
two
motions
de?ned,
o n l y
t h e r o t a r y
m o t i o n
o f the cam disk o n the crankpin o f the
c r a n k s h a f t
i s
u t i l i z e d ,
w h i l e t h e g y r a t o r y
motion
o f the cam i s k i s
without
e i f e c t .
T h e
rotary moti o n o f the cam d i s k 2 , wh ic h
has been d e?ned , i s transmitted
t o
the d r i v e n
member, r e p r e s e n t e d
by
t h e member
s i n F i g s .
2 a n d 3 , by s i x
b a l l s 6
o f
standard manufacture
each
o f
which
r o l l s
i n an annular
ball race d e
veloped i n accordance with
the invention and
f o rme d i n a
race
member r r i n g l ’ c a r r i e d by the
cam d i s k , t h i s
t r a n s m i s s i o n t a k i n g
p l a c e i n such
a m a n n e r
that
the
gyratory
m o v e m e n t
o f the
cam d i s k
2 caused by
the crankshaft 1 2 -
r o l l s out
without any e f f e c t i n the annular b a l l r a c e , while
there i s only transmitted the r o t a t i o n
o f cam
d i s k 2
about
i t s a x i s
brought about
by the d i f f e r
ence
betwee n the
n u m b e r
o f
r o l l e r s i ; an d the
number f
curves
9 6 of
the cam
isk .
At
equal
d i s t a n c e s from the c e n t e r
and
a l s o a t
an
equal
distance f r o m
each
o t h e r ,
there
are
f o r m e d
in
the cam i s k 2 , a s w e l l
as
i n the mem
ber
9 , the
race
members
o r r i n g s 7 which may
be
standardized a n d which can be
replaced
a f t e r
wear, a n d the i nne r curvature o f
wh ic h
c o r r e —
sponds
t o
t h e
r a d i u s o f
the b a l l ,
w h i l e
t h e diam
e t e r o f t h e i r r a c e f o r b a l l s 6 i s e q u a l t o that o f
the c i r c l e
o f r o t a t i o n o f crankpin
3 0 .
D u e t o
the
c o n t i n u o u s l y e c c e n t r i c p o s i t i o n o f cam
d i s k 2 ,
caused by the o f f s e t
o f t h e c r a n k s h a f t , and t h e
c o n t i n u o u s l y c e n t r a l
p o s i t i o n
o f the d r i v e n
mem
b e r 9 a l o n g t h e c e n t e r l i n e o f t h e g e a r i n g , b a l l s { 5
c o n t i n u o u s l y
r e s t a g a i n s t
the
r a c e
diameter o f
t h e
r i n g a l o n g
t h e i n n e r
c u r v a t u r e . By
t h e
r o
t a t i o n o f
c m d i s k 2 d u r i n g o p e r a t i o n , the c e n t e r
o f the
diameter
o f the
race o f
the r i n g s 7 moves,
i n the
cam
i s k 2 a s the d r i v i n g membe r, and
i n
the
m e m b e r
9 a s the d r i v e n member, l a t e r a l l y t o
t h e c e n t e r
l i n e
o f t h e g e a r i n g . This
displacement
e ? ‘ e c t s a complete r e v o l u t i o n
o f
part
8 w h e n
n ine
f u l l
rotations
o f crankshaft 4 ha v e acted o n cam
d i s k 2 .
T h e d r i v i n g b a l l s
6
transmit the r o t a t i o n
o f the
d r i v i n g
cam
d i s k 2
completely,
only
when cam
d i s k
2 i s , o n t h e
crankpin
o f crankshaft % ,
i n
that
zone
o f i t s
c i r c l e
o f
swing w h ich i s o p p o s i t e the
d i r e c t i o n o f rotation o f cam
i s k 2 .
