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`EXHIBIT Q
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`

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`(19) United States
`(12) Patent Application Publication (10) Pub. No.: US 2015/0091363 A1
`(43) Pub. Date:
`Apr. 2, 2015
`Reuter et al.
`
`US 20150.091363A1
`
`(54)
`
`(71)
`
`(72)
`
`DRIVING DEVICE IN A SELF-PROPELLED
`CONSTRUCTION MACHINE AND METHOD
`FOR SETTING ASPEED RATION SUCH A
`DRIVING DEVICE
`
`Applicant: BOMAG GmbH, Boppard (DE)
`
`Inventors: Marco Reuter, Emmelshausen (DE);
`Rafael Schomaker, Lingen (DE);
`Manfred Hammes, Emmelshausen (DE)
`
`(21)
`
`Appl. No.:
`
`14/388,512
`
`(22)
`
`PCT Fled:
`
`Mar. 8, 2013
`
`(86)
`
`PCT NO.:
`S371 (c)(1),
`(2) Date:
`
`PCT/EP2013/OOO686
`
`Sep. 26, 2014
`
`(30)
`Mar. 27, 2012
`
`Foreign Application Priority Data
`
`(DE) ...................... 10 2012 OO6 189.7
`
`Publication Classification
`
`(2006.01)
`(2006.01)
`(2006.01)
`(2006.01)
`(2006.01)
`
`(51) Int. Cl.
`B60K 25/06
`EOIC 23/2
`EOIC 23/088
`B60K 6/12
`B60K 6/36
`(52) U.S. Cl.
`CPC. B60K 25/06 (2013.01); B60K 6/12 (2013.01);
`B60K 6/36 (2013.01); E0 IC 23/088 (2013.01);
`EOIC 23/127 (2013.01); Y10S 903/915
`(2013.01)
`... 299/10; 74/11: 475/6: 299/39.4; 180/65.21;
`903/915
`
`USPC
`
`ABSTRACT
`(57)
`The present invention relates to a device in a self-propelled
`construction machine with a first driving unit, which provides
`for a first speed of rotation (n). By means of a planetary gear
`the first speed of rotation (n) is translated into a different
`speed of rotation (n) at which a working device of the con
`struction machine, in particular a milling rotor for processing
`ground Surfaces, can be operated.
`
`
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`3.43 & stak-sink
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`Patent Application Publication
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`Fig.4
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`US 201S/0091363 A1
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`s
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`s Y.
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`s ar six 2. as :
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`kx
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`w w
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`y
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`a tie yr
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`Patent Application Publication
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`17, n.
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`2O
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`18, n,
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`US 2015/009 1363 A1
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`Apr. 2, 2015
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`DRIVING DEVICE IN A SELF-PROPELLED
`CONSTRUCTION MACHINE AND METHOD
`FOR SETTING ASPEED RATO IN SUCHA
`DRIVING DEVICE
`
`CROSS-REFERENCE TO RELATED
`APPLICATIONS
`0001. This application is a submission under 35 U.S.C.
`S371 of International Application No. PCT/EP2013/000686,
`filed Mar. 8, 2013, which claims priority to German Applica
`tion No. 10 2012 006 189.7, filed Mar. 27, 2012, the disclo
`sures of which are hereby expressly incorporated by refer
`ence herein in their entireties.
`
`FIELD OF THE INVENTION
`0002 The present invention relates to a driving device in a
`self-propelled construction machine, more particularly, a
`construction machine for the treatment of ground Surfaces,
`comprising a first driving unit and a working device wherein
`a first drive train disposed between the first driving unit and
`the working device operates at a different speed of rotation.
`The present invention further relates to a method for effecting
`a change in the speed of rotation of the working device dis
`posed within the first drive train.
