U.S. patent application number 13/817010 was filed with the patent office on 2013-06-06 for cone/friction ring transmission and method for a cone/friction ring transmission.
This patent application is currently assigned to Ulrich ROHS. The applicant listed for this patent is Werner Brandwitte, Christoph Draeger, Ulrich Rohs. Invention is credited to Werner Brandwitte, Christoph Draeger, Ulrich Rohs.
Application Number | 20130143713 13/817010 |
Document ID | / |
Family ID | 45528516 |
Filed Date | 2013-06-06 |
United States Patent
Application |
20130143713 |
Kind Code |
A1 |
Rohs; Ulrich ; et
al. |
June 6, 2013 |
CONE/FRICTION RING TRANSMISSION AND METHOD FOR A CONE/FRICTION RING
TRANSMISSION
Abstract
In order for it to be also possible to transmit relatively high
torques in an operationally reliable manner with low power loss and
with a low or inexpensive design outlay in a bevel friction ring
gear mechanism, consisting of at least two component transmissions
which are configured as bevel friction ring gear mechanisms and
have a first adjusting device for a friction ring of the first
component transmission and a second adjusting device for a friction
ring of the second component transmission, wherein the bevel
friction ring gear mechanism has a regulating device for regulating
an axial position of the friction rings, it is proposed that the
regulating device has at least one first part regulating device
with a first reference variable and a second part regulating device
with a second reference variable which is separate from the first
reference variable, wherein the first component transmission has
the first part regulating device for regulating the position of the
friction ring of the first component transmission, and the second
component transmission has the first part regulating device and the
second part regulating device, but at least the second part
regulating device, for regulating the position of the friction ring
of the second part transmission.
Inventors: |
Rohs; Ulrich; (Dueren,
DE) ; Draeger; Christoph; (Langerwehe, DE) ;
Brandwitte; Werner; (Langerwehe, DE) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Rohs; Ulrich
Draeger; Christoph
Brandwitte; Werner |
Dueren
Langerwehe
Langerwehe |
|
DE
DE
DE |
|
|
Assignee: |
ROHS; Ulrich
Dueren
DE
|
Family ID: |
45528516 |
Appl. No.: |
13/817010 |
Filed: |
August 16, 2011 |
PCT Filed: |
August 16, 2011 |
PCT NO: |
PCT/DE11/01597 |
371 Date: |
February 14, 2013 |
Current U.S.
Class: |
476/1 |
Current CPC
Class: |
F16H 15/42 20130101;
F16H 61/6649 20130101; F16H 61/6648 20130101; F16H 61/26 20130101;
F16H 61/664 20130101 |
Class at
Publication: |
476/1 |
International
Class: |
F16H 61/26 20060101
F16H061/26 |
Foreign Application Data
Date |
Code |
Application Number |
Aug 16, 2010 |
DE |
10 2010 034 502.4 |
Jan 18, 2011 |
DE |
10 2011 008 863.6 |
Claims
1. Cone/friction ring transmission consisting of at least two
subsidiary transmissions structured as cone/friction ring
transmissions, which have a first adjustment device for a friction
ring of the first subsidiary transmission, and a second adjustment
device for a friction ring of the second subsidiary transmission,
wherein the cone/friction ring transmission has a regulation device
for regulation of an axial position of the friction rings, wherein
the regulation device has at least a first subsidiary regulation
device having a first reference variable, and a second subsidiary
regulation device having a second reference variable, which is
separate from the first reference variable, wherein the first
subsidiary transmission has the first subsidiary regulation device
for regulation of the position of the friction ring of the first
subsidiary transmission, and the second subsidiary transmission has
at least the second subsidiary regulation device for regulation of
the position of the friction ring of the second subsidiary
transmission.
2. Cone/friction ring transmission according to claim 1, wherein a
regulation variable of the first subsidiary regulation device is a
reference variable of the second subsidiary regulation device.
3. Cone/friction ring transmission according to claim 2, wherein
the reference variable of the first subsidiary regulation device is
a reference variable of the second subsidiary regulation
device.
4. Cone/friction ring transmission according to claim 1, wherein
the reference variable of the second subsidiary regulation device
is a reference variable of the first subsidiary regulation device,
corrected by way of a position offset characteristic field.
5. Cone/friction ring transmission consisting of at least two
subsidiary transmissions structured as cone/friction ring
transmissions, wherein the subsidiary transmissions have an input
cone and a common output cone, in each instance, according to claim
1, wherein the common output cone has a press-down device.
6. Cone/friction ring transmission consisting of at least one input
cone and one output cone, and a friction ring disposed between the
input cone and the output cone, enclosing at least one cone,
according to claim 1, wherein the cone/friction ring transmission
has a device for measuring the speed of rotation of the friction
ring.
7. Cone/friction ring transmission according to claim 6, wherein
the device for measuring the speed of rotation of the friction ring
detects the speed of rotation of the friction ring directly on the
friction ring.
8. Cone/friction ring transmission according to claim 7, further
comprising a guide device that is axially displaceable with the
friction ring, on which the measurement device is disposed.
9. Cone/friction ring transmission consisting of at least one input
cone and one output cone and a friction ring disposed between the
input cone and the output cone, enclosing at least one cone,
according to claim 1, further comprising a torque measurement
device.
10. Cone/friction ring transmission consisting of at least one
input cone and one output cone and a friction ring disposed between
the input cone and the output cone, enclosing at least one cone,
according to claim 1, wherein a torque converter is disposed
between an input shaft of the cone/friction ring transmission and
the input cone.
11. Cone/friction ring transmission according to claim 10, wherein
the input cone has a lower torque than the input shaft.
12. Cone/friction ring transmission according to claim 10, wherein
the input cone has approximately half the torque of the input
shaft.
13. Cone/friction ring transmission according to claim 10, wherein
the torque converter comprises a gear wheel transmission.
14. Cone/friction ring transmission according to claim 13, wherein
an input-side gear wheel of the gear-wheel transmission has an even
number of teeth, and an output-side gear wheel of the gear-wheel
transmission has an odd number of teeth, or wherein the input-side
gear wheel of the gear-wheel transmission has an odd number of
teeth, and the output-side gear wheel of the gear-wheel
transmission has an even number of teeth.
15. Cone/friction ring transmission consisting of at least a first
subsidiary transmission structured as a cone/friction ring
transmission and a second subsidiary transmission structured as a
cone/friction ring transmission, according to claim 1, wherein at
least two cones from different subsidiary transmissions have a
press-down device, in each instance, wherein the two press-down
devices have a device for equalizing the difference in the
press-down forces.
16. Cone/friction ring transmission consisting of a first
subsidiary transmission structured as a cone/friction ring
transmission and a second subsidiary transmission structured as a
cone/friction ring transmission, wherein the two subsidiary
transmissions have a common cone, and the first subsidiary
transmission has a first further cone and the second subsidiary
transmission has a second further cone, wherein the axes of
rotation of the common cone as well as of the two further cones are
disposed in an axis plane, and wherein at least the common cone has
a shaft-side friction cone bearing as well as a shoulder-side
friction cone bearing, according to claim 1, wherein the shaft-side
friction cone bearing and/or the shoulder-side friction cone
bearing have a degree of freedom of translation along the axis
plane.
17. Method for a cone/friction ring transmission having at least
two subsidiary transmissions structured as cone/friction ring
transmissions, which have a first adjustment device for a friction
ring of the first subsidiary transmission and a second adjustment
device for a friction ring of the second subsidiary transmission,
wherein an axial position of the friction rings is regulated by way
of a regulation device, wherein the regulation device has at least
a first subsidiary regulation device having a first reference
variable and a second subsidiary regulation device having a second
reference variable, separate from the first reference variable,
wherein the position of the friction ring of the first subsidiary
transmission is regulated by way of the first subsidiary regulation
device, and the position of the friction ring of the second
subsidiary transmission is regulated by way of the second
subsidiary regulation device.
18. Method for a cone/friction ring transmission having at least
two subsidiary transmissions structured as cone/friction ring
transmissions, which have a first adjustment device for a friction
ring of the first subsidiary transmission and a second adjustment
device for a friction ring of the second subsidiary transmission,
wherein an axial position of the friction rings is regulated by way
of a regulation device, wherein the regulation device has at least
a first subsidiary regulation device having a first reference
variable and a second subsidiary regulation device having a second
reference variable, dependent on the first reference variable,
wherein the second reference variable is generated by way of
correction of the first reference variable by way of a position
offset characteristic field, and the position offset characteristic
field is generated by means of a calibration measurement of
deviations in the axial position of the first and of the second
friction ring.
19. Method for a cone/friction ring transmission according to claim
18, wherein the calibration measurement takes place before initial
startup of the cone/friction ring transmission.
20. Method for a cone/friction ring transmission consisting of at
least one input cone and one output cone and a friction ring
disposed between the input cone and the output cone, enclosing at
least one cone, also according to claim 1, wherein a torque of the
input cone is converted to a lower torque, with reference to an
input shaft of the cone/friction ring transmission.
21. Method according to claim 20, wherein the torque of the input
cone is converted to approximately half the torque of the input
shaft.
Description
[0001] The invention relates to a cone/friction ring transmission,
consisting of at least two subsidiary transmissions structured as
cone/friction ring transmissions, and to a method for a
cone/friction ring transmission having at least two subsidiary
transmissions structured as cone/friction ring transmissions.
[0002] Such a transmission is known from U.S. Pat. No. 1,709,346,
whereby in these arrangements, a central cone is driven, which
interacts with one or more output cones, by way of a friction ring,
in each instance; these output cones are directed opposite the
input cones, axis-parallel to them, disposed at a distance from the
input cone that is constant over the cone mantle. The friction
rings can be displaced along the gap, in each instance, by way of a
common frame, so that a translation ratio between the input cone
and the output cone can be adjusted in infinitely variable manner.
The power take-offs of the power take-off cones, in each instance,
are connected with the planets of a planetary gear, so that a
torque applied by the input cone is divided up among the power
take-off cones, in each instance, and totaled up again by way of
the planetary gear, where a constant speed of rotation of the
planets as well as of the power take-off cones is forced to occur
as the result of coupling of the planets. However, this arrangement
contains the problem that even tiny production tolerances or
inaccuracies lead to friction losses between the friction rings and
the cones.