After enter
i n g into
the z o n e
of the
same
direction as
the
d i r e c t i o n
o f
r o t a t i o n
o f
cam
d i s k
2 ,
the
d r i v i n g
b a l l 6 i s
not
held o n
i t s
races o f r i n g s ‘ i . When
cam disk 2 again enters the zone opposite i t s
d i r e c t i o n o f
r o t a t i o n , t h e g e o m e t r i c c o n d i t i o n
i s again brought a b o u t , which
w i l l
make
i t s e l f
n o t i c e a b l e by
s u d d e n
r o t a t i o n s
o f
the driven
member , both
i n
the cam
d i s k
2 a n d member
9 . By
p o s i t i v e
g u i d i n g
o f
t h e
d r i v i n g
b a l l s 8
along t h e i r r a c e
c i r c l e s
by
m ea n s o f
s e p a r a t e
r i n g s
1
o r e q u a l i z i n g
members, each having
the
f o r m of the
race
c i r c l e w i t h a recess for the driv
ing b a l l 6 , a u n if o rm transmission o f the r o t a t i o n
t o
the driven member
s
a c h i e v e d .
This
ar ran g emen t
has the advantage o f ex
t r e m e l y
s i m p l e m a n u f a c t u r e ,
a s s e m b l y and ad
justment,
a s w e l l
as
an
easy exchangeability
o f
a l l parts which have
become worn.
T h e r e d u c t i o n
o f
the d r i v i n g speed t o
t h e
d e
s i r e d
d r i v e n speed
i s
e f f e c t e d
i n
t h e g e a r i n g by
us i ng any
o n e
o f a p l u r a l i t y
o f d i f f e r e n t cam
d i s k s
o f
di?erent
s i z e s an d each with a
d i f f e r e n t
number o f
curves 9 0 in
connecti o n
w i t h a r o l l e r
cage
5 o f
constant
diameter 1 3
a n d ha v i n g
a
con
s t a n t
memb er
o f
r o l l e r s 3 ,
f o r
example,
4 0
r o l l e r s .
By u s i n g
s i x
d i ? e r e n t
cam d i s k s
2
each
w i t h a
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2 , 6 7 7 , 2 8 8
d i f f e r e n t
n u m be r
o f c u r v e s ( f o r
i n s t a n c e
3 8 , 3 ' 7 ,
3 6 ,
3 5 , 3 4 , and
3 3 c u r v e s )
and each h aving a
d i f f e r e n t
diameter
J 9 , and mo unt ing
each
d i s k
o n a orankpin
3 0 wh ic h
has
the
p r o p e r
eccentric
i t y
t o maintain
the
cam i s k i n e ngageme nt
with
the
r o l l s
3
o f
the
r o l l e r
cage
5 ,
s i x
d i f f e r e n t
speed
reductions can be obtained.
I f
the driven
o r
output member, such
a s
the
member i s l o c a t e d
within
the gearing an d con~
s t i t u t e s an
el ement o n t o
w h i c h
the rotation o f
the ?rst cam i s k 2 i s transmitted, a n d such e l e
m e n t i n turn i s journaled f o r r o t a t i o n c o n c e n t r i
c a l l y
Within the gearing an d i s p rovided with a
concentric shaft
e n d
w h ich
p r o j e c t s
f rom
earing
i n
a
d i r e c t i o n
o p p o s i t e
t o
that
o f
the
? r s t cam d i s k 2 , then according t o
t h e i n v e n t i o n
an eccentric piece 9 | can be ?tted o n
t o
t h i s
shaft e n d
a n d
a second cam
disk
2 ’
similar
t o the
f i r s t
cam disk 2 , and
w h i c h a l s o has
curves
or
indentations
which
cooperate with
the
r o l l e r san be m o u n t e d
o n the
e c c e n t r i c p i e c e t i
i n
such
a Way
that
t h e curves or
i nd e nta t i o ns
o f
t h e
seco nd cam disk w i l l e n g a g e the
r o l l e r s
3
i n
the
same
manner
as described w i t h r ef er ence
to
t h e
?rst cam
d i s k
2 .
