Note: Descriptions are shown in the official language in which they were submitted.
-- 1 --
Mechanism with con-tinuous adjustment for the -transmission
of a rotary motion between two coaxial shafts
The invention relates to a mechanism with continuous
adjustment for the transmission o~ a rotary motion between
an input shaft and a coaxial output shaft comprising a
first concentric wheel integral with the casing and having
two first wheel rims with first conical transmission surfaces,
the axial dis-tance between said two rims being adjus-table,
further comprising a ring with conical surfaces running on
said first transmission surfaces, said ring being rotatably
mounted on a radially displaceable hub adapted to move with
the inpu-t shaft, and further comprising an output member
be-tween the ring and the outpu-t shaft.
A mechanism of this kind in the form of a friction wheel
mechanism has been described in an emoodiment of the
FR~PS 1 332 135, published June 4, 1963 to Fichtel.
Herein, power is -transmitted from the ring onto the wheel.
arranged on the output shaft by means of double conical
disks as intermediate members adjustably spaced from
20: one another, said intermedia-te members alternately
coactlng with the conical surfaces of thering, on
: the one hand, and with the conical transmission surfaces
of the second wheel, on the other hand. The radial adjust-
ment of -the hub is effected by means of an eccentric movable
in the inPut shaft designed as a hollow shaft, a clutch
being provided-between the input shaft and the driving member.
~.~
~ ~ .
r~j
-- 2
Further, the two wheel rims of each concentrlc ~rheel are
acted upon by pressure springs so tha-t the con-tact pressure
between the transmission surfaces is limite~ and great
torques are not transmissible. Because of the great number
of gear members and conical surfaces, the structure of thc
prior art mechanism is very complicated.
A similar mechanisM has also been described in the
AT-PS 222 966, published August 31, 1963 to Vallalat.
The reduction ratio thereof is con-tinuously and precisely
adjustable to the infinite but this mechanism, too,
has constructional de:~iciencies in respect of the
transmission of -the rotary motion between the radially
adjus-table and, hence, eccentrically adjus-table friction
ring and the output shaft, said motion being effected by
means of a wobbling bell-shaped coupling member as output
member. Only at an in:fin.i.-te reduction ratio runs the
wobbling bell-shaped coupling rnember concentrically with
the outpu.t shaft, but malcec a wobbling motion ~t any other
posit:ion, whereby a double cardan joint with the friction
r:ing and the output shaft is obtained. The radial adjustment
of the ~riction ring towards the input shaft is forced by
: the approach of the two friction rims of the friction wheel
integral with the casing, away from the input shaft,
howeverj by means of a spring biased between the input shaft
: 2S and the hub. In this case, it has also been found that in
-the transmission of particularly great torques, the spring
inserted between the input shaft and the hub is not able to exert
'''~ ``'~
~),'7~
-- 3 --
the required contact pressure between the fric-tion riny
and the friction wheel, particularly when irregular loads
occur.
It is the object of the invention to improve and simplify
a mechanism of the above-mentioned kind in its working part.
Moreover, in a preferred embodiment, a forced displacement
of the wheel rims and the hub of the ring in both directions
shall be obtained in order to be able to transmit also
particularly great torques.
According to the invention, this is achieved by that a
second wheel concentrically arranyecl on the output shaft
: is provided as an output member, said second wheel having
. second wheel rims with second conical transmission surfaces,
~` t.he axial distance of .said second rims being adjustable,
said r:ing also running on said second conical transmission
surfaces the transmission ranges between said ring and
:: said first wheel in-tegral wi-th the casing as well as said
second wheel xotatable with said ou-tput shaft being offset
by 180.
:~ ~ 20 The offset arrangement of the transmission regions by
~:~ 180 has already been known from toothed gearings with
:~ : eccentric double-toothed intermediate member, e. g. from
the U5-PS 546.249, puhlished September 10, 1895 to Regan.
'
. I
: ; . .
:
2~3~
The eccentrically adjustable ring is now on the one hand,
according to -~he AT-PS 222.966, with its outwardly directed
transmission surface pressed into the first concentric
wheel integral with the casing, on the other hand, due to
the solution according to the invention, with its inwardly
directed transmission surface forced into the second wheel
which is also concentric and linked to the output shaft.