[0003] Another embodiment of a transmission that can be adjusted in
infinitely variable manner is known from JP 2000-291759, in which
the friction rings are not guided along a gap by way of a common
frame. Instead, each friction ring of each subsidiary transmission
has an adjustment device that is mechanically independent of the
others, which can be controlled a common regulation device.
[0004] An alternative, known from WO 2004/063598 A1, proposes
merging the power take-off cones, in each instance, of two parallel
subsidiary transmissions that can be adjusted in infinitely
variable manner, by means of a superimposition transmission on the
power take-off. The need for equalizing the slip between an input
cone and an output cone that occurs as the result of production
tolerances or inaccuracies is eliminated, by way of the power-split
joining of the power take-off shafts, because a total drive joined
in this form allows differences in the speed of rotation between
the subsidiary transmissions, in each instance. However, it is a
disadvantage of such an embodiment that the increased complexity of
the overall transmission and the increased number of friction
pairings in the subsequent superimposition transmissions increase
not only the production, assembly, and maintenance costs, but also
the failure likelihood and the loss in degree of effectiveness.
[0005] It is therefore the task of the present invention to make
available a transmission of the type stated, which can be adjusted
in infinitely variable manner, which can also transfer higher
torques, in operationally reliable manner, with little power loss,
and at low or cost-advantageous construction expenditure.
[0006] As a solution, the invention proposes a cone/friction ring
transmission having at least two subsidiary transmissions
structured as cone/friction ring transmissions, which have a first
adjustment device for a friction ring of the first subsidiary
transmission, and a second adjustment device for a friction ring of
the second subsidiary transmission, whereby the cone/friction ring
transmission has a regulation device for regulation of an axial
position of the friction rings, and is characterized in that the
regulation device has at least a first subsidiary regulation device
having a first reference variable, and a second subsidiary
regulation device having a second reference variable, which is
separate from the first reference variable, whereby the first
subsidiary transmission has the first subsidiary regulation device
for regulation of the position of the friction ring of the first
subsidiary transmission, and the second subsidiary transmission has
at least the second subsidiary regulation device for regulation of
the position of the friction ring of the second subsidiary
transmission.
[0007] The use of regulation by means of a second subsidiary
regulation device and a second reference variable separate from the
first reference variable has the advantage that regulation of the
position of the friction ring of the second subsidiary
transmission, independent of production tolerances or inaccuracies,
can take place. A regulation device that makes the desired
translation ratio of the transmission available by means of a
control variable that is identical for both subsidiary
transmissions, according to the state of the art, cannot be able to
take the wear behavior in the two subsidiary transmissions into
consideration in targeted manner, because the compulsory sameness
of the speed of rotation of the two subsidiary transmissions can
lead to increased slip in at least one of the subsidiary
transmissions, or necessarily leads to an increased or undefined
slip because of the unavoidable production tolerances. Only by
means of regulation of the friction ring of the second subsidiary
transmission that is independent of the first subsidiary regulation
device can differences in speed of rotation between the friction
rings of the two subsidiary transmissions be equalized, so that the
transfer of force in the two subsidiary transmissions takes place
with little slip, if at all possible, or with precisely defined
slip between the friction rings, in each instance, and the cones
that are connected to interact by means of these friction
rings.
[0008] It is also possible that a regulation device is implemented
within an engine or transmission control device that is present, in
any case, which device takes on all or most of the relevant control
and regulation procedures in modern motor vehicles. In this regard,
it is understood that--particularly in distinction from JP
2000-291759--such an engine or transmission control device that is
present, in any case, can be implemented with a regulating effect
by means of inclusion in the regulation circuit described
above.
[0009] According to a preferred embodiment of the present
invention, the translation of the first subsidiary transmission can
be regulated by means of a first subsidiary regulation device,
which corresponds to a regulation device according to the state of
the art, whereby, for example, the reference variable is a
translation ratio predetermined by a characteristic field or a
translation ratio otherwise predetermined by a control device.
[0010] In order to implement the advantage of
speed-of-rotation-synchronous friction rings in particularly simple
and operationally reliable manner, it is proposed that a regulation
variable of the first subsidiary regulation device is a reference
variable of the second subsidiary regulation device.
[0011] A regulation variable of the first subsidiary transmission
used according to this aspect of the invention can be, for example,
the speed of rotation of the friction ring of the first subsidiary
transmission or the speed-of-rotation slip at the friction ring of
the first subsidiary transmission, or a torque transferred by way
of the first subsidiary transmission. The regulation variable of
the first subsidiary transmission that is used is consequently
linked with the second subsidiary regulation device in such a
manner that the regulation variable of the first subsidiary
transmission is a reference variable of the second subsidiary
regulation device, and that a regulation variable of the second
subsidiary regulation device, of the same type, in terms of value,
as the regulation variable of the first subsidiary regulation
device, is regulated to a corresponding value.
[0012] Alternatively or cumulatively to this, the reference
variable of the first subsidiary regulation device can also be a
reference variable of the second subsidiary regulation device.
[0013] A reference variable preset by a control device, for example
a transmission translation or a position of a friction ring of the
first subsidiary transmission, but also an angular position of the
first friction ring, can therefore also be used for regulation of
the position of the friction ring of the second subsidiary
transmission.
[0014] This has the advantage that regulation of a friction ring of
the second subsidiary transmission, at high required adjustment
speeds, can follow the regulation of a friction ring of the first
subsidiary transmission at sufficiently great accuracy or speed,
because adjustment of the regulation variable of the second
subsidiary transmission by way of the reference variable of the
first subsidiary transmission can be used as preliminary
regulation, and the second subsidiary regulation device merely has
to readjust the position of the friction ring of the second
subsidiary transmission, if necessary, by a small amount relative
to the predetermined position, if the second reference variable of
the second subsidiary transmission requires corresponding
deviations.
[0015] This method of regulation of the position of a friction ring
of the second subsidiary transmission, with simultaneous use of the
reference variable of the first subsidiary transmission and a
second reference variable separate from this reference variable,
makes it possible to adjust the position of a friction ring of the
second subsidiary transmission synchronous to the position of a
friction ring of the first subsidiary transmission, and, if
necessary, to balance out any production tolerances or inaccuracies
by means of correcting the position of a friction ring of the
second subsidiary transmission by way of the second subsidiary
regulation device.
[0016] Alternatively or cumulatively, transmission control is also
possible, by means of which the first subsidiary transmission and
the second subsidiary transmission are regulated by way of the
reference variable of the first subsidiary transmission, and in
which correction of a slip value that is different in value at the
friction rings takes place by way of correction of the position of
the friction ring of the second subsidiary transmission, in that a
position offset characteristic field is used as the reference
variable for the second subsidiary regulation device.
[0017] In this connection, a data set that is determined during
running-in, for example after assembly of a corresponding
cone/friction ring transmission and before initial startup of the
said cone/friction ring transmission, by means of measurement of
same, for example on a test bench, can be used as the position
offset characteristic field. A characteristic field determined
according to this method can be a two-dimensional diagram, for
example, in which a correction variable is stored for every axial
position of the friction ring of the second subsidiary transmission
that is approached, which variable is necessary the amount of the
required axial displacement of the friction ring of the second
subsidiary transmission to the position set by the reference
variable of the first subsidiary regulation device. Alternatively
or cumulatively, such a position offset characteristic field can
also be recorded or changed during operation, by means of the
existing transmission control device itself, if a device for
detecting the slip that is applied to the friction rings is present
and the values determined by it are evaluated in suitable manner.
It is understood that such a position offset characteristic field
can also be made available in various other ways,
[0018] In order to implement the aforementioned advantages, it is
therefore proposed, within the scope of a preferred alternative,
that the reference variable of the second subsidiary regulation
device is a reference variable of the first subsidiary regulation
device corrected by way of a position offset characteristic
field.
[0019] In this manner, the regulation process can be significantly
simplified and accelerated during normal operation, or can be
carried out with less computing effort.
[0020] Regulation of friction rings of two subsidiary
transmissions, independent of one another or partly independent of
one another, furthermore requires that the different friction rings
do not exert any kinematic influence on one another. If the
different subsidiary transmissions have a common cone and a further
cone, in each instance, and the friction rings connect the common
cone and the further cone of a subsidiary transmission so as to
interact with one another, in each instance, it is advantageous,
particularly if all the friction rings are the same parts and are
therefore identical in design, that each friction ring of a
subsidiary transmission encloses the further cone of this
subsidiary transmission.
[0021] For an embodiment with two subsidiary transmissions, it is
therefore preferably proposed that the first subsidiary
transmission and the second subsidiary transmission have a common
cone and a further cone, in each instance, that the friction ring
of the first subsidiary transmission merely encloses the further
cone of the first subsidiary transmission, and that the friction
ring of the second subsidiary transmission merely encloses the
further cone of the second subsidiary transmission.
[0022] In order to advantageously benefit from further symmetry
properties and to divide the power transferred by way of the two
subsidiary transmissions in equal parts, and then bring these
together again, it is proposed to structure the power, force, or
torque division and merging at the different subsidiary
transmissions or at the further cones of the different subsidiary
transmissions in such a manner that the cones are guided on a
common shaft, by way of a gear drive, whereby the individual gear
wheel pairings of the subsidiary transmissions, in each instance,
have an identical translation ratio. It is therefore proposed that
the further cone of the first subsidiary transmission is connected
to interact with a shaft, by means of a first transmission,
particularly a gear wheel transmission, and the further cone of the
second subsidiary transmission is also connected to interact with
this shaft, by means of a second transmission, particularly a gear
wheel transmission, whereby the first and the second transmission
have an identical translation ratio.
[0023] It is understood that such an arrangement is also possible
for a cone/friction ring transmission having more than two
subsidiary transmissions, whereby each further subsidiary
transmission has a regulation device provided for this subsidiary
transmission and independent of the first regulation device.