W i t h t h i s ar ran g emen t the
gyratory mo t io n o f the second cam d i s k 2 ' w i l l
cause i t t o
rotate
backwardly
o n
the
eccentric
piece 9 as described with reference t o the ?rst
cam disk 2 . Such rotary m o t i o n o f the
second
cam
disk 2 ’ may be
transmitted
t o a dr i ven mem~
b e r , such a s
the s h a f t
8 , by b a l l s 5 ’ operating
i n
b a l l
races i n r i n g s 7 ’ carried by
the second
i s k 2 ’
a n d
a l s o by
the member 8 2 m o u n t e d
o n
the shaft 8 i n the s me manner
as the rotation
o f
the ? r s t
cam d i s k 2 i s
transmitted
t o
the driven
member
.
W i t h t h i s
ar ran g emen t the
n u m b e r o f
gyra~
t i o n s
o f
the second cam
d i s k
2 ’
w i l l
be
equalhe R. P . M. o f
the
?rst
cam
i s k
2 . Any e s i r e d
number o f cam d i s k s can
be
a r r a n g e d i n s e r i e s ,
within s e n s i b l e l i m i t s .
F o r
example, the f i r s t
cam
disk may h a v e 33 curves,
the
s e c o n d
cam
disk a l s o 3 8 ,
or
a l t e r n a t i v e l y 3 7 ,
or
3 6 , o r 3 5 , o r
o r 3 3 .
Or,
f o r
example,
the ?rst
cam
d i s k
may have
37
curves,
the
s e c o n d
cam
d i sk also .
3 7 , or alternatively 3 6 o r 3 5 o r 3 4 or 33 e t c . Or,
. T c r e r a m p l e , t h e ? r s t cam o k
may
have
c u r v e s ,
the second 3 5 , a n d t h i r d
c u r v e s .
Each member of
curves
cor resp on ds t o
a
cer~
Pi n reduction r a t i o . This
p o s s i b i l i t y o f i n d i ~
. u a l
combinations
o f f e r s
t h e
advantage
o f a l ~
m o s t
unl imi ted p o s s i b i l i t i e s o f combinations a s a
whole.
T h e d e v e l o pmen t
o f
the gearing a horizon~
t a l , v e r t i c a l , i n c l i n e d ,
or
swingable
gearing does ;
not
o i f e r any d i f ? c u l t y .
F i g .
3
sho ws
o ne
i n d u s t r i a l d e v e l o pmen t o f
the
d e v i c e according t o F i g s . 1 a n d 2 . T h e corre
s p o n d i n g parts
a r e
p rovided with the same r e f
er ence n u m b e r s .
In o rd e r t o
eliminate the disadvantage
o f wear
o f the
race r i n g s ‘ l ,
these transmission parts are
r e p l a c e d ,
i n
the
embod im en t
according
t o L l
t o
by s e p a r a t e
r o t a t a b l e e q u a l i z i n g e l e m e n t s ,
the n u m be r o f which s determined by the t o r - d u e
t o
be
t r a n s m i t t e d .
Such
e q u a l i z i n g
elements
a r e
suppo rted i ndepend ently
o i ‘ each
other
o n b a i l
hearings a n d each i s rotatable about an a x i s that
i s
p a r a l l e l t o
that
o f
the cam i s k .
T h e
r o t a t a b l e e q u a l i z i n g
members
i n thei s k 2 are indicated a t I t a n d each i s m o u n t e d i n
b a l l
bearings 2 9 in
a
r e c e s s i 2 ,
each
e q u a l i z i n g
memb er b e i n g r o t a t a b l e
about i t s
a x i s 2 % ,
which
a s stated
above i s p a r a l l e l t o the a x i s o f the e c ~
c e n t r i c p o r t i o n 3 0 o f t h e s h a f t 5 .
Each
r o t a r y
1 0
20
25
50
6 . .
e q u a l i z i n g membe r i s provided with
a
semi—
s p h e r i c a l r e c e s s - 3 3 t o r e c e i v e a s t e e l b a l l ’ H,
which
may be
a
b a l l
o f
standard manufacture.