- The transmission of the rotary motion between the radially
andt hence, eccentrically moving ring and the second concentric
wheel is thereby direct without intermediate member. As
preferably one wheel rim, each, of the two concentric wheels
is undisplaceable in axial direction and, therefore, an axial
adjustment of the ring is simultaneously required with its
radial displacement because of the conical surfaces, it may
1~ be provided that the ring is arranged on the hub to be axially
displaceable. It is, however, also possible to link the hub
to the ring to be axially undisplaceable and to provide,
instead, the possibility of axially displacing the hub in
respect of the input shaft. The change in the axial
distances of the wheel rims of the second wheel is obtained
by its being axially coupled to the first externsl wheel,
whereby it is preferably provided that one of said wheel
rims, eachj of said two wheels is axially undisplaceable
and that said other wheel rims of said wheels are co~nonly
axially displaceable by means of an adjustment device, a
rolling bearing being arranged between said the two
displaceable wheel rims of said two wheels.
:
,
.
For the forces radial adjustment of the hub in both
directions, i.e. for altering its eccentricity, an
embodiment further provides that said hub of said ring
is associated with an adjustment device acting by means
S of a pressure member rotatably mounted on said input
shaft upon an axially displaceable driving member
radially moving said hub. At least one compensating
body may advantageously be coupled to the hub, said body
being radially displaced opposite to the hub by said - i
axially displaceable second driving member in order to
obtain at least a static balance of the hub.
- The mechanism according to the invention has the further
advantage that the mass of the eccentrically adjustable
structural members is restricted to the friction ring so
1_ that a reduced inversel~ alterable compensating mass is
req~ired for compensating the changing unbalanced mass.
The mechanism according to the invention further provides
the possibilitiy of arranging the balancing weights axially
.
at both sides of the fric~ion ring so that not only a
static but also a dynamic balance is obtained.
; '
The radial displacement of the hub may, according to one
embodiment, be effected by means of hinge links trans-
ferring the axial motion of the intermediate members into
- a radial notion Oe the hub.
I .
-
.
1~ ~;'72F~
A further embodiment provides wedge surfaces effectinamoving connection between the driving member and the hub.
The adjustment device for changing the distance of the wheel
rims is provided on the output side, the adjustment device
for the hub on the input side of the
mechanism. The two adjustment devices can be coupled so
that the displacement of the wheel rims and the hub is
precisely adapted to one another. In a preferred embodiment,
a single adjustment device is provided axially acting upon
said axially displaceable wheel rims of said two wheels and,
further upon said axially displaceable member of the hub,
- Moving connection between said axially displaceable driving
member of said input shaft and said axially displaceable
wheel rims of said two wheels may be effected by connecting
1~ elements r~dially exter"ling betwee. said axially displaceable
wheel rim of said second wheel rotatable with said output
shaft and a ring associated with said driving member and
relatively movable thereto, said connecting members extending
through slots parallel to the axes and arranged in the
20 ~undisplaceable wheel rim of said second wheel rotatable
with said output shaft,
The mechanism according to the invention may be a friction
wheel mechanism with conical friction rims. A preferred
embodiment of the invention provides, however, all conical
25 transmlssion surfaces of said two wheels with a toothing
formed by substantially radially extending grooves, ribs
.
~ . ,.. ... , ~ .. , . .. ....... . . . . , .. . . , i
7;~
being arranged between said grooves, said grooves and
said ribs of the two transmission surfaces of each of said
wheels lying alternately opposite one another, and provides
further that two rims of axially free toothing elements
meshing with said grooves of the transmission surfaces are
arranged in the ring, said toothing elements being formed
by sets of lamellas individually displaceakle parallel to
the axis and each of said lamellas projecting from said
ring by the depth of one of said groove.
The rims of toothing elements are arranged in the two
regions of the ring having conical surfaces, openings
of square or rectangular cross-sections being provided
-~herein. The sets of lamellas forming the toothing
_13~ents have a trapezoid shape, whereby the angle of
1, ~clin~tion oE the lamellas corresponds to the :,ne of
t~ co~ical surfaces.