[0024] According to another aspect of the invention, it is desired,
within the scope of the aforementioned task, that to apply the
press-down force required at the cones by means of the use of a
device that is as cost-advantageous as possible. For example, a
device for applying a press-down force can be provided on the
common cone, instead of providing two different devices for
applying the press-down force on two or more further cones. This
has the advantage that a cost-advantageous transmission with
relatively simple regulation of the press-down force, by means of a
single unit, can be implemented.
[0025] In order to implement this advantage, it is therefore
particularly proposed to make available a cone/friction ring
transmission consisting of at least two subsidiary transmissions
structured as cone/friction ring transmissions, in which the
subsidiary transmissions have an input cone and a common output
cone, in each instance, and which is characterized in that the
common output cone has a press-down device. Such an arrangement
makes it possible to coordinate the press-down device with the
different operating states, in particularly precise manner and with
a simple construction.
[0026] According to another aspect of the invention, it is also
possible, as an alternative to a single press-down device for a
common cone, to use multiple press-down devices for the further
cones. In order to achieve an advantage as compared with an
individual press-down device, the possibility exists, in the case
of such an arrangement, to keep press-down forces on cones of
different subsidiary transmissions the same, in terms of amount.
Equalization of different press-down forces can take place, in this
connection, by means of suitably coupled press-down devices, for
example.
[0027] In order to implement this advantage, a cone/friction ring
transmission consisting of at least a first subsidiary transmission
structured as a cone/friction ring transmission and a second
subsidiary transmission structured as a cone/friction ring
transmission is proposed, which is characterized in that at least
two cones from different subsidiary transmissions have a press-down
device, in each instance, whereby the two press-down devices have a
device for equalizing the difference in the press-down forces.
[0028] Force equalization performed according to this aspect of the
invention can advantageously be implemented, in this connection, by
means of a scale, whereby this scale can be a hydraulic scale or a
mechanical scale.
[0029] A scale that acts hydraulically, between two press-down
devices, can be structured, for example, in such a manner that two
oil-filled pressure chambers of the press-down device, filled with
oil, are connected with one another by means of a line system, in
such a manner that hydraulic pressure equalization between the
press-down devices takes place.
[0030] Accordingly, it is proposed that the force equalization
takes place hydraulically.
[0031] An alternative scale, which works mechanically, can be
structured, for example, by means of a skillful arrangement of
levers, whereby preferably, two levers having the same length and
connected to interact opposite to one another, to balance out
forces between the two press-down devices according to the balance
scale principle, are provided. Also, such equalization can take
place, for example, by means of pulleys and cables or similar
arrangements. In this regard, force equalization can also take
place mechanically.
[0032] Furthermore, the use of force equalization offers
alternative possibilities for applying a press-down force by way of
the press-down device. The use of two uncoupled press-down devices,
in contrast to this, also requires separate application of the
press-down forces. Coupling of two press-down devices as described
above therefore allows applying the required press-down forces by
means of a single device common to both press-down devices.
[0033] Therefore the only requirement, when using hydraulic force
equalization, is to use a single device, such as a pump, for
applying the press-down force.
[0034] For mechanical force equalization that works according to
the balance scale principle, a skillful arrangement of devices for
applying a press-down force, such as a spring package, is also a
possibility, whereby such a spring package or other type of device
for applying a press-down force only has to be provided either in a
press-down device, or can be provided at the pivot point of the
lever mechanism of the mechanical force equalization device.
[0035] A previously proposed possibility of using a second
subsidiary regulation device for a second subsidiary transmission
consists in using a speed of rotation of a friction ring as a
regulation variable of a regulation segment. It is therefore
proposed to make available a cone/friction ring transmission
consisting of at least one input cone and one output cone, and a
friction ring disposed between the input cone and the output cone,
enclosing at least one cone, which is characterized by a device for
measuring the speed of rotation of the friction ring.
[0036] In this connection, measuring the speed of rotation of the
friction ring means a direct measurement of the physical speed of
rotation of the friction ring that is actually present. It is
therefore proposed that the device for measuring the speed of
rotation of the friction ring preferably detects the speed of
rotation of the friction ring directly at the friction ring,
preferably by means of a sensor system that acts on the friction
ring. In this connection, "direct measurement of the speed of
rotation" is understood to mean measurement of the speed of
rotation that does not take place by means of modules that are
acted on by a main torque that passes through the corresponding
subsidiary transmission and corresponds to the torque that acts on
the input cone of the subsidiary transmission, in each instance.
For example, the measurement can be undertaken by means of a sensor
system that engages directly on the friction ring, for example by
means of an inductive measurement or by means of an optical
measurement, if the friction ring has corresponding devices, such
as, for example, corresponding teeth or recesses. On the other
hand, a corresponding measurement can be carried out by way of a
friction ring guide and the guide wheels that engage directly on
the friction ring, for example.
[0037] Alternatively, an indirect determination of the speed of
rotation of the friction ring is also possible, in which the speed
of rotation of the cones that are connected to interact, by means
of the friction ring, is detected, and the physical speed of
rotation of the friction ring is detected by way of physical and/or
mathematical models. In this connection, however, it is very
difficult to include slip, which might occur differently in the
output cone and the input cone, in these models.
[0038] Because the friction ring is freely movable in its axial
position, it is then otherwise generally necessary to also dispose
a measurement device in axially displaceable manner for a direct
measurement of the speed of rotation of the friction ring, so that
the measurement device assumes a non-changeable position relative
to the friction ring. Therefore a guide device that is axially
displaceable with the friction ring is proposed, on which the
measurement device is disposed.
[0039] Alternative to regulation of the axial position of the
friction rings by means of the speed of rotation of the friction
rings, regulation by means of the slip of the friction rings can
also take place, for example. For determining slip on a friction
ring or on a friction cone, however, it is advantageous to know not
just the speed of rotation of a friction ring, but also at least
one further speed of rotation of one of the cones connected, so as
to interact, by means of the friction ring. In order to implement
this, the cone/friction ring transmission can have not only the
device for measuring the speed of rotation of the friction ring,
but also a device for measuring the speed of rotation of at least
one cone.
[0040] In this connection, it is understood that a cone/friction
ring transmission having a device for measuring the speed of
rotation of the friction ring, particularly if this detects the
speed of rotation directly on the friction ring, as well as a
cone/friction ring transmission having a device for measuring the
speed of rotation of at least one of the cones are correspondingly
advantageous, even independent of the other characteristics of the
present invention.
[0041] Likewise, torque can also be used as the regulation variable
for a cone/friction ring transmission, particularly as the
regulation variable for a second subsidiary regulation device of a
second subsidiary transmission, in other words for an overall
transmission that comprises two cone/friction ring transmissions.
Accordingly, independent of the other characteristics of the
present invention, a cone/friction ring transmission consisting of
at least one input cone and one output cone and a friction ring
disposed between the input cone and the output cone, enclosing at
least one cone, which is characterized by a torque measurement
device, is advantageous.
[0042] If the torque measurement device comprises contact-free data
transmission, then influences of the torque measurement device on
the cone/friction ring transmission itself can be minimized;
likewise, wear can be restricted to a minimum. In particular,
optical and/or inductive data transmission is possible for
contact-free data transmission. Likewise, the modules of the torque
measurement device that rotate and require energy can be supplied
with energy in contact-free manner, for example optically or
inductively.
[0043] In the present connection, the term data transmission
comprises all data or measurement values, whether analog or
digital, which provide information about the torque or stand in
proportionality to the applied torque. Thus, these can be
measurement values that are already digitalized, which are supposed
to be transferred from the rotating modules of the torque
measurement device to fixed modules. Likewise, these can be
measurement signals that still require further processing.
[0044] Preferably, the torque measurement device comprises a cone
shaft, in other words a shaft that is connected with one of the
cones as a drive shaft or power take-off shaft. In particular, the
torque measurement device can have a module that is connected in
one piece with the cone. Likewise, the measuring modules can be
connected with the cone in rigid and at most bending-elastic
manner, so that the torque measurement device, although it can be
installed and removed, can measure the torque applied to the
cone/friction ring transmission or to the corresponding cone
directly, if at all possible.
[0045] Preferably, a corresponding torque measurement device is
provided both on the input cone and on the output cone, whereby a
statement concerning the slip of the friction ring can also be made
by means of the difference in the torques.
[0046] In order to accomplish the task stated initially,
alternatively or cumulatively to the above characteristics, a
cone/friction ring transmission consisting of at least one input
cone as well as one output cone and a friction ring disposed
between the input cone and the output cone, enclosing at least one
cone, is proposed, which is characterized in that a torque
converter is disposed between an input shaft of the cone/friction
ring transmission and the input cone. In particular, this torque
converter can be used for a cone/friction ring transmission, in
such a manner that the input cone has a lower torque than the input
shaft. In this way, a cone/friction ring transmission is
advantageously made available, which can transfer significantly
greater drive power by means of the torque conversion on the input
side. This is due to the properties of a cone/friction ring
transmission, which transfer torques only by way of force fit, in
other words friction, and therefore has a maximal torque that can
be transferred. The conversion of this torque into a lower torque,
while simultaneously increasing the speed of rotation at the input
cone, leads, as is immediately evident, to the increase in the
maximal force that can be transferred, as described above, if now
twice the original torque, for example, is introduced into a
transmission with unchanged dimensioning.
[0047] In a particularly advantageous embodiment, the input cone
can have approximately half the torque of the input shaft.
Consequently, a torque and speed of rotation translation at a
translation ratio of about i=0.5 is implemented. It has been shown
that in terms of design, this translation ratio is particularly
well suited for making available a cone/friction ring transmission
for higher torques, without having to accept disadvantages, for
example caused by greater friction.
[0048] In a further particularly advantageous embodiment, and in
order to keep additional friction at the cone/friction ring
transmission to a minimum, the torque converter can comprise a
gear-wheel transmission. Furthermore, a gear-wheel transmission can
be produced in particularly cost-advantageous manner, and therefore
the advantages that result are not or insignificantly cancelled out
by higher costs.
