Source: http://www.patentsencyclopedia.com/app/20080220929
Timestamp: 2017-07-26 14:04:25
Document Index: 87236973

Matched Legal Cases: ['art\n11', 'art 11', 'art 11', 'art\n11', 'art 11', 'art 11', 'art\n11', 'art\n11']

Engine-Driven Vehicle Having a Gear Mechanism for an Auxiliary Unit, in Particular as a Planetary Gear Set for Integration Into the Drive of the Auxiliary Unit, and Corresponding Gear Mechanism - Patent application
Patent application title: Engine-Driven Vehicle Having a Gear Mechanism for an Auxiliary Unit, in Particular as a Planetary Gear Set for Integration Into the Drive of the Auxiliary Unit, and Corresponding Gear Mechanism
Jens Gebhardt (Bernsbach, DE)
Andre Gopfert (Waldenburg, DE)
Dominik Zschocke (Chemnitz, DE)
MBM Technologie GMBH
IPC8 Class: AF16H354FI
Patent application number: 20080220929
The present invention relates to a gear mechanism, in particular to a
planetary gear set, which can be used in a motor vehicle in order to make
it possible, in an advantageous way in terms of energy, to drive
auxiliary units of the motor vehicle from the main drive device in a
speed-adapted and therefore power-adapted manner.Claims:
1. An engine-driven vehicle comprising:a main drive device,an auxiliary
drive device for an auxiliary unit, wherein the main drive device couples
with the auxiliary drive device and transmits power generated on the main
drive device dependent on the rotational speed to the auxiliary drive
device,such thatbetween the auxiliary drive device and the auxiliary unit
a gear mechanism shiftable without interruption in multiple stages,
comprising a sun gear an inner planetary gear an outer planetary gear and
a ring gear is arranged, wherein the drive takes place via the ring gear.
2. The engine-driven vehicle according to claim 1, wherein the gear
mechanism steps up the transmission while maintaining the direction of
3. The engine-driven vehicle according to claim 1, wherein the gear,
mechanism, comprises several operating modes of which at feast one first
operating mode is an externally actuated shift.
4. The engine-driven vehicle according to claim 1, wherein a second
operating mode stops the auxiliary unit.
5. The engine-driven vehicle according to claim 3 4, wherein the operating
modes comprise up to three shifting stages, wherein by means of brake an
operating mode (i≠1) can be switched on.
6. The engine-driven vehicle according to claim 5, wherein the 3 shifting
stages comprisea first shifting stage i=0,a second shifting stage i=1
anda third shifting stage i≠1,wherein the first shifting stage
brings about the stoppage, preferentially of the auxiliary unit,the
second shifting stage brings about an identical rotational speed
transmission and the third shifting stage i≠1 brings about step-up
transmission or step-down transmission.
7. The engine-driven vehicle according to claim 1, wherein the ring gear
is driven by a pulling means.
8. The engine-driven vehicle according to claim 1, wherein the ring gear
is designed as internally toothed belt pulley.
9. The engine-driven vehicle according to claim 1, wherein the gear
mechanism transmits a force flow from the ring gear to the sun gear free
of deflection, preferentially with the same orientation direction, more
preferably in the same plane.
10. The engine-driven vehicle according to claim 1, wherein the gear
mechanism transmits a moment flow from the ring gear to the sun gear free
of deflection, preferentially with the same orientation direction, more,
11. The engine-driven vehicle according to claim 1, wherein the gear
mechanism comprises a substantially cylinder-shaped planet carrier, a
substantially cylinder-shaped sun gear and a substantially
cylinder-shaped ring gear.
12. The engine-driven vehicle according to claim 1, wherein at least one
of the planetary gears of the planetary gear set comprising two planetary
gears is embodied as slot-carrying planetary gear, through whose slot an
oil mist is able to get to a planetary gear bearing.