: . ,
In order to obtain an impeccable meshing of the toothing
elements with the grooves, when moving into the trans-
mission regions as well as when mo~ing out from the trans-
.
- i
. ~-.; ~ , ,.
'7~
mission regions, a further preferred embodiment provides
that.the grooves in the transmission surfaces of the fir.~t
wheel integral with the casing are adapted to diverge
towards the axis of the mechanism, and the grooves in the
5 transmission surfaces of the second wheel rotatable with
the output shaft are adapted to converge towards the
axis of the mechanism.
. . .
As during the motion of the toothing elements through the
non-meshing regions, particularly at the greatest possible
... 10 radial displacement.of the ring, the wheel rims do
possibly not form a lateral stop for the individual axially
~ee lamellas, the invention further provides that each
mella has a trapezoid shape, whereby limiting stops for
e axial movement of the lamellas proiect from the end
1~ ~artions of the long side of thè trapezoid.
~ DesFription of the figures of the drawiny
;: '
~ -In the following several embodiments o~ the invention will
.. . .
be described in greater detail by means of the figures of
the drawing without being limited thereto. I
20 Fig. 1 shows a longitudinal sectional view of a first em- !
bodiment of a friction wheel mechanism with a first adjust- ¦
ment device;
Fig. 2 shows the arrange~ent and position oE the balancing
weights, the ring being irl centric position;
FigO 3 shows their arrangement and position, when the ring
is in eccentric position;
Fig. 4 shows a longitudinal sectional view of a second
embodiment of a friction wheel mechanism with a second
adjusbment device;
Fig. 5 shows a section along line V - V of Fig. 4;
: .
Fig. 6 shows a longitudinal sectional view of a third
~odiment with toothing and a combined adjustment
~v~ce;
F~g. 7 shows a section along line VII - VII of Fig. 6;
Fig. 8 shows a section along line VIII - VIII of Fig. 6;
;
Fig. 9 shows an enlarged view of portion A of Fig. 6j
~ 15 Fig. 10 shows a sectional view of portion A along line
:~: X - X of Fig~ 9;
Fig. 11 shows a sectional view along line XI - XI of Fig.
0; and
7~
-10 ~
Fig. 1~ shows a longitudinal sectional view of a fourth
embodiment with a second combined adjustment device.
Description of preferred embodiments
The mechanism according to the invention illustrated in
Fig. 1 comprises an input shaft 1 and an output shaft 12
coaxial thereto. A hub 2 is rigidly connected with the
input shaft 1 but arranged to be eccentrically and, if
desired, also axially displaceable. To this end, the in-
put shaft 1 has a square portion 17 in the region of the
hub 2. The recess 18 has the same breadth but a greater
1ength than the square poriton 17 so that the hub 2 is
d~splaceable in longitudinal direction of the recess 18.
T~ hub 2 is surrounded by a radial rolling bearing 21 on
~hi~h a cranked disk 3 lS rotatably mounted. A ring in the
S lorm or a riction ring is laterally fastened to the disk
3, said ring having four Gonical transmission surfaces 30,
31 and a convex octangular cross-sectionO The ~wo outwardly
directed conical transmission surfaces 30 engage between
; two ~heel rims 7, 8 of a first external wheel 6 rigIdly
Zo connected with the casing 5, whereby the~ coact in one
:~ . t region with the transmission surfaces 33 of the wheel rims
7, 8. The two wheel rims 7, 8 are adapted to change their
distance between each other, which is effected by axial
displacement of one wheel rim 8.
" ~ . .
The two other inwardly directed conical transmission sur-
faces 31 of the ring 4 engage between two wheel rims 10,
11 of a second internal wheel 9 whose distance to each
other is also alterable, whereby the transmission surfaces
31 coact with the transmission surfac~s 34 of the wheel
rims 10, 11 in a region offset by 180, In the illustrated ,.
embodiment, one wheel rim 10 is axially undisplaceable and
the second wheel rim .11 is axially free, whereby the
àxially free second wheel rim 11 is unrotatable mounted
1U on a cranked part of the second wheel 9. .