`
`BACKGROUND OF THE INVENTION
`0003. Examples of self-propelled construction machines
`are, in particular, rollers, refuse compactors, road milling
`machines, recyclers, ground stabilizers, and stationary and
`mobile crushers. Such construction machines comprise an
`internal combustion engine as the main drive, powering the
`traveling drive and the drives for the working device. Working
`device within the scope of the present invention should be
`understood to refer, in particular, to a working device having
`a large mass and, thus, a large inertia, the speed of which can
`only slowly be increased from the idling speed to the operat
`ing speed. Examples thereof are the traveling drives of the
`self-propelled construction machines and the milling rotors
`of the aforementioned construction machines. During road
`milling operations, construction machines comprising mill
`ing rotors typically alternate between the operational mode at
`a slow traveling speed and the maneuvering or transportation
`mode at an increased traveling speed. During the operational
`mode, the milling rotor is lowered to a working position and
`is run at operating speed.
`0004. The main drive and the drives of the working device,
`also referred to as secondary drives, usually operate at differ
`ent speeds of rotation. When working devices are connected,
`a defined procedure must therefore be regularly strictly
`adhered to, during which a predefined speed of rotation of the
`main drive must first be established before the connection can
`be made and the force flow restored. In the case of known
`construction machines, the gear system operates in slip mode
`during the coupling operation until the first driving unit and
`the milling rotor rotate at a synchronized speed of rotation.
`Depending on the difference in speed of rotation and the
`inertia of the drive train, the slip mode continues for a longer
`period of time and the wear therefore increases, resulting in a
`shortening of the lifespan of the components. Due to the
`predominant use of an internal combustion engine as the main
`drive unit with an output that is highly dependent on the speed
`of rotation, said engine does not operate within the optimal
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`range due to the alternation between the idling and operating
`speeds, resulting in increased fuel consumption.
`0005 Coupling of the milling rotor is generally not pos
`sible while the driving unit is switched off or while it is
`running at the operating speed. It is instead necessary to
`reduce the speed of rotation of the driving unit, usually down
`to the idling speed, for the purpose of making coupling pos
`sible. Afterwards, the operating speed must be restored. For
`the purpose of avoiding the time-consuming coupling process
`when changing from maneuvering mode to operational mode,
`the milling rotor is often allowed to continue to run at the
`same speed of rotation in the maneuvering mode as is used
`during the operational mode. Due to the fact that the direction
`of rotation of the wheels or tracks of the construction machine
`corresponds to that of the milling rotor while reversing, there
`is a risk of the construction machine accelerating uncontrol
`lably should the milling rotor unintentionally make contact
`with the ground. Such contact can be extremely hazardous
`and might also lead to damage to the milling rotor.
`0006. In the event of maintenance or installation work
`being carried out on the milling rotor of a milling machine, for
`example, when replacing milling chisels, it is necessary to
`move the milling rotor slowly and gradually at Small angular
`steps or continuously, in order to allow an operator free access
`to the entire cylinder jacket, even when the milling rotor is
`fitted inside the milling machine. The first driving unit is not
`suitable for this purpose when said unit is the main drive. In
`the prior art, the use of the main drive is also not permitted for
`this purpose for safety reasons. It must therefore always be
`Switched off. Such tasks are thus carried out using a second
`driving unit acting as a secondary drive. The known proce
`dure involving the connection of said secondary drive whilst
`simultaneously switching off the main drive has been found
`to be relatively complex.
`
`SUMMARY OF THE INVENTION
`0007. One aspect of the present invention is therefore to
`provide a device and method for effecting a change in the
`speed of rotation of the type described above, by means of
`which the speed of rotation of the working device can be
`readily adjusted.
`0008 According to one embodiment, there is provided a
`second drive train comprising a second driving unit between
`the second driving unit and the working device and in that the
`two drive trains are connected via a Summation transmission.
`0009. In one embodiment, a third speed of rotation is
`generated by the second driving unit and is Summate with the
`first speed of rotation, and that said working device is driven
`at said third speed of rotation.