13. A planetary gear set to be coupleable between an main drive device and
an auxiliary device in such a kind that:the planetary gear set is
intended to transmit power of a main drive device generated in a
rotational speed-dependent manner to an auxiliary drive device, wherein
the gear mechanism is a gear mechanism that can be shifted without
interruption in multiple stages, and the gear mechanism comprises a sun
gear,an inner planetary gear,an outer planetary gear anda ring gear,and
the ring gear constitutes the outer drive means via which the power from
the main drive device is introduced into the auxiliary drive device tied
to the sun gear.
14. The planetary gear set according to claim 13, in which on the ring
gear an externally positioned running surface is present, which serves as
contact or introduction surface for a drive to be fed from the main drive
15. The planetary gear set according to claim 13, in which the gear
mechanism, steps up the transmission while maintaining the direction of
16. The planetary gear set according to claim 13, in which the gear
mechanism comprises several operating modes of which at least one first
17. The planetary gear set according to claim 16, in which a second
18. The planetary gear set according to claim 16, in which the operating
19. The planetary gear set according to claim 18, in which the three
shifting stages comprisea first shifting stage i=0,a second shifting
stage i=1 anda third shifting stage i≠1wherein the first shifting
stage brings about the stoppage preferentially of the auxiliary unit,the
second shifting stage brings about identical rotational speed
20. The planetary gear set according to claim 13, in which the ring gear
21. The planetary gear set according to claim 13, in which the ring gear
22. The planetary gear set according to claim 13, in which the gear
mechanism, transmits a force flow from the ring gear to the sun gear free
23. The planetary gear set according to claim 13, in which the gear
24. The planetary gear set according to claim 13, in which the gear
25. The planetary gear setup according to claim 13, in which at least one
gears is embodied as slot-carrying planetary gear through whose slot an
26. The planetary gear set according to claim 13, in which a shifting
device is embodied as braking device, more preferably electromagnetic
braking device, which consists of at least two braking elements and
shifts between the operating modes (i=0, i=1, i≠1) through braking.Description:
[0001]The present invention relates to an engine-driven vehicle with a
main drive device, with an auxiliary drive device for an auxiliary unit,
wherein the main drive device is coupled to the auxiliary drive device
and transmits power generated on the main drive device to the auxiliary
[0002]Such engine-driven vehicles are known from the general prior art.
These can be land, air or water vehicles which are driven with, any main
drive device for example a combustion engine, an electric motor or the
like. Such engine-driven vehicles comprise auxiliary units which likewise
have to be driven via an auxiliary drive device. Such auxiliary units are
for example a power steering pump, an air-conditioning compressor, a fan
[0003]The auxiliary drive device in such engine-driven vehicles is
regularly driven by an output shaft of the main drive device.
[0004]Because of increasing rated outputs, auxiliary units in
engine-driven vehicles require correspondingly increased drive power.
This results in increased energy consumption and in the case of
combustion engines also in increased total pollutant emission of the
engine-driven vehicle. Also a reason for increased energy consumption and
increased pollutant emission is that the auxiliary units are dependent on
the operation of the main drive, i.e. are driven by said main drive
irrespective of whether the auxiliary unit concerned happens to be in
need of power or not.
[0005]If the auxiliary unit for example is a power steering pump it has to
provide the maximum power at low speeds since rapid steering movements
with large steering angles are only required then. Low speed however also
means low engine rotational speed and thus a low drive rotational speed
of the power steering pump in the auxiliary drive. For this reason the
power steering pump must be dimensioned so that it is of a sufficiently
large nominal size in order to be able to make available satisfactory
steering assistance even at a low drive rotational speed.
[0006]If the auxiliary unit is an air-conditioning compressor it is
generally only operated at idle speed after the engine is started until
the vehicle is driven off and even while driving said air-conditioning
compressor has no permanently increased rotational speed at its disposal
because of shifting operations and vehicle stoppage with idle speed. If
maximum output happens to be demanded for example following a prolonged
stoppage phase with solar radiation this compressor must be designed so
that the rated output is achieved even at low rotational speeds. During
subsequent driving with higher engine rotational speeds merely a
considerably reduced cooling output is utilized once the vehicle interior
[0007]The two aforementioned examples of auxiliary units thus show a less
than optimal adaptation of power demand and power output or rotational
speed, demand and rotational speed availability.