The
d i s t a n c e d o f
t h e
c e n t e r
l i n e ’ o f
the b a l l - r e c e i v i n g
r e c e s s 3 3 . fr om
the
axis 2 8
o f
r o t a t i o n
o f
the
e q u a l i z i n g
m e m b e r
0
i s
equal
t o
the
crank
a d i u s
o f
the crankshaft A ‘ o n
wh ic h the cam disk
2 i s
mounted,
and
t h i s
may b e
v a r i e d
de pe n di ng
o n
t h e d e s i r e d
speed
t r a n s m i s s i o n
r a t i o .
The d ri v e n
member
9 s h o w n i n F i g .
4
i s
a l s o
provided
with
t h e r o t a t a b l e
e q u a l i z i n g
members
8 8
s i m i l a r
i n a l l r e s p e c t s t o : an d
c o r r e s p o n d i n g
with t h e e q u a l i z i n g . members
l l }
o f t h e d r i v i n g
member
2 . Each
e q u a l i z i n g
member 3 6 3 i s
m o u n t e d
i n
b a l l bearings 2 9 a n d r o t a t e s about an
a x i s
p a r a l l e l
t o
t h a t o f s a i d d r i v e n
member,
and
i s
a l s o p r o v i d e d .
with
a » semi-spherical r e c e s s t o
receive a
s t e e l
b a l l I l
,
each such
recess b e i ng s i t u
ated w i t h i t s center lo cated at
o n e
s i d e o f
the
a x i s o f
r o t a t i o n
o f s a i d . e q u a l i z i n g member.
T h e
r o t a t a b l e e q u a l i z i n g
members
o f
the
d r i v ~
i n g member r
cam
isk
2
a n d the
d ri v e n
member
9
are
so
disposed
that
each b a l l
H
i s received
partly
in a
b a l l - r e c e i v i n g .
r e c e s s
3 3 -
o f an e q u a l i z
ing member
I i i
o f
the
driving member or
cam
d i s k 2 , a n d
p a r t l y in a
semi-spherical r e c e s s o f
an e q u a l i z i n g
member 5 ) i n the driven member
9 ,
a n d thereby a d r i v i n g connection i s e s t a b l i s h e d
betwee n
the
driving
an d driven members.
During t h e g y r a t o r y motion o f t h e d r i v i n g
m e m b e r
t h e
e q u a l i z i n g
m em be r s
w i l l r o t a t e
about
t h e i r axes a n d only the backward rotation
o f s a i d d r i v i n g member w i l l - be
transmitted
t o
t h e d r i v e n memb er through t h e b a l l s I I , t h e
g y r a t o r y motion
o f t h e
d r i v i n g
member r o l l i n g
out
d u e
t o
the
rotation
o f
the
e q u a l i z i n g
mem
b e r s .
i f ,
f o r i n s t a n c e ,
there
a r e
4 0 ' r o l l e r s 3
t h e
r o l l e r
~ 5 35 curves
or
depressions in
t h e
d r i v i n g
memb er
2 , s a i d d r i v i n g memb er w i l l
make
a complete backawr d rotation about
the
crank p in a t w h e n the crank
shaft
4 ‘ has
i ne
f u l l
r o t a t i o n s .
In F i g .
6
there i s s h o w n a n
e m b o d i m e n t o f the
invention
i n w h ich
the driven
member
s i n d i ~
cated
at
2 5
a n d has m o u n t e d
therein
rotatable
members
2 6 e a c h ‘ .
o f
wh ic h has a central
b a l l
receiving
r e c e s s 3 4 t o r e c e i v e the b a l l l l s o that
each
b a l l
i s o n the
a x i s
o f rotation o f
the
corre
sponding memb er
2 6 .