[0049] For a cone/friction ring transmission with a gear-wheel
transmission, it is furthermore advantageous if an input-side gear
wheel of the gear-wheel transmission has an even number of teeth,
and an output-side gear wheel of the gear-wheel transmission has an
odd number of teeth. This embodiment can also be advantageous for a
cone/friction ring transmission vice versa, in that the input-side
gear wheel of the gear-wheel transmission has an odd number of
teeth, and the output-side gear wheel of the gear-wheel
transmission has an even number of teeth. This pairing of two gear
wheels, having an even and an odd number of teeth, in each
instance, leads to the result that after one circulation of the
gear wheel, in each instance, a tooth at first comes into
engagement with a different tooth of the opposite gear wheel. In
this way, it is prevented that a tooth of one gear wheel
exclusively comes into engagement with one and the same tooth of
the opposite gear wheel, and therefore non-uniform wear of the gear
wheels might be brought about.
[0050] In this connection, it is immediately evident that the term
"approximately" in connection with half the torque of the input
shaft is aimed at the meaning that a gear wheel of the input shaft
has twice the number of teeth of the gear wheel of the input cone,
plus or minus one tooth.
[0051] Furthermore, a method for a cone/friction ring transmission
or for operation of a cone/friction ring transmission consisting of
at least one input cone as well as one output cone and a friction
ring disposed between the input cone as well as the output cone,
enclosing at least one cone, is proposed, which is characterized in
that a torque of the input cone is converted to a lower torque,
with reference to an input shaft of the cone/friction ring
transmission. Therefore, as has already been explained above, the
incoming torque is reduced, by means of the torque converter used
ahead of the cone/friction ring transmission or ahead of the input
cone of the cone/friction ring transmission, while simultaneously
increasing the speed of rotation, to such an extent that
significantly greater power can be transferred by the cone/friction
ring transmission.
[0052] In addition to the method explained above, the torque of the
input cone can be converted to approximately half the torque of the
input shaft, making use of the advantages already explained
above.
[0053] It is understood that the characteristics concerning torque
conversion between the input shaft and the input cone are
advantageous for a cone/friction ring transmission even independent
of the other characteristics of the invention.
[0054] Also, as a further solution of the task stated above, a
method is proposed for a cone/friction ring transmission having at
least two subsidiary transmissions structured as cone/friction ring
transmissions, which have a first adjustment device for a friction
ring of the first subsidiary transmission and a second adjustment
device for a friction ring of the second subsidiary transmission,
whereby an axial position of the friction rings is regulated by way
of a regulation device, and the cone/friction ring transmission is
characterized in that the regulation device has at least a first
subsidiary regulation device having a first reference variable and
a second subsidiary regulation device having a second reference
variable, separate from the first reference variable, whereby the
position of the friction ring of the first subsidiary transmission
is regulated by way of the first subsidiary regulation device, and
the position of the friction ring of the second subsidiary
transmission is regulated by way of the second subsidiary
regulation device.
[0055] A cone/friction ring transmission regulated according to
this method can be regulated, in its overall translation, in
accordance with the state of the art, by way of a transmission
control device that contains the first subsidiary regulation
device, whereby the first subsidiary regulation device receives its
reference variable by way of the transmission control device itself
or by way of an engine control device that is present. The control
variable output by the first subsidiary regulation device is used
for regulation of the axial position of a friction ring at least of
the first subsidiary transmission, but also for regulation of a
friction ring of every further subsidiary transmission that is
present, particularly for regulation of the friction ring of the
second subsidiary transmission.
[0056] A regulation variable detected at the first subsidiary
transmission can be passed back to the second subsidiary regulation
device, and as a result, the second subsidiary regulation device in
turn outputs a second control variable for an adjustment device of
a friction ring of the second subsidiary transmission. Any desired
speed of rotation, for example the speed of rotation of the
friction ring, the speed of rotation of a friction cone situated in
the subsidiary transmission, a slip that occurs on the friction
ring, or also a torque transferred by the subsidiary transmission,
can be used as a regulation variable of the first regulation
segment, in other words of the first subsidiary transmission. The
control variable output by the second subsidiary regulation device
can then be used, together with the control variable output by the
first subsidiary regulation device, to regulate the axial position
of the friction ring of the second subsidiary transmission.
[0057] In this connection, superimposition preferably takes place
in such a manner that the axial position of the friction ring of
the second subsidiary regulation device is set by the first control
variable, so that it corresponds or is equivalent to the axial
position of the friction ring of the first subsidiary transmission,
and that the second control variable, which is superimposed on the
first control variable, only slightly readjusts the friction ring
of the second subsidiary transmission, in terms of its position, in
such a manner that because of this slight relative change in
position of the friction ring of the second subsidiary
transmission, the regulation variables of the first subsidiary
transmission and of the second subsidiary transmission reach the
same value, in other words the regulation deviation of the second
regulation variable from the first regulation variable, which is
used as the second reference variable, approaches zero. Of course,
the position of the friction ring of the second subsidiary
transmission can be regulated not just slightly by means of the
control variable of the second subsidiary regulation device, but
rather also in such a manner that it is possible to do without the
first subsidiary regulation device for positioning of the friction
ring of the second subsidiary transmission, and regulation of its
position then takes place only by way of the second subsidiary
regulation device.
[0058] In order to improve a cone/friction ring transmission
according to another aspect of the present invention, a method is
proposed for a cone/friction ring transmission having at least two
subsidiary transmissions structured as cone/friction ring
transmissions, which has a first adjustment device for a friction
ring of the first subsidiary transmission and a second adjustment
device for a friction ring of the second subsidiary transmission,
wherein an axial position of the friction rings is regulated by way
of a regulation device, which cone/friction ring transmission is
characterized in that the regulation device has at least a first
subsidiary regulation device having a first reference variable and
a second subsidiary regulation device having a second reference
variable, dependent on the first reference variable, whereby the
second reference variable is generated by way of correction of the
first reference variable by way of a position offset characteristic
field, and the position offset characteristic field is generated by
means of a calibration measurement of deviations in the axial
position of the first and of the second friction ring.
[0059] A cone/friction ring transmission operated according to this
method presumes that the position offset characteristic field that
is used is either already present or is recorded during operation
of the cone/friction ring transmission.
[0060] To generate a position offset characteristic field that has
already been stored in the control device of the transmission, for
operation of the regulation device, a testing and running-in
program for determining the position offset characteristic field
can advantageously be used, carried out on a test bench after
assembly. In this connection, the production tolerances and
inaccuracies are recorded, for example by means of measurement
instruments present on the test bench, and permanently stored in
the control device of the cone/friction ring transmission, thereby
making it possible to do without additional sensors for determining
the regulation variables required for regulation. The position
offset characteristic field consists, in this test bench
calibration, for example of a position of the friction ring of the
first subsidiary transmission predetermined by the first regulation
device, and a position deviation of the friction ring of the second
subsidiary transmission that correlates to it. A corresponding
correction variable for the first control variable is determined
from this position deviation, and the corrected signal is output by
the second subsidiary regulation device as a second control
variable.
[0061] It is understood that generation of a data set for a
position offset characteristic field is not limited to a test bench
run before initial startup of the cone/friction ring transmission,
because a calibration process is possible also during operation, by
means of a transmission control device present in the vehicle and a
suitable sensor system on the cone/friction ring transmission. A
learning function can be implanted in a control device, according
to this method, for example, by means of which function the
position offset characteristic field is constantly adapted to the
current wear state of the cone/friction ring transmission.
[0062] Alternatively or cumulatively to the above embodiments of
the invention, a cone/friction ring transmission consisting of a
first subsidiary transmission structured as a cone/friction ring
transmission and a second subsidiary transmission structured as a
cone/friction ring transmission is proposed, in order to accomplish
the task stated initially, in which the two subsidiary
transmissions have a common cone and the first subsidiary
transmission has a first further cone and the second subsidiary
transmission has a second further cone, whereby the axes of
rotation of the common cone as well as of the two further cones are
disposed in an axis plane, whereby at least the common cone has a
shaft-side friction cone bearing as well as a shoulder-side
friction cone bearing, and whereby the cone/friction ring
transmission is characterized in that the shaft-side friction cone
bearing and/or the shoulder-side friction cone bearing has a degree
of freedom of translation along the axis plane. If a press-down
device is provided only for the common cone in a cone/friction ring
transmission, the torque transferred by the two subsidiary
transmissions can be distributed to the two subsidiary
transmissions in particularly uniform manner, by means of the
configuration described above, in particularly advantageous manner.
In particular, the friction forces and press-down forces that occur
at the friction contacts of the two subsidiary transmissions are
uniformly distributed to two subsidiary transmissions by means of
this configuration. It is also possible, at this point, that the
configuration of any desired friction cone bearing or both friction
cone bearings with a degree of freedom of translation along the
axis plane is advantageous also in the case of a cone/friction ring
transmission having two press-down units, whereby the press-down
units are provided in the two further cones. In particular, the
arrangement explained above is advantageous if only one press-down
unit is provided in the further cones.
[0063] In this connection, it is understood that roller bearings,
in particular, but also slide bearings, if necessary, can be used
as friction cone bearings. In particular, four-point bearings,
other ball bearings, are suitable as roller bearings, or, in the
case of certain bearings, also conical roller bearings; likewise,
needle bearings can be used.
[0064] For transferring the torque transferred by the cone/friction
ring transmission, an individual cone has an input shaft connected
with this cone, or an output shaft. The term "shaft-side" therefore
characterizes that end of the axial expanse of a cone that faces
such an input or output shaft. Accordingly, the term
"shoulder-side" refers to the side of the cone that faces away from
the corresponding shaft. If a second output shaft or a second input
shaft is provided on a cone, for a possible secondary drive, the
reference point for the terms "shaft-side" and "shoulder-side" is
always the shaft that transfers the main drive torque. In this
connection, the term "axial" always refers to the axis of rotation
or symmetry of a cone.
[0065] The term "degree of freedom of translation" refers to the
movement directions of a point or of a body in the coordinate
system, independent of one another, in each instance. The present
invention here is based on the Cartesian coordinate system and thus
on six degrees of freedom, three degrees of freedom of translation
and three degrees of freedom of rotation. A degree of freedom of
translation that runs along the axis plane and essentially radial
to the axis of rotation of the common cone therefore describes a
movement direction of two axes of rotation, which are moving toward
one another or away from one another, or of two points on two axes
of rotation, which are moving toward one another or away from one
another. In this connection, the term "essentially" expresses that
the movement of a friction cone bearing along the axis plane and
radial to the axes of rotation does not have to involve only a
translational movement of a corresponding bearing in the direction
of a further axis of rotation, whereby the axis of rotation of the
moving cone moves parallel to the remaining axis of rotation, but
rather can also involve movement of the cone axis or bearing axis
of rotation about a rotational point on the axis of rotation.