`0010. The present invention has the advantage of enabling
`clutch-free starting, accelerating, and decelerating, as well as
`the operation of the working device at optimum speed of
`rotation without having to first decelerate the first driving unit
`from its optimum operating speed. The adjustment of the
`speed of rotation required to start the working device can be
`carried out solely by selecting the speed of rotation of the
`second driving unit. The first driving unit can therefore
`always operate at an optimum operating speed, thus reducing
`the energy consumption. The first driving unit is preferably an
`internal combustion engine that is able to determine, by
`means of operating characteristics, at which speed of rotation
`the internal combustion engine must operate in order to
`deliver a specified output at lowest possible fuel consump
`tion. The Summation transmission makes it possible to con
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`tinuously adjust the desired speed ratio between the first
`driving unit and the working device in a simple manner.
`0011. At the same time, the third speed of rotation can be
`adjusted to Suit the relevant usage of the working device so
`that the working device can operate as desired. In the case of
`the aforementioned construction machines, the traveling
`drive and/or the milling rotor, for example, can operate at a
`higher or lower second speed of rotation. Furthermore, in the
`case of milling machines, the milling power can be increased
`at a reduced traveling speed and the milling rate can be set by
`selecting the third speed of rotation so as to optimize the
`ground quality of the ground being processed, for example,
`during so-called fine milling. During maneuvering and
`reversing operations, the third speed of rotation can be
`reduced or even reset to Zero while maintaining the operating
`characteristics of the first driving unit. There is no need for
`time-consuming coupling operations and speed runs of the
`first driving unit, so that faster and cheaper processing of a
`work order is possible as compared with prior art construction
`machines.
`0012. An advantage of the present invention is further
`achieved for maintenance and installation work by use of a
`device and a method according to the present invention, in
`which the first drive train is disconnected and the second drive
`train is connected to the milling rotor. According to the
`present invention, connection to the secondary drive formed
`by the second driving unit can be established particularly
`easily by means of a Summation transmission. A particular
`advantage is achieved when the secondary drive is used both
`for maintenance and installation work as well as for the
`adjustment of the speed of rotation during traveling operation
`and when connecting the working device. In that case, all of
`the said functions can be carried out by means of just one
`second driving unit.
`0013 An advantageous further development of the device
`according to one embodiment of the present invention is
`characterized by the fact that the gear system comprises a
`planetary gear with the second driving unit engaging with the
`planetary gear. Planetary gears make for large scale-up or
`scale-down ratios in compact constructions. Since the second
`driving unit engages within the planetary gear, the compact
`construction form is maintained.
`0014. The present invention is further developed accord
`ing to one embodiment in that the planetary gear comprises a
`Sun wheel, a planetary carrier comprising a number of plan
`etary wheels, and a gear ring, the gear ring being mounted for
`rotation on a driving shaft, while the planetary carrier is
`non-rotatably connected to an output shaft, while the second
`driving unit engages the gear ring. To this end, the gear ring
`can comprise an outer intermeshing gear system as well as an
`inner intermeshing gear system which an output shaft of the
`second driving unit engages by means of an appropriate inter
`meshing gear system. Due to the gear ring being pivoted on
`the driving shaft of the gear system, it can rotate without
`slipping relatively to the first speed of rotation of the first
`driving unit and relatively to the second speed of rotation of
`the second driving unit. A torque converter is not required in
`this case, meaning that the constructive effort of the gear
`system can be kept to a minimum and the power output of the
`first driving unit can be better utilized.
`0015. In the event of the first driving unit being designed as
`an internal combustion engine, the engine can operate con
`stantly at an optimum speed of rotation for the purpose of
`achieving a predetermined power output at minimum fuel
`
`consumption. If the first driving unit operates at a mainly
`constant first speed of rotation in an optimum output range,
`the third speed of rotation and, thus, the speed of rotation of
`the working device can be selected fully variably and con
`tinuously, solely by controlling or regulating the second driv
`ing unit, and, thus, the speed ratio can be adjusted as desired.
`During the maneuvering phase, the working device can oper
`ate at a low third speed of rotation. As there is no interruption
`in the force flow between the first driving unit and the working
`device, there is no further requirement for a slip mode for the
`purpose of coupling the working device, which is concomi
`tant to a reduction in wear on the device components and an
`increase in their lifespan as compared with prior art devices.