... ' . :
~he second wheel 9 is unrotatably connected with the out-
~u~ shaft 12. The planes o~ symmetr~ of the two wheels 6,
~ ~ as well as of the ring 4 coincide so that tilting
:~ .~ments are almost impossible.
.15 ~e ~wo axially displaceable wheel rims 8, 11 are ad-
j~stable by means of a common first adjustment device,
' whereby an axial rolling bearing 13 is arranged between
the two wheel rims 8, 11, as they turn relatively to each
other. The adjustment device .~, has an adjustment ring
~: ~ 20 15 adapted to move on a thread 14 of an annular extension
32 integral with the casing and surrounding the output
sha~t.12.'The adjustment ring 15 acts upon several inter-
,mediate members'16 formed by bolts axially displaceable in
',bores 28 of the casing side wall 29 and resting against .
25 :the'displaceable'wheel rim 8 of the external wheel 6 in- I
'7~B~
-12 -
teyral with the casing. A movement of the adjustment ring
15 e~fects a joint change in the wheel rim distance bet-
ween the two wheels 6, 9.
The eccentric arrangement of the ring 4 effects an
oscillating motion of the ring 4, when the input shaft 1
is rotated, the external transmission surfaces 30 running
on the transmission surfaces 33 on the wheel rims 7, 8
of the external wheel 6. The required contact pressure
is obtained by means for increasing the eccentricity, in
the embodiment illustrated in Fig. 1 said means being
formed by a spring 19 inserted into the recess 18 of the
- . hub 2 and radially abutting the square portion 17 of the
input shaft 1. Other parts may be pro~ided instead of the
spring 19, e.g. a hydraulically extensible structural
member or the like. Further possibili_ies will be described
later on b~ means of Figs. 4 and 7 A spring 19 may be .
used, when transmitting lower torques and in case of
constant load as the spring power which increases with
: incxeasing compression can by means of a suitable spring
be substantially adapted to the torque to be transmitted
and increasing w1th decreasing eccentricity.
.
The motion of the oscillating ring 4 is simultaneously
transmitted on-to the second internal wheel 9 in -the same
~ direct manner, whereby the transmission surfaces 31 of the
:~ ~ 2S ring 4 run on the transmit~ion surfaces 34 of the wheel 9.
-
: ~
Hence, no further output members are re~uired, and the massof the eccentrically moving structural members is re
stricted to the disk 3 with the ring 4.
By means of the position of the ring 4 illustrated in Fig.
1, a medium reduction ratio is obtained. When its distance
from the casing side wall 29 is increased by turning the
ad~ustment ring 15, the distances between the wheel rims
7, 8 and 10, 11 of the two wheels 6, 9 are simultaneously
increased. By means of the spring 19, the eccentricity
of the hub 2 and the disk 3 and, hence, also of the ring
4 is increased, and the wheel rims 7, 8 and 10, 11,
- respectively, are moved from each other, whereby the
spring 19 simultaneously provides for the required con-
ct pressure onto the external as well as onto the
l~ ~ ternal wheel. Therby, a slight a~ial displaceAment o~
t~e riny 4 occurs. The increase in eccentricity entails
decrease in the xeduction ratio, which is dependen~ on
the dif~erence in diamenter o:E the external wheel 6 and
the ring 4 and inversely proportional to the eccentricity.
: ~ :
When~approaching the wheel xims 7, 8 and 10, 11, re-
spectively, by turning the adjustment xing 15, the ring
4 is pressed inwardly against the spring 19 and its
:: :
eccentricity is reduced~ In the extreme, eccentxicity
is zero so that the hub 2 is exactly centrically arranged
on the input shaft 1. In this case, the hub 2 runs freely
; .
- ~
-14
through the radial rolling bearing 21, and the rotary
motion of the hub 2 is not transmitted onto the disk 3.
The reduction ratio is infinite in this case.