Therefore it is true that a point on the moving axis of rotation
would always move perpendicular to this axis of rotation, but this
movement would not be perpendicular or radial to the axis of
rotation toward which the bearing in question is moving.
[0066] In order to guarantee drive or power take-off of the common
cone that is free of bending force, if this cone is being displaced
in the axis plane, a shaft of the common cone can have at least one
movable, torsionally rigid coupling. A "movable, torsionally rigid
coupling" can be structured, for example, as a universal joint, as
a constant velocity ball joint, as a curved-tooth coupling, or as a
multiple disk clutch. Essentially, the coupling must balance out an
angle and/or an offset of the common cone. Accordingly, it can also
be necessary to dispose two movable, torsionally rigid couplings,
such as two cardan joints, one behind the other, thereby giving the
shaft connected with these couplings a total of four degrees of
freedom, two degrees of freedom of rotation and two degrees of
freedom of translation. In connection with the degree of freedom of
translation of a shaft-side or a shoulder-side friction cone
bearing mentioned above, there is therefore a total of one degree
of freedom of translation and one degree of freedom of rotation for
the entire arrangement or the common cone. This said degree of
freedom of translation of the common cone results if both bearings,
the shaft-side friction cone bearing and the shoulder-side friction
cone bearing, jointly perform a movement along the axis plane. A
rotational movement of the common cone results if only one of the
two bearings performs a translational movement in the axis plane.
In this connection, the term "essentially" becomes clear once
again, because a friction cone bearing will move on a circular path
if the common cone is immovably clamped on a further friction cone
bearing. For the translational movement being considered, however,
the angle range represented in such a case is so small that
movement on a straight line can be approximated.
[0067] Although the angle range being considered during rotational
movement of the entire common cone is being considered, it is
advantageous for a cone/friction ring transmission if the
shaft-side friction cone bearing and the shoulder-side friction
cone bearing are structured as floating bearings. In this way,
tensions on the basis of movement, but also tensions caused by
thermal expansion processes in the common cone or in the shaft can
be balanced out. In this regard, it is also advantageous,
alternatively to a floating bearing structured on the shaft side
and shoulder side, if one of the shaft-side or shoulder-side
friction cone bearings is structured as a floating bearing, and the
further shaft-side or shoulder-side friction cone bearing is
structured as a fixed bearing. In this connection, it is
particularly advantageous if the fixed bearing is an angle-movable
bearing. An "angle-movable bearing" can particularly be a spherical
roller bearing or a self-aligning bearing, which is able to balance
out an angle offset of the shaft.
[0068] It is furthermore advantageous for a cone/friction ring
transmission if the shaft-side and/or the shoulder-side friction
cone bearing have a bearing guide. This can be advantageously
implemented, in particular, if the bearing is merely used for
mounting a rotating axle, and is firmly clamped in the stated
bearing guide, and the bearing guide is therefore responsible for
translational movement in the axis plane. In this regard, the
various bearing tasks are also distributed among different
modules.
[0069] It can furthermore be advantageous for a cone/friction ring
transmission, particularly in connection with a common cone that
can move in the axis plane, if at least one friction ring of the
cone/friction ring transmission has a contact surface that faces
the common cone, whereby the contact surface is configured to be
convex relative to a surface of the common cone, at least at a
sectional plane that lies in the axis plane. This crowned
configuration of a friction ring surface furthermore promotes the
slanted position or an angle offset of the axis of rotation of the
common cone, in that the same contact geometry between friction
ring and common cone is always guaranteed. If the friction ring
were to have a level contact surface relative to the common cone,
thereby causing a contact line to form at this friction contact
instead of a contact point, and furthermore also at the other
friction contacts, the surface of the common cone would no longer
run parallel to the friction ring surface in the event of an angle
offset of the common cone, thereby causing overly strong edge
pressures on this friction ring. A surface of the friction ring
configured in crowned manner counters this edge pressure and always
allows a uniformly structured contact point between the friction
ring and the common cone.
[0070] It is understood that the characteristics of the above
solutions and those described in the claims can also be combined,
if necessary, in order to be able to implement the advantages in
correspondingly cumulative manner.
[0071] Further advantages, goals, and properties of the present
invention will be explained using the following description of the
attached drawing. The drawing shows:
[0072] FIG. 1 a cone/friction ring transmission having a first
subsidiary transmission and a second subsidiary transmission, as
well as a first gear-wheel transmission and a second gear-wheel
transmission, which connects the further cones of the first
subsidiary transmission and of the second subsidiary transmission
so as to interact with a common shaft, with synchronous speeds of
rotation;
[0073] FIG. 2 a cone/friction ring transmission having a first
subsidiary transmission, having a second subsidiary transmission,
and having a first power-split equalization transmission, which
connects the further cones of the first subsidiary transmission and
of the second subsidiary transmission so as to interact with a
common shaft;
[0074] FIG. 3 a further cone/friction ring transmission having a
first subsidiary transmission, having a second subsidiary
transmission, and having a second power-split equalization
transmission, which connects the further cones of the first
subsidiary transmission and of the second subsidiary transmission
so as to interact with a common shaft;
[0075] FIG. 4 a further cone/friction ring transmission having a
first subsidiary transmission, having a second subsidiary
transmission, and having a third power-split equalization
transmission, which connects the further cones of the first
subsidiary transmission and of the second subsidiary transmission
so as to interact with a common shaft;
[0076] FIG. 5 a cone/friction ring transmission having a first
subsidiary transmission, having a second subsidiary transmission,
having a first press-down unit for a further cone of the first
subsidiary transmission, having a second press-down unit for a
further cone of the second subsidiary transmission, and having
hydraulic force equalization between the first press-down unit as
well as the second press-down unit;
[0077] FIG. 6 a cone/friction ring transmission having a first
subsidiary transmission, having a second subsidiary transmission,
having a first press-down unit for a further cone of the first
subsidiary transmission, having a second press-down unit for a
further cone of the second subsidiary transmission, and having
mechanical force equalization between the first press-down unit as
well as the second press-down unit;
[0078] FIG. 7 a cone/friction ring transmission having a first
subsidiary transmission, having a second subsidiary transmission,
and having a common press-down unit situated on a common cone;
[0079] FIG. 8 a cone/friction ring transmission having a first
subsidiary transmission, having a second subsidiary transmission,
and having a common cone that is freely movable in an axis plane,
which cone has two movable and torsionally rigid couplings on its
shaft;
[0080] FIG. 9 the arrangement of the bearings and shafts shown
in
[0081] FIG. 8, in a top view;
[0082] FIG. 10 a cone/friction ring transmission having a first
subsidiary transmission, having a second subsidiary transmission,
having mechanical coupling between the two transmissions, in a
first perspective view, at a low translation ratio;
[0083] FIG. 11 the cone/friction ring transmission according to
FIG. 10 in another perspective view;
[0084] FIG. 12 the cone/friction ring transmission according to
FIGS. 10 and 11 in a perspective view similar to FIG. 10, at a high
translation ratio;
[0085] FIG. 13 the cone/friction ring transmission according to
FIGS. 10 to 12 in a perspective view similar to FIG. 11, at a high
translation ratio;
[0086] FIG. 14 the cone/friction ring transmission according to
FIGS. 10 to 13 in a top view, at a high translation ratio; and
[0087] FIG. 15 a schematic top view of another cone/friction ring
transmission.
[0088] FIG. 1 shows the cone/friction ring transmission 1 having a
first subsidiary transmission 11 and a second subsidiary
transmission 21, as well as a first gear-wheel transmission 13 and
a second gear-wheel transmission 23, which connects the further
cone of the first subsidiary transmission 12 and the further cone
of the second subsidiary transmission 22 with a common shaft, with
synchronous speeds of rotation.
[0089] The introduction of force into the cone/friction ring
transmission 1 takes place, in this embodiment, by way of an input
shaft of a common cone 2 of the two subsidiary transmissions 11,
12. The further cones 12, 22 pass the shaft power passed on by the
common cone 2 to friction rings 14, 24 on to an output shaft, the
common shaft 3. In this connection, the friction rings 14, 24 are
axially adjusted by way of adjustment devices 15, 25 having
servomotors 16, 26, which are controlled by way of a reference
variable 18.
[0090] In this embodiment, the output shafts of the further cones
12, 22 are connected with a common spur gear that sits on the
common shaft 3, in order to pass the shaft power on by way of two
spur gears, in each instance. The power transfer from the common
cone 2 to the common shaft 3 is structured in such a manner,
because of these two spur gears, that the further cones 12, 22 of
the two subsidiary transmissions 11, 21 are always driven at a
synchronous speed of rotation, and a difference in the speed of
rotation between the further cones 12, 22, caused by a deviation
between the axial position of the friction ring 14 of the first
subsidiary transmission and the axial position of the friction ring
24 of the second subsidiary transmission cannot be balanced
out.
[0091] A position deviation between the friction rings 14, 24
therefore also necessarily leads to a difference in the speed of
rotation between the friction ring of the first subsidiary
transmission 14 and the friction ring of the second subsidiary
transmission 24, although this difference in the speed of rotation
can also achieve a very small value or, in an idealized,
theoretical cone/friction ring transmission, is not present at all.
A friction ring operated at a different speed of rotation is
subject, as a result, to greater slip at a friction pairing present
at this friction ring, such as the friction surface between the
surface that lies radially outside of the friction ring and the
surface of the common cone 2, or the surface that lies radially
within the friction ring and a surface of the further cone
connected with the common cone, so as to interact with it, by means
of the friction ring.
[0092] The second servomotor 26 of the second subsidiary
transmission 21, according to this embodiment, uses not only the
first reference variable 18, which is used to generate a common
control variable 19 for regulation of the two adjustment devices
15, 25, but also a second reference variable 28, which in turn is
formed from the regulation variable of the first subsidiary
transmission 11, here the difference in the speeds of rotation of
the friction ring of the first subsidiary transmission 14 and of
the friction ring of the second subsidiary transmission 24, whereby
here, for example, the absolute position of the first friction ring
14 or the like can also be used, for example.