`0016 A further development of the present invention is
`characterized in that the planetary gear comprises a Sun
`wheel, a planetary carrier comprising a number of planetary
`wheels, and a gear ring, in which the planetary carrier is
`mounted for rotation on a driving shaft and the gear ring is
`non-rotatably connected to an output shaft and that the second
`driving unit engages the planetary carrier. To this end, the
`planetary carrier can comprise an outer intermeshing gear
`system as well as an inner intermeshing gear system that is
`engaged by an output shaft of the second driving unit by
`means of an appropriate intermeshing gear System. Due to the
`fact that the planetary carrier is mounted for rotation on the
`driving shaft of the gear system, it can rotate without slipping
`depending on the first speed of rotation of the first driving unit
`and on the second speed of rotation of the second driving unit.
`Here again, there is no need for a torque converter. If the first
`driving unit operates at a mainly constant first speed of rota
`tion in an optimum output range, the third speed of rotation
`and, thus, the speed of rotation of the working device can be
`selected fully variably and continuously, solely by controlling
`or regulating the second driving unit.
`0017. The second driving unit is preferably designed in the
`form of a hydraulic engine. When used in construction
`machines, a hydraulic Supply is usually provided and, thus, no
`additional measures are required to operate the hydraulic
`engine.
`0018. According to a further embodiment, the hydraulic
`engine can operate by means of a hydraulic pump powered by
`the first driving unit, preferably by means of a transfer gear. In
`this embodiment, the hydraulic engine is powered indirectly
`by means of the first driving unit so that there is no need for a
`separate drive assembly for the hydraulic engine.
`0019. It is further advantageous when the second driving
`unit is directly powered by the first driving unit. This also
`makes for a reduction of the constructive effort for the provi
`sion of the second driving unit, as there is again no need for
`additional drive assemblies for the second driving unit of this
`embodiment.
`0020. The device according to one embodiment of the
`present invention is further developed in that the second driv
`ing unit is designed as an electric motor. Electric motors are
`characterized by their compact design and provide an output
`which is largely independent of the speed of rotation. Fur
`thermore, such motors can be easily controlled by means of
`an electronic control device and integrated in an existing
`control circuit or regulating circuit of a construction machine.
`0021. The first driving unit preferably drives a generator
`supplying the electric motor. There is therefore no need for a
`separate energy Supply for the electric motor, with the result
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`that there is a constant, Sufficient Supply of energy to the
`second driving unit as long as the first driving unit is in
`operation.
`0022. An advantageous embodiment of the present inven
`tion is characterized in that the first driving unit co-operates
`with a storage device for the purpose of storing energy. The
`storage device can take the form of an accumulator for storing
`electrical energy when the first driving unit powers a genera
`tor. Alternatively or additionally, the storage device may be in
`the form of a flywheel that directly stores the kinetic energy
`or, more particularly, the rotational energy of the first driving
`unit. If the second driving unit is at a standstill, the energy
`emitted by the first driving unit can be stored by the storage
`device also powering the second driving unit if so required.
`The first driving unit can thus be of smaller dimensions,
`resulting in reduced fuel consumption ("downsizing”).
`0023 The second driving unit preferably comprises a
`CVT transmission which can be driven by the first driving
`unit. This also indirectly powers the second driving unit via
`the first driving unit, wherein the CVT transmission offers the
`advantage of a continuous gear ratio with the result that the
`second speed of rotation can also be adjusted continuously by
`mechanical means.
`0024. The working device is preferably designed in the
`form of a milling rotor of a construction machine adapted for
`treatment of ground Surfaces. Milling rotors of construction
`machines usually have a large mass and, thus, large inertia,
`meaning that the device according to the present invention
`can be used to particular advantage in the case of construction
`machines. The reduction in fuel consumption as well as the
`continuous adjustability of the second speed of rotation at
`which the milling rotor is driven result in more economical,
`faster, and safer milling of road Surfaces compared with prior
`art construction machines.