For compensating the unbalanc~d mass of the changing
eccentric ity, oppositely movable compensating bodies 23
are provided. In Figs. 2 and 3, the arrangement of the
compensating bodies is shown in the two limit positions~
Fig. 2 shows the position in which the infinite re-
duction ratio is given, in which there is no unbalanced
mass in the hub 2. The compensating bodies 2~ are arranged
sy~etrically to ~helongitudinal axis of the!recess 18
. .
of ~he hub 2 at intersecting levers 22 having longitudinal
- holes 25. The levers 22 are pivotally mounted on bolts 24
extending through the longitudinal holes 25 and projecting
o~er the hub in axial direction. A displacement of the
hub 2 into theposition illustrated in Fig. 3 efects an
opposite motion of thetwo compensating bodies 23 and,
hence, a static balancing of the hub. A dynamic balance
is obtained by axially arranginy the compensating bodies
23 at both sides of the hub.
In the embodiment according to Fig. 4, the radial eccentric
I ~ adjustment of the hub 2 forcedly in both directions is,
on the one hand, illustrated by a separate adjustment de- ¦
;~ vice~and, on the other hand, the adjustment device shown in
~ig. 1 is replaced by readjustment springs 35. The
structure of the mechanism and the arrangement of the
two concentric wheels 6, 9 and of the radially displace-
able ring 4 remaining the same, the adjustment device for
the radial adjus.tment of the hub 2 of the ring 4 is
arranged on the side o.~ the casing 5 directed to the
input sha~t. The casing side wall 51 is in this embodiment
provided with a hollow cylindrical extension 45 coaxial
to the input shaft 1~ said extension having an external
thread 40. An.adjustment ring 36 is movable on the thread
40 and presses by means of pressing bolts 37, which extend
- through the casing si.de wall 51, onto a stationary pres- ¦
sure plate 38. The square portion 17 of the input shaft 1,
in contrast to the embodiment o~ Fig. 1, extends on both
sides over the hub 2, whereupon a drivi-ng member 27 is
arranged in an unrotatable but axially displaceable manner.
The driving member 27 is, due to a:.recess 53, also radially
; dl~placeable and forms a first compensating body 42. The
recess 53 has the same breadth as the square por~ion 17 but
20 ~ a greater length. On the part of the square portion 17
. . directed towards the casing side wall 51, an intermediate
plate 39 is fur~her arranged in a unrotatable and axially
displaceable manner. Between the stationary pressure plate
; 38 and the intermediate plate 39 adapted to more with the
: 25 input shat, an axial rolling bearing 43 is provided, and`
between the intermediate plate 39 and the driving member
..27 a thrust bearing 44 is inserted. The thrust bearing
:3 ~ i"7Z~
- 16 -
serves to reduce the friction between the coaxial inter-
mediate plate 39 and the radially free driving member 27
and may, for example, be formed by rollers or balls re-
tained in a cage, which has not been illustrated, said
rollers or balls running in grooves 52 extending in the
radial direction o-E displacement. The driving member 27,
therefore, serves as compensating body 42 for balancing
- the hub 2, as it is radially displaceable opposite to
~the hub. In order to radially transmit onto the hub 2
the pressure exerted on the driving member 27 by the ad-
justment device, ~our hinge levers 41 are provided, one
pair, each, forming parallel guiding means. For receiving
the hinge levers 41, the driving member 27 is provided at
~oth sides of the recess 53. Two hinge axles 48 extend
~hrough the driviny member 27 parallel ~o the shor~er side
of the recess 53 and form the bearings for the ninge links
¢~ arranged in pairs. Two oppositely arranged hinge levers,
.
each, are connected in the center hy means of a guiding
bolt 47 mounted in a longitudinal slot 46 of the square
2~ portion 17 in an axially displaceahle manner. The other
.
ends of the two-arm hinge levers 41 are in the same manner
mounted in the hub 2, as can clearly be seen in Fig. 5.