[0008]Earlier examples are already known from the patent literature in
which it was attempted, through additional gear mechanisms for auxiliary
units which were driven from the main drive device such as the crankshaft
or an output device connected with the crankshaft such as a belt pulley,
to operate the auxiliary unit with rotational speeds that were modified
compared to the main drive device. Here, measures are more preferably
known which operate with different transmission ratios as a function of
[0009]DE 36 22 335 A1 shows a planetary gear set attached to the camshaft
which can be shifted backwards and forwards between a transmission ratio
of 1:1 and a transmission ratio of 1:3 through a braking device to be
engaged. According to the description a mean rotational speed range
between approximately 700-1000 rpm and 2'000-2400 rpm is to be raised.
Although the planetary gear set operates with a hysteresis, it only
offers two rotational speeds that can be alternately selected. The gear
mechanism thus provides no multi-stage shifting capability. In addition,
the only figure of DE 36 22 335 A, which represents the gear mechanism
proper, shows the planetary gears whose teeth are engaged with sun gear
and ring, gear, wherein the output shaft is embodied similar to a ring
[0010]GB 20 22 202 A describes two exemplary embodiments, shown in FIGS. 2
and 5, of a temperature-dependent fan drive which differ in their
controls. In GB 20 22 202 A, too, only a single planetary gear can be
seen whose teeth are engaged with sun gear and ring gear, wherein the
output shaft is embodied similar to a ring gear.
[0011]The object of the present invention therefore is to further embody
an engine-driven vehicle of the type mentioned at the outset that the
rigid coupling of an auxiliary unit to the rotational speed of the main
drive device is omitted in an advantageous manner in that with the
building space available in the auxiliary drive a solution is looked for
which in terms of energy can be advantageously integrated. Furthermore
the object consists in creating a corresponding gear unit which can also
be installed in a motor vehicle of today's type.
[0012]According to the invention the object is solved in that a gear
mechanism that can be shifted without interruption in multiple stages is
arranged, between the auxiliary drive device and the auxiliary unit. The
gear mechanism is characterized by the features of the corresponding
[0013]With the arrangement of a gear mechanism that can be shifted without
interruption in multiple stages between the auxiliary drives device and
the auxiliary unit it is possible to save a lot of energy. With
combustion engines the fuel saving could be around 0.5 to 1.0 litre/100
km. The overall pollutant emission with combustion engines is also
[0014]A further advantage according to the present invention must be seen
in that the gear mechanism comprises a ring gear via which the drive is
effected. In addition to this it is an advantage that the gear mechanism
also comprises a sun gear, an internal planetary gear and an external
planetary gear. With these components the gear mechanism can be embodied
as a planetary gear set and configured in such a way that in an
advantageous manner it provides step-up transmission while maintaining
the direction of rotation. The possibility of step-up transmission with
absent or low load permits the operation of the auxiliary unit favourable
in terms of energy with minimum rotational speed with identical
rotational speed transmission. If power is demanded it is possible to
change to step-up transmission without interruption in a jumping function
so that the demanded power is available adequately spontaneously.
[0015]A further advantage consists in that the gear mechanism has several
operating modes of which at least one first operating mode can be shifted
externally actuated.
[0016]A further advantage consists in that a second operating mode stops
the auxiliary unit. In addition to this it is also advantageous that the
operating modes comprise three switching stages. In this preferred
advantageous embodiment the first switching stage results in stopping
(i=0), the second switching stage in identical rotational speed
transmission (i=1) and the third switching stage in step-up transmission
or step-down transmission (i≠1).
[0017]Finally it is of advantage that the ring gear is driven through a
pulling means such as for example a belt. To this end the ring gear in an
advantageous manner is to be designed as internally toothed belt pulley.
With these features it is possible to integrate the gear mechanism into
the belt drive for an auxiliary unit.
[0018]Various embodiments of the present invention are described in more
detail in the following by means of the drawings. It shows:
[0019]FIG. 1 a schematic perspective view of a gear mechanism designed as
planetary gear set according to the present invention for use in an
engine-driven vehicle;
[0020]FIG. 2 a schematic lateral view of the planetary gear set from FIG.