`0025. An advantage of the present invention is also
`achieved by means of a construction machine for processing
`ground Surfaces comprising a device of one of the exemplary
`embodiments described above. The advantages and technical
`effects resulting herefrom correspond to those described
`above with reference to the device according to exemplary
`embodiments of the present invention.
`
`BRIEF DESCRIPTION OF THE DRAWINGS
`0026. The present invention is explained in detail below
`with reference to preferred exemplary embodiments shown in
`the figures, in which:
`0027 FIG. 1 is a self-propelled construction machine for
`processing the ground;
`0028 FIG. 2 is a detailed view of the device according to
`the present invention built into the construction machine
`shown in FIG. 1; and
`0029 FIG.3 to FIG. 15 each show an exemplary embodi
`ment of the device according to the present invention.
`0030. Like parts are identified in the figures by the same
`reference numerals.
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`DETAILED DESCRIPTION OF THE INVENTION
`0031
`FIG. 1 illustrates a construction machine 1 in the
`form of a road milling machine comprising a machine frame
`3 and wheels 4 adapted to process a traffic area 2. In the
`example shown, it comprises a working device 5 designed as
`a milling rotor 6. In the view shown in FIG.1, the milling rotor
`6 is in a descended working position. The direction of travel
`
`during the milling operation is identified by the arrow P. In
`this case the direction of rotation of the milling rotor 6 indi
`cated by the arrow P is contrary to the direction of rotation of
`the wheels 4 denoted by the arrow P.
`0032. According to FIG. 2, the construction machine 1
`comprises a driving device 26 for the milling rotor 6. It
`comprises a first driving unit 7 driving a belt transmission 9 at
`a first speed of rotation n via an output shaft 8. In this case,
`the first driving unit 7 is the powerful main drive of the
`construction machine 1 and is designed as an internal com
`bustion engine. A decoupling unit 12, a transfer gear 14, a
`resilient coupling 15, and a switchable clutch 16 are disposed
`on the output shaft 8 in that order between the first driving unit
`7 and the belt transmission 9. In addition to the milling rotor
`6, a number of other working devices (not shown) or imple
`ments of the construction machine 1 can be driven by the
`transfer gear 14, in this case designed as hydraulic variable
`displacement pumps 13.
`0033. The belt transmission 9 drives a first driving shaft 10
`for a gear 11 of the milling rotor 6 disposed within the milling
`rotor 6. In the example shown, the output shaft 8 and the first
`driving shaft 10 run at the same first speed of rotation n. The
`gear 11 is designed as a triple-shaft transmission comprising
`a second driving shaft 18 driven by a second driving unit 19 in
`the milling rotor 6 at a second speed of rotation n. The second
`driving unit 19 is designed as a secondary drive having a
`lower power output than the first driving unit 7. The gear 11
`drives the milling rotor by means of an output shaft 24 at a
`third speed of rotation n.
`0034 Starting from the first and the second driving unit 7.
`19 respectively, two drive trains are formed leading to the
`output shaft 24. The gear 11 is a Summation transmission
`connecting the two drive trains to the output shaft 24 and
`guiding these towards the milling rotor 6. The third speed of
`rotation in can be altered by changing the first and/or the
`second speed of rotation n by way of the Summation trans
`mission. The third speed of rotation n, in particular, can be
`altered by changing the second speed of rotation n indepen
`dently of the first speed of rotation n.
`0035 FIG. 3 shows a first exemplary embodiment of the
`driving device 26, in which the above described components
`between the first driving unit 7 and the belt transmission 9 are
`not shown for the sake of simplification. The belt transmis
`sion 9 is depicted by a cogwheel symbol and the transfer gear
`is depicted by a cogwheel 14. The gear 11 comprises a plan
`etary gear 25 comprising a Sun wheel 21, planetary wheels 22,
`and a first gear ring 20.