The hub 2 also has two slots 50 extending parallel and at
both sides of the longer side of the recess 18 into the
25~ hub 2. The ends of the two-arm hinge levexs 41 are mounted
in hinge axles 49 extending parallel to the shorter side
of the recess 18 through the hub 2. An axial pressure onto
'7~
- 17 -
the driving member 27 displaces the yuiding bolts ~7 in
the longitudinal slot 46. As the wheel rims 30, 31 of the
ring 4 rest against the wheel rims 33, 34 of the wheel
6, 9, there is no possibility of freely displacing the
hub 2 linked to the ring 4 by means of the disk 3. The
hinge levers 41 are, therefore, pivoted around the guiding
bolts 47, whereby the hub 2, on the one hand, and the
driving member 27, on the other hand, are radially dis-
placed but into opposite directions.
In order to obtain a dynamic balance of the hub 2 and
of the disk 3 carrying the ring 4, a further equally
designed compensating bod~ 42 is preferably arranged on
th2 part of the sguare portion 17 of the input shaft 1
~lrected towards the output sha~t 12, said compensating
~ody 42 being also linked to the hub 2 by means of hinge
le~ers 41 arranged in pairs~ The hinge levers 41 are also
g~ided in the slots 50 and mounted on the hinye axles 49.
These hinge levers 41, too, are provided with guiding
bolts 47 which are also guided in the longitudinal slot
46 of the square por tion 17 in an axially free manner.
~ .
This structural design on the second adjustment de~ice
is suitable for the embodiment illustrated in Fig. 4 as
.
well as for an embodiment corresponding to Fig. 1. The
radial displacement of the hub 2 also eEfects a radial
displacement of the hub because of the conical transmission
ilL.~lt;~
_ 18 _
surfaces 30, 31, 33, 34. When ac-tuating the adjustment
device, the compensating body 42 on the side of the out-
put shaft will, hence, remain substantially axially un-
changed and will be radially adjusted only. It is also
possible, however, that the hub 2- is not axially displaced
in respectof the input shaft 1 but that the disk 3 is
axially displaced' in respect of the hub 2. In thIs case,
the two compensating hodies 42 are alterna-tely axially
displaced, when the adjustment device is actuated.
In the embodlment according to Fig. 4, several read just-
ment springs 35 are prestressed between the casing side
wall 29 and the displaceable wheel rim 8 of the external
-~neel 6 for readjusting'the two displaceable wheel rims
~:r 1'I 0~ the wheels 6, 9.
~ ~ .
n the illustration shown in Fig. 6, the adjustment of th~
eccentricity of ~he ring 4 as well as the axial displace-
ment o the wheel rims 8 and 11 of the wheels 6 and 9,
-respectivelyr is in both directions forced by a common ad-
justment device.
20 The essential parts of the mechanism correspond to the em- ;
bodiment according to Fig. 1 or 4. On the input shaft 1 a
radially displaceable hub 2 is arranged which makes a disk
3 mounted on a radial rolling bearing 21'oscillate, when
the input shaft is rotated. The first concentric wheel 6
:
- 19 -
is linked to the casing 5, said wheel 6 beiny formed by
the stationary wheel rim 7 and the axially free wheel rim
8 having conical transmission surfaces and a toothing,
which will be described in greater detail later on. The
second concentric wheel 9 is linked to output shaft 12 and
is al-so formed by the s~ationary wheel rim 10 and the
axially free wheel rim 11. Their transmission surfaces 34
are also conical and provided with a toothing. The common
adjustment device has an adjustment ring 55 adapted to
move on a thread 58 of an axial casing extension 32. A
1ange 57 of the adjustment ring 55 engages behind hook-
shaped intermediate members 56 axially extending through
- the side wall 29 of the casing and linked to the displace- -
~ble wheel rim 8 o the first concentric wheel 6. ~s can
~o b~- seen in Fig. 7, a rolling bearing 59 adapted to
~ar load in axial direction, e.g. a radial-groove ball
~ear~n~r is, irst arranged in the displaceable wheel rim
; -- 8 of the fi~st wheel 6 and, second, in the displaceable
wheel rim 11 of the second wheel 9 adapted to move with
the output shaft 12, whereby the two wheel rims 8, 11 are
jointly displaceable but individually rotatable. From the
wheel rim 11 of the second wheel 9, linking elements 61
extend radially to a ring 62, whereby the linking elements
61 extend through an axially running part of the undisplace-
abLe wheel rim 10 of the second ~heel 9 in which corres-
~ponding slots 60 are provided. By means of the linking