[0021]FIG. 3 a schematic exploded view of the planetary gear set from FIG.
[0022]FIG. 4 a schematic, perspective view of a further embodiment of a
gear mechanism designed as planetary gear set according to the present
invention for use in an engine-driven vehicle;
[0023]FIG. 5 a schematic lateral view of the planetary gear set from FIG.
[0024]FIG. 6 a schematic exploded representation of the planetary gear set
[0025]FIG. 7 a sectional view of a further exemplary embodiment of a
planetary gear set according to the invention;
[0026]FIG. 8 a force flow with deflections which is more disadvantageous
compared with FIG. 7; and
[0027]FIG. 9 a suitable planetary gear of a similar embodiment according
to FIG. 1 to 3 or according to FIG. 4 to 6 or according to FIG. 7.
[0028]Similar parts have been designated with the same reference symbols
although in some aspects, which are not so essential to the
understanding, they may differ from one another.
[0029]FIG. 1 schematically shows a perspective representation of a gear
mechanism 1 for installation in an engine-driven vehicle according to
Claim 1 in partial section. The gear mechanism 1 in the present
embodiment is designed as planetary gear set. The gear mechanism 1
comprises a ring gear 3. Which in the present embodiment, is designed as
internally toothed belt pulley. The ring gear 3 is engaged with an outer
planetary gear 5. The outer planetary gear 5 is engaged with an inner
planetary gear 7. The inner planetary gear 7 is engaged with a sun gear
9. The sun gear encloses a coupling device 11 which in the present
embodiment is designed as a cone coupling and comprises the coupling part
11.1 and a second coupling part 11.2.
[0030]In addition, the coupling device 11 also comprises a freewheeling
coupling 11.3. The first coupling part 11.1 and the second coupling part
11.2 are seated on a coupling carrier 13. The coupling carrier 13 is
mounted on a torque support 15 and on an adapter 17. Via the adapter 17,
the gear mechanism 1 is mounted in the vicinity of the relevant auxiliary
unit or in the vicinity of the relevant auxiliary drive device in such a
manner that it is integrated in the auxiliary drive of the auxiliary
unit. A planet carrier device 19 is split into a first planet carrier
19.1 and 19.2 and serves for the guidance and mounting of the planetary
gears 5,7 and for the introduction and discharge of the torque.
[0031]FIG. 3 is a schematic exploded view of the gear mechanism from FIG.
1. On the torque support 15 the components described with, reference to
FIG. 1 are arranged: the first coupling part 11.1, the first, right
planet carrier 19.1, the coupling carrier 13, the ring gear 3, the
freewheeling coupling 11.3, the sun gear 9, the inner planetary gears 7
and the outer planetary gears 5, the second coupling part 11.2, the
second, left planet carrier 19.2, the adapter 17.
[0032]Accordingly, the gear mechanism 1 substantially comprises a ring
gear 3 as well as a or a plurality of outer planetary gears 5 permanently
engaged with said ring gear and inner planetary gears 7 in turn
permanently engaged with said outer planetary gears, which inner
planetary gears are engaged with the concentrically arranged sun gear 9,
wherein the drive is effected via the ring gear 3.
[0033]In a preferred embodiment the gear mechanism has several operating
modes, wherein three operating modes correspond to three shifting
positions, namely a first shifting stage, which brings about stoppage or
complete decoupling, a second shifting stage, which brings about
identical rotational speed transmission (i=1) and a third shifting stage
which brings about step-up operation or step-down operation (i≠1).
[0034]The shifting positions can be triggered either self-actuated and/or
based, on the direction of rotation or externally actuated, as for
example hydraulically or electromechanically or in combination of the
[0035]The gear mechanism 1 that can be shifted without interruption in
multiple stages can comprise kinematics with fail-safe characteristics,
so that upon failure of the actuator the gear mechanism 1 spontaneously
returns to (i=1).