`0036. The second driving unit 19 is connected via the
`second driving shaft 18 to a cogwheel 17 engaging the plan
`etary gear 25. In this first example, the second driving unit 19
`is designed as a controllable hydraulic engine.
`0037 Via the transfer gear 14 and the belt transmission 9.
`the first driving unit 7 drives the driving shaft 10 comprising
`the sun wheel 21 at the first speed of rotation n. Said sun
`wheel engages the planetary wheels 22 mounted for rotation
`on a planetary carrier 23. The planetary carrier 23 is non
`rotatably connected to the output shaft 24 driving the milling
`rotor 6 (see FIGS. 1 and 2) at the third speed of rotation n.
`The first gear ring 20 is mounted for rotation on the driving
`shaft 10 and comprises an inner intermeshing gear system 28
`and an outer intermeshing gear System 29. The first gear ring
`20 engages the planetary wheels 22 via the inner intermesh
`ing gear system 28 whilst the second driving unit 19 engages
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`the outer intermeshing gear system 29 of the first gear ring 20
`by means of the cogwheel 17 at the second speed of rotation
`Il2.
`0038. The first drive train comprises the first driving unit 7.
`the transfer gear 14, the belt transmission 9, the sun wheel 21,
`the planetary wheels 22, and the planetary carrier 23. The
`second drive train comprises the second driving unit 19, the
`cogwheel 17, the first gear ring 20, the planetary wheels 22,
`and the planetary carrier 23.
`0039. During operation, the first driving unit 7 drives the
`driving shaft 10 at the first speed of rotation n, at which the
`sun wheel 21 also rotates. When the second driving unit 19 is
`at a standstill, the first gear ring 20 is also at a standstill, so that
`the planetary wheels 22 roll on the inner intermeshing gear
`system 28 of the first gear ring 20 and cause the planetary
`carrier 23 to rotate at the third speed of rotation n at a fixed
`ratio relative to the first speed of rotation n, as determined by
`the gear ratios of the gear 11.
`0040. In the event of the second driving unit 19 being
`operated at a second speed of rotation nz0, the first gear ring
`20 will rotate about the driving shaft 10. Accordingly, the
`planetary wheels 22 run at a different relative speed on the
`first gear ring 20 compared with the first gear ring 20 being at
`a standstill, resulting in a change in the third speed of rotation
`n of the output shaft 24. The third speed of rotation n may be
`increased or reduced depending on the direction of rotation
`and the second speed of rotation n of the second driving unit
`19. In this way it is even possible to reduce the third speed of
`rotation in to zero. In addition, the direction of rotation of the
`output shaft 24 can also be altered by way of the second
`driving unit 19.
`0041. When the first driving unit 7 is at a standstill, the
`second driving unit 19 determines the third speed of rotation
`Ils.
`0042. The second speed of rotation n of the second driv
`ing unit 19 can be controlled by a control device according to
`fixed algorithms, wherein a variety of programs can be pro
`vided for the various materials of the road surface 12 or for
`achieving the desired surface condition. Alternatively or addi
`tionally, the second speed of rotation n of the second driving
`unit 19 may also be regulated to Suit various aims. In this case,
`the third speed of rotation n is registered by means of a sensor
`(not shown) and compared with a setpoint value. If necessary,
`the second speed of rotation n of the second driving unit 19
`may be altered for the purpose of setting the setpoint value. In
`this way, it is possible to balance out any fluctuations in the
`first speed of rotation n, or in the third speed of rotation n.
`0043. In the event of the second driving unit being used to
`start the milling rotor 6 and/or to Support the milling opera
`tion, the performance ratio between the first driving unit 7 and
`the second driving unit 19 (P/P) is typically 10 or more.
`For example, P. can thus be 500 to 240 kW, the first speed of
`rotation n being, for example, 1800 min' and the third speed
`of rotation in 300 min'.