An
important advantage
o f
t h e c o n s t r u c t i o n
s h o w n
i n F i g s . 4 a n d 6
i s
t h a t , due t o t h e r o t a r y
motion o f the e q u a l i z i n g
members
i t and 2 %
about
t h e i r
a x e s ,
the slow
backward
rotation
o f
the
d r i v i n g
member
i s
transmitted
evenly a n d
unif o rmly
t o
the d ri v e n member o r 2 % a n d thus
t o
the
driven
s h a f t 8 .
T h e bottom o f each s e m i - s p h e r i c a l b a l l - r e c e i v
ing
r e c e s s 3 3 , 3 4
i s pro v i d ed with an adjusting
member i 3 by which
the
b a l l I I can
be
r a i s e d
f rom
i t s
s e a t t o compensate
f o r machining t o l e r
a n c e s ,
t h e r e b y
a v o i d i n g
t h e
n e c e s s i t y o f extreme
p r e c i s i o n i n m a n u f a c t u r i n g .
T h e s t r u c t u r a l d imensi o ns o f t h e e q u a l i z i n g
m em be r s
a r e s t a n d a r d i z e d , thereby s i m p l i f y i n g
replacement
o f
w o r n
p a r t s .
The
gyratory
m o t i o n
o f
the
cam disk 2 has n o
e f f e c t w h e n r o l l i n g i n
t h e s e bodies
o f r o t a t i o n i n
asmuch
a s
the distance
o f
each b a l l f rom the
center
o f
i t s body
o f
r o t a t i o n i n the cam d i s k
i s
e q u a l
t o the r a d i u s o f gyratory motion o f
t h e
cam isk
a n d the bodies o f
rotation
are s u p p o r t e d
i n r o l l e r b e a r i n g s .
D u e
t o
the f a c t , h o w e v e r ,
t h a t
the cam disk a l s o
has a m o t i o n
o f rotation
about
i t s
a x i s
which i s
o p p o s i t e i n
d i r e c t i o n t o
t h e
d i
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7
r e c t i o n
o f
i t s
g y r a t o r y m o t i o n ,
t h e r e
t a k e s
p l a c e
a l a t e r a l
displacement
o f
the
driven member d u e
t o
t h e d r i v i n g
b a l l s ,
h a l f
o f which
a r e
embraced
i n t h e r o t a r y e q u a l i z i n g
members
o f
the cam
d i s k ,
a n d
h a l f i n
the
e q u a l i z i n g
members
o f
the driven
member.
F o r example, by a proper
p r o p o r t i o n ~
ing
o f
the parts i t can be brought about that
t h i s
rotation covers
a f u l l
c i r c l e a f t e r n i n e f u l l
rotations o f
the
crankshaft have acted o n
the
cam
d i sk 2 .
C o n s i d e r e d
geometrically,
any
desired p oi n t
o n
the curved pe ri phe ry o f
the cam
i s k describes an
e l o n g a t e d e n d l e s s s p i r a l around t h e
c e n t e r
l i n e o f
t h e
g e a r i n g ,
the l o n g i t u d i n a l i n t e r v a l s
o f which
are equal t o the di ?erence between
the
n u m be r
o f
r o l l e r s 3
i n
the
r o l l e r
cage 5 a n d the
n u m be r
o f
curves 90 o n the
cam disk
and
the
transverse in—
t e r v a l s o f which are equal t o
the
diameter o f
the
gyratory m o t i o n
o f
the cam d i s k .
This
m o t i o n
w o u l d
t h e o r e t i c a l l y
bring
about a
n o n - u n i f o r m
r o t a t i o n
o f
the driven
shaft
8 .