[0036]The arrangement according to the invention allows the operation of
the auxiliary unit with a rotational speed adapted, compared with the
rigid coupling, to the rotational speed of a crankshaft, so that even
with reduced size of the auxiliary unit said auxiliary unit is able to
provide the same output in the design point. Step-up transmission, of the
gear mechanism 1 that can be shifted without interruption in multiple
stages with the value (i=x) allows an increase of the rotational speed of
the auxiliary unit by the factor x and allows a reduction of the specific
displacement volume of the unit to the value 1/x.
[0037]Upon a change to operation with i=1 the energy consumption of the
respective auxiliary unit is reduced because of the reduced power
consumption resulting from the reduced size.
[0038]Through the arrangement according to the invention the output, of
the associated gear mechanism 1 shiftable free of interruptions in
multiple stages or planetary gear set and the auxiliary unit with absent
or low load at i=1 with low rotational speeds and optimum efficiency, low
wear and minimum noise. Accordingly, the rated quantities and thus the
power consumption of the power steering pump described as an example and
the air-conditioning compressor described as an example can be reduced to
1/x. Thus, considerable savings potentials both on the investment side
with the costs of the units as well as with the operating costs through
lower fuel consumption because of the reduced total power consumption are
achieved. At the same time, the pollutant balance is improved and the
power available to drive the vehicle is increased.
[0039]Two states are exemplarily described (in a first embodiment):
[0040]State I. (Transmission ratio 1:1) [0041]Drive via belt pulley
[0042]Output via planet carrier [0043]Cone coupling open
[0044]Freewheeling coupling engaged [0045]Two gear elements are rigidly
connected, which means the gear mechanism 1 circulates as a block
[0046]State II. (Transmission ratio 1:x) [0047]Drive via belt pulley
[0048]Output via planet carrier [0049]Cone coupling closed.
[0050]Freewheeling coupling in overrun mode [0051]Sun gear stationary,
which means gear mechanism in step-up transmission
[0052]FIG. 4 schematically shows a perspective representation of a gear
mechanism 2 for installation in an engine-driven vehicle according to
Claim 1 in partial section. The gear mechanism operates according to the
inventive principle of the subordinate claim. The gear mechanism 2 in the
present embodiment is designed as planetary gear set. The gear mechanism
2 comprises a ring gear 3, which in the present embodiment is designed as
9. The planetary gears are connected with the planet carrier 19. A
shifting device 12 is adapted to the planet carrier which in the present
embodiment is designed as electromagnetic brake and comprises the braking
element 12.1 and a second braking element 12.2.
[0053]In addition to this, the shifting device 12 also comprises a
freewheeling coupling 11.3. The first braking element 12.1 is connected
in a rotationally fixed, manner with the housing of the respective
auxiliary unit and thus establishes the support of the torque in the
shifted mode. The second braking element 12.2 is connected with the
planet carrier 19. This planet carrier 19 is divided into a first planet
carrier 19.1 and 19.2 and serves for the guiding and accommodating of the
planetary gears 5, 7 and to introduce, or discharge the moment, more
preferably a rotational or braking moment. Via the sun 9 the gear
mechanism, 2 is mounted in a suitable manner in the vicinity of the
corresponding auxiliary unit or in the vicinity of the corresponding
auxiliary drive device in such a manner that said gear mechanism is
integrated in the auxiliary drive, of the auxiliary unit.
[0054]FIG. 6 schematically shows an exploded representation of the gear
mechanism 2 from FIG. 4. The components described with reference to FIG.
4 are arranged about the sun 9 the first braking element 12.1, the first,
right planet carrier 19.1, the ring gear 3, the freewheeling coupling
11.3, the sealed bearing 23, the inner planetary gears 7 and the outer
planetary gears 5, the second braking element 12.2, the second, left
planet carrier 19.2, the clamping screws 31.
[0055]The gear mechanism 2 thus substantially comprises a ring gear 3 as
well as 1 or a plurality of outer planetary gears 5 permanently engaged
with said ring gear and inner planetary gears 7 which in turn are
permanently engaged with said ring gear, which are engaged with the
concentrically arranged sun gear 9 wherein the drive is effected via the
ring gear 3.