elements 61, an unrotable but axially displaceable connec-
tion between the wheel rims 10 and 11 of the second wheel
9 i5 obtained. One part of a further rolling bearing 63
adapted to bear axial load, e.g. a radial-groove ball
bearing, is associated with the ring 62 surrounding the
S input shaft 1, the second part thereof being coupled to
a flat driving member 54 which is axially displaceable on
the input shaft 1 and engages in grooves 67 of the input
shaft 1 and is, hence, unrotatably linked thereto. The
flat driving member 54, which is preferably a two-part
10 member, also extends through a slot 66 of the input
. shaft 1 and is on the other end reinforced by a ring 79
linked thereto. Two wedge surfaces parallel to each other
are provided on thedriving member 54, said wedge surfaces
. engaging in grooves 65 of the hub 2, the bases of said
grooves being corresponding wedge surfaces. ~ig. 8 shows
a sectional view o~ a mechanism in this region. When
~ctuating the adjustment device, which effects the axial
~isplacement of the driving member 54, the hub 2 is
radially free and transmits its radial motion by means of
: ~0 t~e rolling bearing 21 onto the disk 3 and its ring 4
whose transmission surfaces 30, 31, which are offset by
180, run, on the one hand, on the transmission surfaces
- 33 of the first wheel 6 and,on the other hand, on the
--- - '
transmission surfaces 34 oE the second wheel 9. As the
transmission surfaces 30, 31, 33, 34 are conical surfaces
t and the wheel rims 7 and 10 are axially undisplaceable,
: the coupled axial displacement of the wheel rims 8 and 11
~; and the radial displacement of the hub 2 simultaneously
.
'
. ~
7~
effects an axial displacement of the ring 4 which is
possible because o~ a ring 69 surroundiny the rolling
bearing 21, said ring 69 having ribs engaging in grooves
68 of the disk 3 in order to prevent the relative rotary
motion between the ring 69 and the disk 3.
In this case, the grooves 68 do not run parallel to the
axis but are also inclined towards the input shaft 1 so
that the bases o~ the grooves 68 and the ribs of the ring
69 also form wedge sur~aces 85, which are parallel to
each other. The angle between two wedge surfaces 64 and
85 c~rresponds to the angle bet,ween the transmission sur-
faces 33, 34 and the axis of the mechanism.
Tn the previously described embodiments according to Fig.
1 and 4~ ~he transmission surfaces 30, 31, 33, 34 are
1~ riction surfaces so that the'mechanisms are conical-disk
~riction wheel mechanisms.
'
The embodiment according to Fig. 6 ist, however, provided
with a toothing between the conical transmission surfaces
which will be described in greater detail in the following
with reference to Figures 9 - 11. In the ring 4, two rims
are formed by openings 74 having rectangular or square
cross-sections (Fig. 8, 10), a set o~ inidvidually axially
, free lamellas 75 being inserted into each of them. The
lamellas in Fig. 9 are substantially trapezoid, whereby the
' :
~,.. ' . ' '
72~
22
side edges form an angle with the base line which corres-
ponds to the angle between the transmission surfaces 33,
34 and the axis of the mechanism. Grooves 71 and ribs 72
runningsubstantially radially therebetween are provided in
the transmission surfaces 33, 34. The number of c3rooves 71
and ribs 72 is of minor importance, it is essential, how-
ever, that opposite one rib, each, in one transmission
surface 33 and 34, respectively, one groove 71 is formed in
the other transmission surface 33 and 34, respectively, of
the same wheel 6 and 9, respectively. Each lamella 75 of
the external rim of toothing elements 70 either engages in
a groove 71 of the axially undisplaceable wheel rim 7 or
the axially free wheel;rim 8 (Fig. 11 ) and rests with the
opposite side against the upper side of a rib 72 as the
t3 ~r2adt~0f each groove 71 at least corresponds to the
~read~h of one rib 72, the breadth preferably being slightly
; ~reater This is also true for the lamellas 75 of the in-
- -- ternal rim o toothing elements 70 offset by 180 and
associated with the grooves 71 and the ribs 72 of the
Sransmission surfaces 34 of the wheel rims 10, 11 of the
second wheel 9. All grooves 71 in both transmission sur-
~aces 33, 34 of both wheels 6~ 9 may have parallel side
walls, but they preferably di~erc3e into the direction of
the ring 4 to improve engagement and disengagement of the
~;~ 25 sets of lamellas in the transmission regions, as the radii 4
of the rims of toothing elements 70 differ from those of
the wheel rims 7, 8, 10, 11.