[0093] The adjustment devices of the friction rings 15, 25
furthermore include two small guide wheels 5, in each instance,
which engage around the friction rings 14, 24 without play, so that
on the one hand, axial adjustment of the friction rings 14, 24 can
take place without delay, and, on the other hand, the axial
position of the friction rings 14, 24 in a stationary state, in
other words at a translation ratio that remains the same, can be
kept as stable as possible, so that the friction rings are not
additionally subject to fluttering or axial migration between the
cones 2, 12, 22.
[0094] Measurement of the difference in the speed of rotation
between the friction rings 14, 24 takes place by way of measurement
devices 20, 30 situated on the adjustment devices of the friction
rings 15, 25, whereby these measurement devices 20, 30 consist, in
this exemplary embodiment, of optical or inductive sensors, not
shown, which recognizes the friction ring speed of rotation by
means of notches or recesses on the friction rings.
[0095] The common control variable 19 of a first subsidiary
regulation device 17 used for the servomotors 16, 26 of the two
adjustment devices 15, 25 is superimposed on the second reference
variable 29 of the second subsidiary regulation device 27, for
regulation of the axial position of the friction ring of the second
subsidiary transmission 21. The first subsidiary regulation device
17 therefore presets the axial position for the friction ring of
the second subsidiary transmission 24, as well, whereby it is made
possible that the friction ring of the second subsidiary
transmission 24 can follow the position of the friction ring of the
first subsidiary transmission 14 almost without delay, at high
adjustment speeds. Equalization of a relative axial malpositioning
of the friction ring of the second subsidiary transmission 24
therefore takes place solely by way of the second subsidiary
regulation device 27, so that in this exemplary embodiment, the
second subsidiary regulation device 27 is used only for relative
positioning, in other words relative to the current position of the
friction ring of the second subsidiary transmission 24 itself, and
the first subsidiary regulation device 17 is used only for absolute
positioning, in other words with reference to a coordinate system
fixed on the cone, of the friction ring of the second subsidiary
transmission 21.
[0096] Regulation of the axial position of the friction ring of the
second subsidiary transmission 24 by means of the use of only the
second subsidiary regulation device 27 is also possible, without
the first reference variable 19 acting on the second servomotor 26
of the adjustment device of the friction ring of the second
subsidiary transmission 25.
[0097] The cone/friction ring transmission 1 shown in FIG. 2,
having a first subsidiary transmission 11 and a second subsidiary
transmission 21, whereby the first subsidiary transmission 11 has a
common cone 2 and a further cone 12, and the second subsidiary
transmission 21 has the common cone 2 and a further cone 22,
transfers a torque issued by way of the common shaft 3, by means of
a first power-split equalization transmission 31. The power-split
equalization transmission 31 consists of a differential
transmission (not numbered), whereby the coaxial bevel gears are
connected with the output shafts of the further cones 12, 22 of the
two subsidiary transmissions 11, 21 by way of further switchable
bevel gears, and whereby a differential case of the differential
transmission is connected to interact with the common shaft 3. An
additional bevel gear connected to interact with the differential
case of the first power-split equalization transmission 31 can
furthermore be connected, in switchable manner, with an output
shaft of the common cone 2, so that a direct gear, in other words
force transfer at a translation ratio i=1, by way of only a single
transmission element, is made possible. The switchable further
bevel gears situated at the output shafts of the further cones 12,
22 allow the representation of a reverse gear, by means of the
clutch sleeve, which is not numbered.
[0098] An equalization transmission 31 configured in this manner,
as a differential transmission, is therefore able to permit
differences in speed of rotation between the friction rings 14, 24,
in that no synchronous speed of rotation between the first
subsidiary transmission 11 and the second subsidiary transmission
21 has to be forced to occur. Consequently, a minimum of slip
always comes about at the friction rings 14, 24, thereby causing
only the further cones 12, 22 to demonstrate a speed of rotation
difference between one another. The power-split transmission 31 is
able to balance out these speed of rotation differences, and
therefore, in turn, relative movements in the differential
transmission of the power-split equalization transmission 31 occur
instead of increased slip at the friction rings 14, 24, and these
relative movements, which balance out the speed of rotation, lead
to a reduction in the degree of effectiveness of the transmission,
due to friction heat. Regulation of the axial position of the
friction rings 14, 24 according to the invention consequently
brings about an increase in the degree of effectiveness of the
transmission, because of avoidance of these relative movements as
explained.
[0099] The cone/friction ring transmission 1 having a friction ring
14 of the first subsidiary transmission 11, having a servomotor 16
that belongs to this friction ring 14, as well as an adjustment
device 15, having a friction ring 24 of the second subsidiary
transmission 21 and having a related servomotor 26, as well as an
adjustment device 25, is controlled, in the alternative embodiment
shown in FIG. 2, in such a manner that only the servomotor 20 of
the adjustment device 15 receives a control variable 19 for
regulation of the axial position of the friction ring of the first
subsidiary transmission 14 from a first subsidiary regulation
device 17, and the second subsidiary regulation device 27 regulates
the friction ring of the second subsidiary transmission 24 by way
of the second servomotor 30 as well as the second regulation device
25, in terms of its axial position, in such a manner that only the
second reference variable 28 is used for generating the second
control variable 29. In this embodiment, the reference variable 28
in turn consists of a regulation variable of the first subsidiary
transmission 11 made available by the first regulation variable
detection 20 and a regulation variable of the second subsidiary
transmission 21 made available by the second regulation variable
detection 30. In this connection, the reference variable 28
evaluated by the subsidiary regulation device is formed by the
difference in the speed of rotation of the friction rings 14, 24,
whereby here, too, an axial position of the first friction ring 14,
for example, can be used, possibly with the inclusion of a position
offset characteristic field, to take a calibration measurement into
consideration.
[0100] In deviation from the measurement devices of the regulation
variable detections 20, 30 described in FIG. 1, in this embodiment
a speed of rotation measurement of the friction rings at the small
guide wheels 5 of the adjustment devices 15, 25, is provided, in
that the speed of rotation of the small guide wheels 5 themselves
is detected. It is immediately evident that slip can occur between
a small guide wheel 5 and a friction ring, as well, and therefore
the measurement of the speed of rotation of the friction ring can
be subject to error for this reason, but this is actually very
unlikely or can be the case only to an extremely slight degree,
because no torque is transferred at this location and the small
guide wheels 5 lie very precisely against the friction ring, for
secure guidance of the latter, in any case. A correction variable
can be superimposed on this measurement variable determined on the
small guide wheel, depending on the requirements, depending on the
operating state of the cone/friction ring transmission 1, such as
stationary operation or an adjustment of the translation ratio in a
specific direction. Furthermore, a measurement at the power-split
equalization transmission 31 used in this embodiment is also
possible, whereby the relative speed of rotation of two
transmission elements can be measured, for example, at which the
relative speed of rotation or difference in speed of rotation
amounts to just zero--as explained further above--during slip-free
operation.
[0101] The cone/friction ring transmission shown in FIG. 3, having
a first subsidiary transmission 11 and a second subsidiary
transmission 21, has a second power-split equalization transmission
32, whereby this second power-split equalization transmission 32
represents a simplified embodiment of the first power-split
equalization transmission 31 according to the exemplary embodiment
from FIG. 2. For the purpose of reducing friction losses and
assembly effort, multiple subsidiary transmissions and a direct
gear connecting the common cone 2 with the common shaft 3, so as to
interact, were eliminated, thereby resulting in a further
possibility for increasing the degree of effectiveness of the
transmission, by reducing friction losses. Regulation of the axial
position of the friction rings 14, 24 shown in this exemplary
embodiment once again uses two superimposed control variables 19,
29 of the two subsidiary regulation devices 17, 27 for regulation
of the axial position of the friction ring of the second subsidiary
transmission 24.
[0102] The second subsidiary regulation device 27 uses the speed of
rotation difference of the further cones 12, 22 of the two
subsidiary transmissions 11, 21 as the reference variable, at this
point, instead of the speed of rotation difference of the friction
rings 14, 24, for relative positioning of the friction ring of the
second subsidiary transmission 24. Use of the second equalization
transmission 32, which is subject to losses in the degree of
effectiveness, preferably allows the use, in this embodiment, of
the speed of rotation difference of the further cones 12, 22 for
generating a second control variable 19 by means of the reference
variable 28 that is made available, so that making the reference
variable 28 available can take place by means of simple regulation
variable detection 20, 30 fixed in place on the housing.
[0103] FIG. 4 shows a further exemplary embodiment of a
cone/friction ring transmission 1, whereby a third power-split
equalization transmission 33 is used, which is structured as a
planetary gear and also is able to balance out differences in speed
of rotation and torque between the first subsidiary transmission 11
and the second subsidiary transmission 21, and clearly reduces the
construction space of the cone/friction ring transmission 1 in the
axial direction, as compared with the exemplary embodiments having
the first and second power-split equalization transmissions 31, 32
shown in FIGS. 2 and 3. The subsidiary regulation device 27 shown
in this exemplary embodiment uses a second reference variable 28,
which is generated from three speed of rotation signals, the speeds
of rotation of the friction rings 14, 24 and the speed of rotation
of the common cone 2, to make available the second control variable
29. Use of the speed of rotation signal of the common cone 2 made
available by way of the speed of rotation sensor 4 makes it
possible to draw conclusions concerning the slip that occurs in the
friction rings 14, 24, by way of mathematical, physical and/or
tribological models, so that instead of a speed of rotation signal,
this determined slip can also be used as a reference variable 28
for regulation of the axial position of the friction ring of the
second subsidiary transmission.
[0104] The use of an equalization transmission, such as the third
power-split equalization transmission 33 used here, does
effectively prevent the occurrence of different slip at the
friction rings 14, 24, for which reason use of this regulation on
further friction cones 12, 22 that are coupled in torsionally rigid
manner is preferably preferred, but the present regulation strategy
allows the use of a differential block in the power-split
equalization transmissions 31, 32, 33, for example, which block
prevents relative movements in the gear set of the equalization
transmissions 31, 32, 33.