[0056]Triggering the shifting positions between the shifting modes can
either take place self actuated and/or dependent on the direction of
rotation or externally actuated, such as for example hydraulically,
pneumatically or electromechanically or in a combination of the mentioned
[0057]When changing to the operation with i=1 the energy consumption of
the respective auxiliary unit is reduced because of the reduced power
consumption which results from the reduced size.
[0058]Through the arrangement according to the invention the output of the
associated gear mechanism 2 shiftable without interruption in multiple
stages or planetary gear set and the auxiliary unit with absent or low
load at i=1 run with low rotational speeds and optimal efficiency of 100%
without wear and noise. Accordingly, the rated quantities and thus the
of the air-conditioning compressor described as an example can be reduced
to 1/x. Thus considerable savings potentials both on the investment side
lower fuel consumption because of the reduced overall power consumption
are achieved. At the same time the pollutant balance is improved and the
power available to drive the vehicle increased.
[0059]Exemplarily two states are described (in a second embodiment):
[0060]State I: (Transmission ratio 1:1) [0061]Drive via belt pulley
[0062]Output via sun [0063]Brake open [0064]Freewheeling coupling engaged
[0065]Two gear elements are rigidly connected, i.e. the gear mechanism 2
circulates as a block.
[0066]State II. (Transmission ratio 1:x) [0067]Drive via belt pulley
[0068]Output via sun [0069]Brake closed [0070]Freewheeling coupling in
[0071]Planet carrier is stationary, i.e. the gear mechanism is in step-up
[0072]The planet carrier device 19 according to the exemplary embodiments
of FIGS. 4 to 6 is clamped through clamping screws 31, which extend from
the right planet carrier 19.1 to the left planet carrier 19.2, as planet
carrier clamping screws. The gear sets of the planetary gear set, which
always occur in pairs, are located between the planet carrier devices.
The ring gear 3 is driven from the drive shaft rigidly coupled, to the
rotational speed via its running surface 21 preferentially shrunk-on in
the case of a belt drive through a drive (not shown) such as for example
a chain or a belt. The planetary step-up gear mechanism 2 arranged within
the ring gear 3, in a space-saving manner through the internal
arrangement in the annulus about the output, transmits the rotational
speed to the component of the auxiliary unit (not shown) connected to the
drive. A suitable transmission for many auxiliary units is a step-up
transmission. As already explained at the outset, for example in the case
of an auxiliary unit power steering pump, more than 99.8% of the running
power of the pump has to be applied to operations during which the gear
mechanism circulates as a block free of loss. The long-term measurement
of 99.8% has been obtained with an embodiment that was determined with a
pump that was constructed with half the specific delivery volume compared
with a pump without gear mechanism. In only 0.2% of the operating
conditions or the operating time is a step-up drive by the factor 2
required. Other auxiliary units show similarly dramatic maladaptations so
that a rotational speed adaptation substantially contributes to the
increase of efficiency. From the ring gear 3 with its internal teeth 25
the rotation, preferentially circulating as a block loss-free, is
transmitted to the sun gear 9 via two planetary gears 5, 7, each which
occur multiply, e.g. in triplicate or quadruplicate. The shifting device
12 with a freewheeling coupling 11.3 ensures the equally oriented
direction of rotation between drive and output of the planetary gear set
arranged in the ring gear 3 with opened brake in order to enable
synchronous circulation as a, block. While with desired transmission
ratios of i≠1, e.g. in low rotational speed ranges of the
combustion engine, the brake is briskly closed by the shifting device 12
and the freewheeling coupling 11.3 overruns without unloading. By means
of the brake, which consists of the braking, elements 12.1 and 12.2, the
planet carrier 19 is connected with the housing of the auxiliary unit
(not graphically represented) and the transmission ratio i≠1
activated. The planetary gears 5, 7 are in mesh with each other. The
inner planetary gear 7 transmits the drive power to the sun gear 9. The
outer planetary gear 5 is driven through the internal teeth 25 of the
[0073]FIGS. 2 and 5 each show a sectional view through two different
embodiments of the invention according to the FIGS. 1 and 4. The
planetary gears 5, 7, the sun gear 9, the ring gear 3 with its internal
teeth 25 look like a double-constructed planetary system from a lateral
perspective, wherein the two inter-meshing planetary gears 5,7, offset
relative to each other both in circumferential direction and also in the
direction towards the centre, can transmit the power from the outside to
the inside without additional deviations. To understand the remaining
reference symbols shown, reference is made to the explanations relating
to the FIGS. 1, 3, 4 and 6.