:
'7~
When changing the distance between the wheel rims 7, 8
and 10, 11, the lamellas 75 are displaced in the grooves.
To make the same lamellas 75 remain in one groove 71, the
radial displacement would, corresponding to the increasing
or decreasing breadth of the ribs 72, require an increa~e
or decrease in the distance between the sets oP lamellas.
A5 this is not possible, lamellas 75 which are forced out
from a groove 71 of a wheel rim move into an oppositely
offset groove 71 of the second wheel rim. Thereby, a con-
tinuous positive meshing of all toothing elements is ob-
tained in spite of the radial displacement of the ring 4.
As the axially free motion of the lamellas 75 is not
impaired outside the meshing regions, and as depending on
,~e pitch angle of the transmission surfaces 30, 31, 33,
1~ 3~1 ,heir axial motion is not impaired ~y said surfaces, the
l?.mellas are in the end portions of their longer sides
provided with limiting stops 76 projecting inserting slots
-- 73 are cut from the outer ring surface into the ring 4 in-
to each opening 74, said slots being closed again after
~20 the insertion of the lamellas (Fig. 10). This can be done
without weakening the mechanism, as the lamellas 75 are
- exposed to radial stress towards the center of the ring
4, i.e. towards the fastening region of the disk 3.
`
Fig. l2 shows a further embodiment of a mechanism accor-
ding to the invention in which a combined adjustment devLce,
also similar to Fig. 4 t iS arranged on an axial casing ex-
f
.
7~
- 2~ -
tension 45 which is arranged on the side oE the input shaf-t
and carries a thread 40. An adjustment ring 80 has again
a hook-like flan~e engaging behind intermediate members
83, and the intermediate members 83 which extend through
the casing side wall 51 are fastened to a ring 84 in-
clu ing a second axial thrust bearing 82. A pressure plate
79 which is unrotatably retained in a groove
67 of the input shaft 1 engages in the thrust bearing 82,
the driving member 54 extending through a slot 65 of the
input shaft 1 and having two parallel wedge surfaces 64
being retained on said pressure plate. On the other side
of the driving member 54, a further axial thrust bearing
77 is arranged to which radially projecting linking ele-
ments 81 are associated in spoke-like manner. The linking
1~ elements 81 extend through slots 60 in the stationary
~heel rim 10 of the second wheel 9 as well as through
: ~ores in the displaceable wheel rim 11 of the second
. wheel 9 and terminate in a further axial thrust bearing
78 inserted into the displaceable wheel rim 8 of the first
wheel 6 integral wi-th the casing. Actuation of the ad-
justment ring radially displaces the hub 2 guided on the
wedge surfaces 64 and effects a joint axial displacement
of the two di splaceable wheel rims 10, 11. Otherwise, the
structure of the mechanism in respect of arxangement and
design of the ring 4 corresponds to the embodiment accox~
ding to Fig. 6. In this case, too, a toothing between the
transmission surfaces 30, 31, 33, 34 has been illustrated
.
i'72~3~
.
~ 25
but friction surfaces may equally be provided.
The mechanism according to the invention has a continuous-
ly adjustable reduction ra~io, coaxial input- and output
shafts, a particularly space-saving and simple structure,
and it is, due to the indirec~ power transmission by means
of the ring 4, also particularly suitable for great torques
and irregular loads. The infinite reduction requires no
additional clutch and allows particularly smooth handling
of the mechanism.
:
~ . I
,
-
I
.
, ~ ' ~ . I
: : I