Ho wev e r , d u e t o
the f a c t t h a t , i n the d e v i c e s o f F i g s. 4
an d
6 , an
imaginary l i n e
fr om the center
o f the r o t a t a b l e
e q u a l i z i n g member I U o f the cam i s k 2 through
the
c e n t e r o f the
d r i v i n g
b a l l H t o t h e c e n t e r o f
the
e q u a l i z i n g
memb er 2 6 o f the
d r i v e n
s h a f ts throughout the e n t i r e
3 6 0 ° g y r a t o r y motion
the o f cam isk , always
in
a r a d i a l l i n e extend
i n g through the a x i s o f the d r i v e n s h a f t and the
particular curve or i n den tation 90 w h i c h at
any
i n s t a n t
i s
completely i n e ngageme nt
with a r o l l e r
3 ,
the
r o t a t i o n
o f
the driven s h a f t i n the u n i t o f
time o f
the
s w i n g i n g
o f the
cam w i l l be de-ac
c e l e r a t e d i n the zone o f
the
l o n g i t u d i n a l
i n t e r v a l
o f
the
imaginary
p o i n t ,
a n d
a c c e l e r a t e d
i n
the
zone
o f the
transverse i n t e r v a l . This
process
causes
a complete e q u a l i z a t i o n
o f
the n o n- u n if o rm
rotation o f
the cam
i s k ,
so as to
p r o d u c e a uni
fo rm r o t a t i o n o f the driven shaft 8 . T h e trans
mission can
be
v a r i e d ,
d e p e n d i n g
o n the
distance
d
s e l e c t e d . I f , f o r i n s t a n c e ,
o n e - h a l f
t h e r a d i u s
o f the crankshaft
i s s e l e c t e d
f o r
d ,
a l ow-speed
t r a n s m i s s i o n with
high po we r
w i l l be
o b t a i n e d .
I f , o n
the
o t h e r hand, 1 i s equal t o
the
r a d i u s o f
the c r a n k s h a f t , the d e v i c e
w i l l t r a n s f e r
a small
am o u n t o f p o w e r
a t
rapid speeds o r
v i c e v e r s a ,
de pe n di ng o n t h e development o f t h e g e a r i n g .
I
c l a i m :
1 . A speed reducing p o w e r transmitting gear
ing
comprising
a d r i v i n g shaft having
eccen
t r i c
portion,
a
disk
member mounted
o n said ec~
c e n t r i c p o r t i o n
f o r r o t a t i o n
t h e r e a b o u t , s a i d d i s k
m e m b e r
having p e r i p h e r a l i n d en t a t i o n s ,
a
stationary r o l l e r cage enclosing s a i d d i s k menu-
her
an d havi ng r o l l e r s
t o
engage s a i d indenta~
t i o n s , the r a d i u s o f
t h e
r o l l e r cage bein g l a r g e r
than
that o f the d i s k m e m b e r by the
e c c e n t r i c i t y
o f t h e e c c e n t r i c p o r t i o n o f t h e
d r i v i n g
s h a f t ,
whereby r o t a t i o n
o f
t h e
d r i v i n g
s h a f t
w i l l pro
d u c e a gyratory m o t i o n o f the
disk member
an:
the
e n g a g e m e n t of
t h e i nd e nta t i o ns i n k
member
with the r o l l e r s o f the r o l l e r cage
w i l l
p r o d uc e a rotation of the disk member at a re
d uce d speed about i t s a x i s , a
d ri v e n
member 00
a x i a l
with the d r i v i n g s h a f t , s a i d d i s k member
having a p l u r a l i t y o f separate c i r c u l a r b a l l
r a c e s ,
each havi ng a diameter
corres po nd i ng
t o the
e c
c e n t r i c
portion
o f
the d r i v i n g
s h a f t ,
2 1 .
b a l l
ach b a l l
r a c e ,
means providing an o p e r a t i v e
d r i v i n g
connection
between each
b a l l
driven
memb er by which the u n if o rm r o t a t i o n
o f
the
d i s k membe r about i t s a x i s
i s transmitted
uniformly and evenly t o the driven member u n~
a f f e c t e d by
t h e g y r a t o r y
motion o f
t h e
d i s k
member .