`0044) For the purpose of effecting installation and main
`tenance work on the milling rotor 6, the first driving unit 7 will
`be disconnected and the milling rotor 6 moved solely by
`means of the second driving unit 19. To this end, the second
`driving unit 7 must be designed such that the third speed of
`rotation in can be adjusted to such a low setting that the
`milling rotor 6 can be moved slowly without risk to an opera
`tor and stopped at short angular intervals.
`0045 FIG. 4 shows a second exemplary embodiment of
`the driving device 26. This comprises a planetary gear 25
`
`comprising the Sun wheel 21, the planetary wheels 22, and a
`second gear ring 31. Unlike the first exemplary embodiment,
`a second planetary carrier 30 is mounted for rotation on the
`driving shaft 10 in the second exemplary embodiment, and
`the second gear ring 31 is non-rotatably connected to the
`output shaft 24. The second gear ring 31 comprises an inner
`intermeshing gear system 28 engaging the planetary wheels
`22. The second driving unit 19 engages the second planetary
`carrier 30, which comprises an outer intermeshing gear sys
`tem 29 for this purpose, by means of the cogwheel 17.
`0046. In the present example, the first drive train com
`prises the first driving unit 7, the belt transmission 9, the sun
`wheel 21, the planetary wheels 22, and the second gear ring
`31. The second drive train comprises the second driving unit
`19, the cogwheel 17, the second planetary carrier 30, the
`planetary wheels 22, and the second gear ring 31.
`0047. The exemplary embodiments shown in FIG. 5, FIG.
`6, FIG. 7, and FIG. 8 each further illustrate examples for the
`propulsion of the second driving unit 19. In all other respects,
`the first and second drive trains each correspond to the drive
`trains of the first example illustrated in FIG. 3.
`0048 FIG. 5 shows a third exemplary embodiment of the
`driving device 26, wherein the second driving unit 19
`designed as a hydraulic engine is Supplied by one of the
`hydraulic pumps 13 via a hydraulic line 32. It is driven by a
`cogwheel 33 by way of the transfer gear 14. The first driving
`unit 7 thus also indirectly drives the second driving unit 19.
`0049. The input shaft 10 is designed as a hollow shaft in
`order that the hydraulic line 32 can be guided into the milling
`rOtOr.
`0050. In the fourth exemplary embodiment of the driving
`device 26 shown in FIG. 6, the first driving unit 7 directly
`drives a hydraulic pump 34 Supplying the second driving unit
`19, designed as a hydraulic engine, by way of the hydraulic
`line 32.
`0051 FIG. 7 shows a fifth exemplary embodiment of the
`driving device 26s that differs from the first exemplary
`embodiment shown in FIG. 3 in that the second driving unit
`19 is designed as an electric motor. A control unit 35 serves to
`control the speed of rotation and the power output.
`0.052
`FIG. 8 shows a sixth exemplary embodiment of the
`driving device 26, comprising a generator 36 in addition to
`the arrangement of the fifth exemplary embodiment as shown
`in FIG. 7. This serves to supply the second driving unit 19
`designed as an electric motor and is directly driven by the first
`driving unit 7. The electric motor and the generator 36 are
`interconnected via an electric line37. The generator 36 can be
`designed as a flywheel generator. In this case, the flywheel
`serves to store the kinetic energy provided by the first driving
`unit 7.
`0053. The input shaft 10 is designed as a hollow shaft for
`the purpose of guiding the electric conductor 37 into the
`milling rotor.
`0054 FIG. 9 shows a seventh exemplary embodiment of
`the driving device 26, which differs from the sixth exemplary
`embodiment shown in FIG. 8 in that an accumulator 38 is
`provided between the second driving unit 19' designed as an
`electric motor and the generator 36 for the purpose of storing
`the electric energy generated by the generator 36. In this
`variant too, the generator 36 may be designed as a flywheel
`generator.
`0055. In the eighth exemplary embodiment of the driving
`device 26s shown in FIG. 10, the second driving unit 19
`designed as an electric motor is Supplied solely by a separate
`
`Case 1:17-cv-00770-JDW-MPT Document 120-4 Filed 11/17/22 Page 14 of 1