[0105] In FIG. 5, a cone/friction ring transmission 1 according to
the invention is shown, with a further cone 12 of the first
subsidiary transmission 11, on which a first press-down unit 42
acts, and a further cone 22 of the second subsidiary transmission
21, on which a second press-down unit 43 acts.
[0106] The requirement of generating press-down forces that act in
the same way in both subsidiary transmissions 11, 21 is taken into
account, in this embodiment, by means of hydraulic equalization 44
disposed between the press-down units 42, 43.
[0107] The use of a regulation device according to the invention
for axial positioning of the friction rings 14, 24, in this
embodiment, requires essentially identical tribological conditions
in the friction contacts between the friction rings 14, 24 and the
cones 2, 12, 22 connected to interact by means of these friction
rings 14, 24, particularly if the second subsidiary regulation
device 27 regulates the axial position of the friction ring of the
second subsidiary transmission 24 by way of measuring the speed of
rotation of the friction rings 14, 24, or by way of measuring the
slip that is present at the friction rings. In this connection, the
hydraulic equalization 44 connects an oil-filled first pressure
chamber 45 of the first press-down unit 42 with an also oil-filled
second pressure chamber 46 of the second press-down unit 43. The
oil contained in the press-down units 42, 43 can therefore flow
back and forth between the pressure chambers 45, 46, so that the
press-down forces on the further cones 12, 22 of the two subsidiary
transmissions 11, 12 always assume the same value, and in this way,
the tribological conditions at the friction contacts of the
friction rings 14, 24 achieve the same state.
[0108] The further cones 12, 22 are mounted, on both sides, by
means of radial bearings, and therefore are freely movable in the
axial direction. All the axial forces, as well as the equalization
forces of the press-down units 42, 43, are supported by a conical
roller bearing situated on the common cone 2. Additional axial
bearings between the press-down units 42, 43 and the further cones
12, 22 uncouple the rotational movement of the further cones 12, 22
from the press-down units 42, 43.
[0109] FIG. 5 furthermore shows an alternative regulation strategy
for the second subsidiary regulation device. In this connection,
the difference of the torques applied at the further cones 12, 22
measured by way of the regulation variable detection 20, 30 is used
as the reference variable 28; this difference results from axial
incorrect positioning of the friction rings 14, 24, because a
reduction in the transferred power takes place by means of an
increase in the slip in one of the friction rings 14, 24.
[0110] The embodiment shown in FIG. 6 comprises a correspondingly
acting equalization of force between the first press-down unit 42
and the second press-down unit 43. In this embodiment, different
press-down forces acting on the further cones 12, 22 are equalized
by way of mechanical equalization 47. In this connection, the
mechanical equalization 47 acts by way of a lever situated between
the first subsidiary transmission 11 and the second subsidiary
transmission 21, which is mounted so as to rotate in its pivot
point 48, situated on its axis of symmetry, on the housing of the
cone/friction ring transmission 1, so that the levers that act on
the press-down units 42, 43 have the same active length and the
press-down forces that act on the further cones 12, 22 always have
the same value.
[0111] The cone/friction ring transmission 1 according to FIGS. 5
and 6 furthermore has a torque converter structured as a spur gear
transmission having a first gear-wheel transmission 13 and a second
gear-wheel transmission 23, in order to reduce a torque of the
common shaft 3 before this torque is introduced into the further
cone 12 of the first subsidiary transmission 11 and into the
further cone 22 of the second subsidiary transmission 21. Along
with the reduction in torque, the speed of rotation of the two
further cones is increased in proportion to the reduction in
torque, as is usual in the case of transmissions having a fixed
transmission translation.
[0112] In contrast to an embodiment of a cone/friction ring
transmission 1 having only one input cone and one output cone, the
cone/friction ring transmission 1 according to the embodiment shown
in FIG. 5 is now suitable for transferring four times the torque
originally introduced. The first doubling of the transferred torque
follows from the use of two input cones 12, 22, and, accompanying
these, two subsidiary transmissions 11, 21, and the friction
contacts therefore present twice between the input cones 12, 22 and
the common output cone 2.
[0113] The second doubling of the transferred torque, thereby
transferring four times the torque, follows from halving of the
incoming torque, as explained above, with doubling of the speed of
rotation. It is immediately evident that final adaptation of the
torque that proceeds from the cone/friction ring transmission 1 can
take place in a differential transmission that follows the
cone/friction ring transmission 1. However, the said final
adaptation of the outgoing torque does not necessarily have to be
performed with the same factor as the input-side torque conversion
by way of the gear-wheel transmissions 13, 23.
[0114] In the embodiment shown, cone-side gear wheels of the two
gear-wheel transmissions, in each instance, have about half the
diameter of a shaft-side gear wheel, disposed on the common shaft
3. However, the numbers of teeth of two gear wheels situated in
engagement within a gear-wheel transmission do not correspond to
precisely twice or half the number of teeth of the other gear
wheel, in each instance. To produce a better wear profile, the
number of teeth of one of the two gear wheels within a gear-wheel
transmission 13, 23 is reduced or increased by one tooth. This
embodiment brings about constantly different pairings of two teeth
during engagement.
[0115] FIG. 7 shows a device for applying a press-down force
between the friction rings 14, 24 and the cones 2, 12, 22, which
can be used preferably supplementally but also alternatively to the
press-down force equalizations according to FIGS. 5 and 6. In this
connection, a common press-down unit 41 is used on the common cone
2, so that the press-down force required for the transfer of force
between the cones 12, 22, in each instance, and the common cone 2
is applied by means of this single common press-down unit 41 and
not by means of the use of two separate press-down units. The
arrangement shown, with a common press-down unit 41, makes it
possible to simplify the assembly of the cone/friction ring
transmission 1 by means of the elimination of assembly-intensive
modules. Furthermore, with this arrangement, the possibility is
provided of structuring the press-down unit 41 itself, in terms of
design, in such a manner that no further components are required
for force equalization between the further cones 12, 22 of the two
subsidiary transmissions 11, 21, because the press-down unit 41
already acts uniformly on both further cones 12, 22, without any
further aids.
[0116] The press-down unit 41 applies a press-down force required
for transfer of force, at least by way of two plate springs, not
numbered, of a first subsidiary press-down device, whereby the
press-down force is constant, at first, in the entire operating
range of the cone/friction ring transmission 1. In addition to this
constant basic load, the second subsidiary press-down unit shown,
not numbered, can generate a torque-dependent press-down force by
means of a roller body and a run-up ramp on which the roller body,
also not numbered, rolls. Therefore the press-down unit 41 shown
can advantageously be used in the case of greatly varying input
torques. In particular, a torque can be measured, if necessary
directly, by way of the press-down unit 41, and used for the
regulation procedures described above, in that the displacement of
the different modules of the press-down unit 41 is used to generate
a corresponding measurement signal.
[0117] The cone/friction ring transmission 1 according to FIG. 8
has a shaft coupling 56 consisting of two universal joints, which
follows displacement of the axis of rotation 61 of the common cone
2 and also makes these possible. The shaft 51 of the common cone 2
is connected with the shaft coupling 56, whereby this shaft 51 is
mounted in the cone/friction ring transmission 1 by means of a
shaft-side friction cone bearing 52. On the side of the common cone
2 that faces away from this shaft-side friction cone bearing 52, a
shoulder-side friction cone bearing 54 is provided, which mounts
the common cone 2 in a housing of the cone/friction ring
transmission 1, at a shoulder 53. In similar manner, the two
further cones 12, 22 are also mounted in the cone/friction ring
transmission 1, whereby each of the two further cones 12, 22 has a
shaft 51 and a shoulder 53, which are furthermore used for
mounting, by means of the shaft-side friction cone bearing 52 and
the shoulder-side friction cone bearing 54. The two further cones
12, 22 are enclosed by their friction ring 14, 24, in each
instance, and transfer a torque to the common cone 2 by means of
this friction ring 14, 24.
[0118] The two bearings of the common cone 2, the shaft-side
friction cone bearing 52 and the shoulder-side friction cone
bearing 54, form a floating bearing, in each instance, in this
embodiment according to FIG. 8, thereby making it possible for
axial shaft displacement to take place at any desired location
along the axis of rotation 61 of the common cone 2. Clamping in the
axial direction only takes place, seen from the common cone 2,
behind the shaft coupling 56, on the guide bearing 55. In this
exemplary embodiment, the guide bearing 55 is structured as a
conical roller bearing, and supports the axial forces on a shoulder
situated on the shaft 51. In contrast to this, the two further
cones 12, 22 of the two subsidiary transmissions 11, 21 have a
fixed/floating mounting usual in the state of the art, with a
conical roller bearing as the shoulder-side friction cone bearing
54, and a cylindrical roller bearing as the shaft-side friction
cone bearing 52.
[0119] The exemplary embodiment according to FIG. 8 allows
translational offset, particularly by means of the two floating
bearings of the common cone 2, by means of its shaft-side friction
cone bearing 52 and its shoulder-side friction cone bearing 54, and
also rotational offset of the common cone 2, in that the two
friction cone bearings 52, 54 of the cone 2 have a degree of
freedom, in each instance, in the direction of the axes of rotation
52, 53 of the first further cone 12 and of the second further cone
22. In an exemplary embodiment that is not shown, however, it is
also possible to do without the guide bearing 55 and to replace one
of the two friction cone bearings 52, 54 with an angularly movable
bearing, for example a spherical roller bearing or a self-aligning
ball bearing. Such an exemplary embodiment allows mounting of the
common cone 2 similar to the method known in the state of the art,
whereby the translational freedom of movement of the other friction
cone bearing, in each instance, of the floating bearing, is
maintained by means of the angular mobility of the fixed bearing.
In this regard, an exemplary embodiment having a rotationally
movable bearing as a friction cone bearing makes available a common
cone having only one degree of freedom, a rotational degree of
freedom.