the
20
50
7 5
8
2 . A speed
r e d u c i n g
po we r t r a n s m i t t i n g g e a r
ing comprising a
driving
shaft havi ng an eccen
t r i c p o r t i o n , a disk member m o u n t e d o n
said
e c
c e n t r i c p o r t i o n f o r
r o t a t i o n t h e r e a b o u t ,
s a i d
d i s k
memb er
having
p e r i p h e r a l
i n d e n t a t i o n s ,
a
s t a
t i o n a r y
r o l l e r
cage e n c l o s i n g s a i d d i s k
memb er
a n d
having r o l l e r s t o engage s a i d i n d e n t a t i o n s ,
t h e r a d i u s o f t h e r o l l e r
cage being
l a r g e r than
t h a t o f
t h e
d i s k memb er
by
t h e e c c e n t r i c i t y o f
the e c c e n t r i c portion
o f the d r i v i n g
s h a f t ,
w h e re
by
rotation o f
the
driving
shaft w i l l pro d uce
a
gyratory
m o t i o n
o f the d i s k member a n d the
e n
gagement o f
the
i n d e n t a t i o n s
i n
t h e d i s k mem
her with the r o l l e r s
o f
the r o l l e r
cage
w i l l
p r o
duce
a rotation o f the disk member a t
a
reduced
speed about i t s a x i s , a
d r i v e n
memb er c o a x i a l
with h e
d r i v i n g
s h a f t ,
a p l u r a l i t y
o f
r o t a r y e q u a l
i z i n g
members
m o u n t e d i n the
d i s k
memb er t o
r o t a t e
about
axes p a r a l l e l t o that o f the driving
shaft
a n d
a l l
situated a t
the
same
distance
f r o m
the c e n t e r
o f
s a i d
d i s k member , each
e q u a l i z i n g
member
ha v i n g
a
b a l l - r e c e i v i n g
r e c e s s situated
e c c e n t r i c a l l y
t h e r e o f ,
a n d a b a l l i n each b a l l
r e c e i v i n g
r e c e s s ,
s a i d driven
member havi ng
r e
c e s s e s in w h i ch
said
b a l l s
are
a l s o r e c e i v e d .
3 . A
peed reducing
p o w e r transmitting mecha
n i s m as d e ? n e d in claim 2 , in w h i ch
the
r e c e s s e s
i n the driven member
a l l
have
the same
r a d i a l
distance f rom i t s
a x i s
o f r o t a t i o n .
a . A
speed reducing
p o w e r transmitting gear
ing compri s i ng
a driving
shaft
ha v i n g
an cccen~
t r i o
portion,
a
disk
member mounted o n said e c
c e n t r i c p o r t i o n
f o r
r o t a t i o n
t h e r e a b o u t , s a i d d i s k
membe r
having
p e r i p h e r a l i n d e n t a t io n s , a s t a
t i o n a r y
r o l l e r
cage
e n c l o s i n g
s a i d d i s k
memb er
and having r o l l e r s t o
engage
s a i d i n d e n t a t i o n s ,
t h e r a d i u s
o f
t h e
r o l l e r
cage
being
l a r g e r
than
that o f the d i s k membe r by the e c c e n t r i c i t y
o f
t h e e c c e n t r i c p o r t i o n o f t h e
d r i v i n g
s h a f t ,
where
by
r o t a t i o n
o f
the
d r i v i n g s h a f t w i l l
produce
a
gyratory
moti o n o f the
d i s k member an d
the
en
gageme nt o f the inden tations
i n
the d i s k
member
with
the r o l l e r s
o f
the r o l l e r cage w i l l pro d uce a
rotation o f the d i s k member at a reduced
speed
about
i t s
a x i s , a
driven
member o a x i a l
with
the
d r i v i n g
s h a f t ,
a p l u r a l i t y o f r o t a r y
e q u a l i z i n g
members
m o u n t e d
i n
the
d i s k
member
t o
r o t a t e
about
a x e s p a r a l l e l t o t h a t o f the d r i v i n g
s h a f t ,
each
e q u a l i z i n g
m e m b e r having
a
b a l l - r e c e i v i n g
r e c e s s
located a
distance
f r o m i t s
a x i s equal
t o
t h e e c c e n t r i c i t y o f t h e e c c e n t r i c p o r t i o n o f t h e
d r i v i n g
s h a f t ,
a
s i m i l a r n u m be r o f b a l l - r e c e i v i n g
members m o u n t e d i n the dr i ven member
t o
r o
t a t e
about
axes p a r a l l e l
t o that
o f
s a i d driven
member ,
each b a l l - r e c e i v i n g
member having an
a x i a l l y l o c a t e d
b a l l - r e c e i v i n g r e c e s s , an d
a p l u
r a l i t y
o f
b a l l s , each o f which s p a r t i a l l y r e c e i v e d
i n the b a l l - r e c e i v i n g r e c e s s o f an equalizing
membe r
a n d
p a r t i a l l y r e c e i v e d i n
the
a x i a l b a l l
receiving r e c e s s
o f
a b a l l - r e c e i v i n g m em b e r .