[0074]Although it is crowded in ring gears 3 according to the invention,
for example a ring gear 3 for a power steering pump has an outer diameter
of approximately 100 mm to 130 mm and for example a ring gear 3 for a
compressor, more preferably an air-conditioning compressor, has an outer
diameter of approximately 90 mm to 135 mm, according to an aspect an
auxiliary unit gear mechanism according to the invention is equipped with
two intermeshing planetary gears each, for in this way a step-up
transmission ratio with a spread of just under 6 up to values of more
than 1.5, e.g. 1.7 can be generated. The transmission maintains the
direction of rotation between driven belt pulley and sun gear. Teeth
numbers of approximately 100 teeth for the internal toothing 25 of the
ring gear 3 have proved favourable in tests, which means a tooth division
of the internal toothing of 1.8° over the internal circumference,
while the sun gear 9 comprises 17 or 60 teeth for example. The gear space
enclosed by the seal 29 (see FIG. 3 and FIG. 6) and the sealed bearing
23, in which the gears are located, is protected from dirt entering the
space and lubricants being lost from the space.
[0075]A further aspect of the present invention can be taken from FIG. 7
compared with FIG. 8. FIG. 7 shows how the force or moment flow (F) is to
be realised in a planetary gear set according to the invention. The force
flow (F) occurs in the same plane from the outside to the inside. Only
the force-discharging speed-adapted element, e.g. the sun gear 9, is
subjected to a force deflection and concomitant moment deflection. The
remaining tooth transmissions between ring gear 3 of the gear mechanism 2
to the outer planetary gears 5 on the one hand, the outer planetary gears
5 to the inner planetary gears 7 on the other hand and from the inner
planetary gears 7 to the sun gear 9 as third transmission are subjected
to an equally directed force transmission, i.e. each force transmission
from one gear to the next gear from the outside to the inside is present
in the same plane which is parallel to the planet carrier device 19.1 and
19.2, wherein only the transmission ratios determine the rotational
speed, the forces and the moment. An auxiliary unit drive according to
the invention directly coupled via a mechanical drive means, fed from the
main engine drive, has a force transmission in identical direction which
runs from the outside to the inside. The gear mechanism 2 according to
the invention in the transmission range of the ring gear 3, the annulus
segment arranged about the sun gear 9, is free of moment deflection. The
gear mechanism 2 according to the invention according to the FIGS. 4 to 7
can thus be realised with lower load, more stability over the long term,
with less wear in a wider spread range of the transmission ratio compared
with a gear mechanism 100 according to FIG. 8, which likewise is to be
formed below a ring, gear 3 with its running surface 21, than the
examples from the prior art cited above. In contrast with the previously
published approaches with one planetary gear 102 the special application
cases in the automotive auxiliary unit drive with transmissions from 2 to
approximately 5, 9 with mechanical coupling can now be realised in the
motor car ready for series production with a gear mechanism 1 or 2
[0076]According to an inventive aspect a planetary gear set according to
the invention consists of the three dominant main components of ring
gear, planet carrier and sun gear. The contours of all three elements can
be described in an abstract manner and fundamentally considered
geometrically as simple hollow cylinders. As is evident from FIGS. 7 and
8 the hollow cylinder elements can be produced free of pre-mounting
without, additional plates. The main components of ring gear 3, planet
carrier 19 and sun gear 3 are simple geometrical figures which (in the
mathematical sense) can be continuously (technologically practical) as a
turned part. They are round bodies, which need not be followed by any
termination surfaces. In contrast with this, moment-transmitting
ring-shaped plates have to, be additionally attached to the hollow
cylinders in the case of the gear mechanisms usual to date, since the
torque has to be directed about at least one gear element. As a result,
the space required by the planetary gear set according to the invention
both in axial as well as in radial direction is significantly less than
with the known gear mechanisms. The superficial disadvantage of using two
planetary gears instead of one is more than significantly compensated for
by these indirect measures. At the same time, the manufacturing methods
are drastically, simplified which is not least reflected also in the
[0077]Activation between the modes can, according to different exemplary
embodiments which are not shown, be demand-controlled or rotational
speed-controlled. The actuating system for the mode adjustment can be
connected to an electronic system such as an engine control unit with
suitable measuring sensors such as angular velocity measuring instrument,
revolution counter, power-measuring instrument. With the electronic
system a control for the gear mechanism can also be established according
to known methods. Valves can also control the auxiliary media such as air
or oil which serve the actuation system.