[0120] A common cone having two degrees of freedom, whereby the
axis of rotation 61 of the common cone 2 can also be guided
parallel to the two further axes of rotation 62, 63 of the first
and of the second further cone, also always leads to parallelity of
the cone surface 57 with cone surfaces of the two further cones 12,
22. In such an embodiment, as it is also shown in FIG. 8, a ring
contact surface 58 of a friction ring 14, 24 of the first or of the
second subsidiary transmission 11, 21 is equipped with a surface
structured, at least in cross-section, as a straight line. This
brings about linear contact between the ring contact surface 58 and
the cone surface 57, as is immediately evident. If instead of a
cone 2 having a floating/floating mounting, a common cone 2 having
a fixed/floating mounting is used, then the common cone 2, as has
already been explained above, has only one degree of freedom of
rotation instead of one degree of freedom of rotation and an
additional degree of freedom of translation. However, this
restriction of the degrees of freedom of the common cone 2 leads to
the result that the cone surface 57 can no longer be guided
parallel to the surfaces of the further cones 12, 22. Consequently,
it is problematical, in a certain sense, to also no longer
structure the ring contact surface 58 of the two friction rings 14,
24 to be level, at least level in a cross-section. A ring contact
surface that is structured to be crowned, in other words a contact
surface that has a convex curvature at least in the axis plane, can
balance out the angle offset of the common cone 2. In this
connection, impermissibly high edge pressure at one of the two
friction rings 14, 24 does not occur.
[0121] As is immediately evident, a cone/friction ring transmission
structured according to FIG. 8, having a movable common cone 2, can
also be structured in such a manner that the further cones 12, 22
or at least one of these further cones 12, 22 is structured as a
movable cone. However, it is immediately evident that a movable
common cone 2 is able to balance out non-uniform contact forces at
the two friction rings 14, 24, by means of a press-down device
applied in this common cone 2.
[0122] The shoulder-side friction cone bearing 54 of the common
cone 2 is disposed in a horizontally structured cone guide 64
according to FIG. 9. This guide 64 allows migration of the friction
cone bearing, in this case of the shoulder-side friction cone
bearing 54, along an axis plane 60, which is spanned by the axes of
rotation 62, 63 of the two further cones 12, 22 and by the axis of
rotation 61 of the common cone 2. The term "horizontal" refers, in
this case, to a direction within the axis plane, whereby "vertical"
would mean a movement direction perpendicular to the axis plane
60.
[0123] In the exemplary embodiment according to FIG. 9, the bearing
guide 64 is structured as an oblong hole having an orientation
relative to the axis plane 60. In this connection, it is also
possible that the bearing guide 64 has an accommodation or socket
for an outer ring of the shoulder-side friction cone bearing 54 and
therefore the bearing guide 64 itself is disposed within a housing
59 of the cone/ring transmission 1, as a carriage. The use of a
separate component as a carriage for a bearing guide 64 furthermore
allows better clamping of the friction cone bearing used, in each
instance, and uncoupling of the translational guidance of the
common cone 2 within the axis plane 60 and the rotational mounting
of the common cone 2 by means of the friction cone bearing, in each
instance.
[0124] If a press-down device within the common cone 2 is
eliminated, it is also possible, alternatively to the embodiment
described above, that two friction cone bearings of the two further
cones 12, 22 have a friction cone bearing guide 64, whereby in such
an exemplary embodiment, these bearing guides 64 can also be
equipped with press-down devices, in order to brace the two further
cones 12, 22 in the direction of the common cone 2, by means of a
force.
[0125] Instead of electronic control of the two adjustment devices
15, 25, control or regulation of the second subsidiary transmission
21 can also take place mechanically, as is explained as an example,
using the exemplary embodiment shown in FIGS. 10 to 15. In this
connection, control or regulation of the first subsidiary
transmission 11 preferably takes place in known manner, so that
here, known devices can be used, in particular. Thus, for example,
the servomotor 16, by way of a transmission arrangement 71, can
displace a case 72 at a work angle, which case in turn displaces
the friction ring 14 in terms of its work angle, by way of an
adjustment bridge 73, which is mounted in axially displaceable
manner on this case and a rotation prevention device 74, so that
this friction ring migrates accordingly, on its own and due to the
rotation of the cones 2, 12. Alternatively, the case 72 can also be
structured as a two-axle case or otherwise, as long as it
accordingly guides the adjustment bridge axially and allows an
angle adjustment. Likewise, the rotation prevention device 72 can
also be implemented by means of a second guide rod or in the first
guide rod of the case 72. Also, it is not absolutely necessary to
configure the adjustment bridge 73 in the manner of a bridge, as
long as it guarantees sufficiently stable guidance and angle
adjustment.
[0126] In this exemplary embodiment, the position of the adjustment
bridge 73 is transferred to the second adjustment device 25 by
means of a transfer rod 76, by way of a mechanical position sensor
75, which can also be used for recording measurement values, if
necessary, by way of a potentiometer.
[0127] The second adjustment device 25 also has a case 77 that
mounts an adjustment bridge 78 in axially displaceable manner, by
means of a rotation prevention device 79, in known manner, and
allows angle adjustment of the friction ring 24 mounted by the
adjustment bridge 78 and allows the adjustment bridge 78 to freely
follow axial migration of the friction ring 24. However, the case
77 is controlled by way of a feedback linkage 81, which encloses
the position sensor 80, on the one hand, and the control rod 82, on
the other hand, and is oriented in such a manner that an axial
position of the friction ring 24 can be preset by way of the
control rod 82, which position is then approached, under the
control of the position sensor 80, by means of mechanical feedback
of the feedback linkage 81.
[0128] In this connection, the transfer rod 76 is coupled with the
control rod 82, so that the mechanically determined position of the
adjustment bridge 73 and therefore of the friction ring 14 serves
as a reference variable of the second adjustment device 25.
[0129] For the remainder, modules of the exemplary embodiment shown
in FIGS. 10 to 14 that act in identical manner are also identically
numbered, so that in order to avoid repetitions, they will not be
described again here, and reference is made to the above
explanations.
[0130] In this connection, the adjustment devices 15, 25 do not
necessarily have to be provided on the side of the cones 12, 22
that faces away from the cone 2, in each instance. Instead, it is
possible to provide the adjustment devices 15, 25 above or below
the cones 2, 12, 22, which are essentially disposed in one plane,
as is shown as an example in FIG. 15. In this way, mechanical
coupling can be significantly simplified, if applicable.
[0131] In the exemplary embodiment shown in FIG. 15, mechanical
coupling of the two adjustment devices 15, 25 is accordingly also
provided, whereby the adjustment bridge 73 of the adjustment device
15 is regulated in known manner, while the adjustment bridge 78 of
the adjustment device 25 is configured as a following adjustment
device, in that a case of the adjustment device 25, not shown,
allows axial displacement of the adjustment bridge 78 in the manner
already described above, but in deviation from the exemplary
embodiment described above, does not preset an angular position but
rather can freely follow an angular position preset by the
adjustment bridge 78.
[0132] By means of a rotational/sliding connection 85 between the
two adjustment bridges 73, 78, the adjustment bridge 78 is tilted
if it has an axial position that deviates from the axial position
of the adjustment bridge 73. The case of the adjustment device 25
follows this tilting accordingly, as has been described above, so
that the friction ring can migrate in accordance with the angular
position, until the angle has been regulated back to zero.
Therefore if the adjustment bridge 73 is displaced, the adjustment
bridge 78 or the corresponding friction ring follows this
displacement.
[0133] In this exemplary embodiment, the rotational/sliding
connection 85 is formed by a groove in the adjustment bridge 78,
into which a round tongue of the adjustment bridge 73 engages.
Fundamentally, such an arrangement of an elongated groove and a
round motion link makes it possible to implement a
rotational/sliding connection in almost any desired manner, whereby
ultimately, even more complex couplings, up to the coupling
corresponding to the exemplary embodiment described above, are
possible.
REFERENCE SYMBOL LIST
[0134] 1 cone/friction ring transmission [0135] 2 common cone
[0136] 3 common shaft [0137] 4 speed of rotation sensor [0138] 5
small guide wheel [0139] 11 first subsidiary transmission [0140] 12
further cone of the first subsidiary transmission [0141] 13 first
gear-wheel transmission [0142] 14 friction ring of the first
subsidiary transmission [0143] 15 adjustment device of the friction
ring of the first subsidiary transmission [0144] 16 first
servomotor [0145] 17 first subsidiary regulation device [0146] 18
first reference variable [0147] 19 first control variable [0148] 20
first regulation variable detection [0149] 21 second subsidiary
transmission [0150] 22 further cone of the second subsidiary
transmission [0151] 23 second gear wheel mechanism [0152] 24
friction ring of the second subsidiary transmission [0153] 25
adjustment device of the friction ring of the second subsidiary
transmission [0154] 26 second servomotor [0155] 27 second
subsidiary regulation device [0156] 28 second reference variable
[0157] 29 second control variable [0158] 30 second regulation
variable detection [0159] 31 first power-split equalization
transmission [0160] 32 second power-split equalization transmission
[0161] 33 third power-split equalization transmission [0162] 41
common press-down unit [0163] 42 first press-down unit [0164] 43
second press-down unit [0165] 44 hydraulic force equalization
[0166] 45 first pressure chamber [0167] 46 second pressure chamber
[0168] 47 mechanical force equalization [0169] 48 pivot point
[0170] 51 shaft [0171] 52 shaft-side friction cone bearing [0172]
53 shoulder [0173] 54 shoulder-side friction cone bearing [0174] 55
guide bearing [0175] 56 shaft coupling [0176] 57 cone surface
[0177] 58 ring contact surface [0178] 59 housing [0179] 60 axis
plane [0180] 61 axis of rotation of the common cone [0181] 62 axis
of rotation of the first further cone [0182] 63 axis of rotation of
the second further cone [0183] 64 bearing guide [0184] 71
transmission arrangement [0185] 72 case [0186] 73 adjustment bridge
[0187] 74 rotation prevention device [0188] 75 position sensor
[0189] 76 transfer rod [0190] 77 case [0191] 78 adjustment bridge
[0192] 79 rotation prevention device [0193] 80 position sensor
[0194] 81 feedback linkage [0195] 82 control rod [0196] 83
rotational/sliding connection
* * * * *