5 .
A
peed reducing p o w e r
t r a n s m i t t i n g
mecha
n i s m as
d e ? n e d i n
claim 2 ,
i n
wh ic h a p l u r a l i t y
o f
separate e q u a l i z i n g members equal i n
num~
her t o those in the disk
member are
mounted
i n
the dr i ven member
o
rotate
about axes par
a l l e l
t o
that o f s a i d driven member, each
o f
s a i d
l a t t e r
e q u a l i z i n g memb e r s a l s o having a b a l l ~ ~
r e c e i v i n g r e c e s s
l o c a t e d
e c c e n t r i c a l l y
t h e r e o f
an d
a
b a l l
received p artly
i n
the
r e c e s s
o f each
equal
i z i n g
membe r
c a r r i e d
by
the d i s k
membe r an d
p a r t l y
i n
t h e c o r r e s p o n d i n g e q u a l i z i n g member
c a r r i e d by t h e d r i v e n member.
5 .
A peed r educing
po we r
t r a n s m i t t i n g mecha
n i s m
a s d e ? n e d i n
claim
5 ,
i n wh ic h
the eccen
t r i c i t y
o f t h e b a l l - r e c e i v i n g r e c e s s i n each e q u a l
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2 , 8 7 7 , 2 8 8
i z i n g
membe r i n both t h e d i s k
member
and t h e
driven memb er i s e q u a l
t o
one-half the
eccen
t r i c i t y
o f
t h e
e c c e n t r i c p o r t i o n
o f t h e d r i v i n g
s h a f t .
7 . A p e e d r e d u c i n g po we r
r a n s m i t t i n g mecha
n i s m
a s
d e ? n e d
i n
claim
2 ,
i n
w h ich
the
member
d r i v e n
by the
d i s k m e m b e r
o p e r a t e s a s
a d r i v i n g
m e m b e r t o r o t a t e a
driven
s h a f t ,
a n d
d r i v i n g
connections
s i m i l a r t o
t h o s e
between the d i s k
1 0
e m b e r and the d r i v e n memb er a r e employed
t o
d r i v e t h e
d r i v e n s h a f t
from the d r i v e n memb er
a t a speed red uced below that
o f
s a i d driven
member.
R e f e r e n c e s C i t e d i n t h e ? l e o f t h i s
p a t e n t
UNITED
STATES
PATENTS
Number
5
9 1 6 , 9 1 4
1 , 6 4 1 , 7 6 6
1 , 7 3 8 , 6 6 2
1 , 8 4 4 , 4 7 1
2 , 5 2 0 , 2 8 2
Number
4 0 2 , 6 1 7
Name Date
Cooley ___________
_
Mar. 30, 1 9 0 9
Laukhuff
_________
_
S e p t .
6 ,
1 9 2 7
Morison
__________ _
Dec.
10, 1929
Johnson
__________
_
Feb.
9 ,
1932
Henry ___________ _ Aug. 29, 1 9 5 0
FOREIGN
PATENTS
Country Date
I taly
____________ _
Mar. 16, 1 9 4 3