[0078]FIG. 9 shows a detail which in each of the exemplary embodiments
shown can be implemented as first planetary gear 5 or as second planetary
gear 7. During tests with planetary gear sets according to the invention
in the auxiliary unit train of motor vehicle engines at greater
percentage step-up times (e.g. 50% step-up component (i≠1) with an
air-conditioning compressor compared to 50% with (i=1) it has been shown
that the oil lubrication of the planetary gear set filled with gear oil
is substantial. The oil mist created in the gear mechanism is used to
lubricate the planetary gear bearings. To this end, one or a plurality of
slots 110, to be utilised as lubricating slots, are provided in a
planetary gear 105 which is used in place of the previously described
planetary gears 5,7. The respective slot 110 is limited in its length.
The slot 110 divides some teeth of the planetary gear 104. The slot 110
runs from a first tooth 106 to a second tooth 108, wherein both teeth
106, 108 need not be adjacent to each other. The slot 110 preferentially
is located in the middle of the width of the planetary gear 104. The
middle 112 of the slot 110 then almost or actually coincides with the
middle 114 of the gear 104. In order to be able to have the planetary
gear 104, which according to an exemplary embodiment rotates with
rotational, speeds between 10,000 and 40,000 revolutions/min.,
preferentially 20,000 revolutions/min., run unbalance-free, the slot 110
is attached in the gear 104 so that the recessed material does not create
any off-centre load. The gear 104 is unbalance-free, it is balanced in
terms of weight. Thus, according to an exemplary embodiment 2 or 3 slots
which are identical in type and which preferentially run at a middle
height in longitudinal direction and cut individual teeth are provided in
circumferential direction. In this case the centre of gravity 118 of the
planetary gear 104 coincides with the axis 116 of the planetary gear 104.
The centre of gravity 118 of the planetary gear 104 is in the middle in
the interior of the planetary gear 104.
[0079]Reference
1 Gear mechanism, more preferably according to a first
2 Gear mechanism, more preferably according to a second
5 Planetary gear, more preferably outer planetary gear
7 Planetary gear, more preferably inner planetary gear
11 Coupling device
11.1 Coupling part
11.2 Coupling part
11.3 Freewheel coupling
12 Shifting device
12.1 Braking element
12.2 Braking element
13 Coupling carrier
15 Torque support
19 Planet carrier device
19.1 First planet carrier, more preferably right planet carrier
19.2 Second planet carrier, more preferably left planet carrier
21 Running surface, more preferably belt running surface
vulcanised on
25 Ring gear internal toothing
27 Freewheel transmission element, more preferably
engagement element pressed on by spring
29 Insert seal
31 Planet carrier clamping screws
100 Gear mechanism, more preferably with single planetary
102 Planetary gear
104 Planetary gear
106 First limitation tooth
108 Second limitation tooth
110 Slot, more preferably lubricating slot
112 Middle of the slot
114 Middle of the gear
116 Axis gear
118 Centre of gravity gear
i Transmission or transmission ratio, more preferably ring
gear to sun, or operating mode
x Factor in connection with the transmission ratio
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