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WO2016090390A1 - Chaîne cinématique et procédé permettant de mettre en marche une chaîne cinématique - Google Patents

Chaîne cinématique et procédé permettant de mettre en marche une chaîne cinématique Download PDF

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Publication number
WO2016090390A1
WO2016090390A1 PCT/AT2015/000121 AT2015000121W WO2016090390A1 WO 2016090390 A1 WO2016090390 A1 WO 2016090390A1 AT 2015000121 W AT2015000121 W AT 2015000121W WO 2016090390 A1 WO2016090390 A1 WO 2016090390A1
Authority
WO
WIPO (PCT)
Prior art keywords
drive
differential
drive train
train according
gear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/AT2015/000121
Other languages
German (de)
English (en)
Inventor
Gerald Hehenberger
Miha ERJAVEC
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SET Sustainable Energy Technologies GmbH
Original Assignee
SET Sustainable Energy Technologies GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by SET Sustainable Energy Technologies GmbH filed Critical SET Sustainable Energy Technologies GmbH
Publication of WO2016090390A1 publication Critical patent/WO2016090390A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/724—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using externally powered electric machines
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
    • B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/028—Units comprising pumps and their driving means the driving means being a planetary gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/028—Units comprising pumps and their driving means the driving means being a planetary gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/721—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously the secondary drive being an energy dissipating device, e.g. regulating brake, in order to vary speed continuously
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/20—Structural association with auxiliary dynamo-electric machines, e.g. with electric starter motors or exciters
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • B60K2006/4825—Electric machine connected or connectable to gearbox input shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/40—Transmission of power
    • F05D2260/403—Transmission of power through the shape of the drive components
    • F05D2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
    • F05D2260/40311—Transmission of power through the shape of the drive components as in toothed gearing of the epicyclical, planetary or differential type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02P—CONTROL OR REGULATION OF ELECTRIC MOTORS, ELECTRIC GENERATORS OR DYNAMO-ELECTRIC CONVERTERS; CONTROLLING TRANSFORMERS, REACTORS OR CHOKE COILS
    • H02P5/00—Arrangements specially adapted for regulating or controlling the speed or torque of two or more electric motors
    • H02P5/74—Arrangements specially adapted for regulating or controlling the speed or torque of two or more electric motors controlling two or more AC dynamo-electric motors
    • H02P5/747—Arrangements specially adapted for regulating or controlling the speed or torque of two or more electric motors controlling two or more AC dynamo-electric motors mechanically coupled by gearing
    • H02P5/753—Differential gearing

Definitions

  • the invention relates to a drive train with a
  • Planetary gear with three input and output drives one output to the drive shaft, one drive to the prime mover and a second drive is connected to a differential drive.
  • the invention further relates to a method for starting a drive train with a drive shaft, a
  • Conveyors e.g. Pumps and compressors
  • Three-phase machines such as Asynchronous motors and synchronous motors with fixed speed.
  • Pole pair number of the drive machine defined. At e.g. Two-pole machines are therefore the synchronous speeds at approximate
  • Planetary gear stage with three input and output drives, wherein an output to the drive shaft of a work machine, a first drive to the prime mover and a second drive is connected to a differential drive.
  • Working machine can be operated at variable speed of the prime mover variable speed by the differential drive compensates for the speed difference.
  • the desired speed range is above the synchronous speed of the prime mover. This means that both the highest and the lowest speed point of the driven machines clearly above the
  • Synchronous speed (rated speed) of the prime mover is. In the case of a differential system, the speed depends on the
  • Output shaft from the synchronous speed of the drive machine and from the speed of the controllable shaft, which e.g. with the
  • Sun wheel is connected, starting from. With such a structure, however, it is difficult to control a super-synchronous speed, i. a
  • the object of the invention is therefore to find a transmission solution for a drive train, with which one can realize a differential stage and on the other hand a high speed on the drive shaft of a work machine without much effort on the one hand.
  • Another object of the invention is to facilitate the start-up of the prime mover.
  • Fig. 1 shows the principle of a differential system for a
  • Fig. 3 shows another embodiment of a differential system for a drive train according to the invention and for a method according to the invention for starting up a
  • Fig. 4 shows yet another embodiment of a
  • FIG. 1 shows the principle of a differential system for a drive train using the example of a pump. It is the
  • Planetary gear 3 executed differential gear 3 is driven by a prime mover 4.
  • the prime mover 4 is preferably a medium voltage three-phase machine connected to a network 12, which in the example shown due to the
  • Medium voltage three-phase machine is a medium voltage network is connected.
  • the selected voltage level depends on the application and v.a. the level of performance of
  • Planet carrier 7 is connected to the drive shaft 2, the prime mover 4 with a ring gear 8 and a sun gear 9 of the differential gear 3 with a differential drive 5.
  • the core of the differential system in this embodiment is thus a simple planetary gear with three inputs and outputs, with a Output with the drive shaft 2 of the work machine 1, a first drive to the drive unit 4 and a second drive to the differential drive 5 is connected.
  • a gear precursor 10 is between the
  • the gear precursor 10 may also be multi-stage, for example, or designed as a toothed belt, chain drive or planetary stage.
  • Transmission precursor 10 can also realize an axial offset for the working machine 1, and thus realize a coaxial arrangement of differential drive 5 and drive machine 4, which is a simple embodiment of the
  • the differential drive 5 is connected to the network 12 by means of a preferably low-voltage inverter 6, consisting of a motor-side and a grid-side inverter, and a transformer 11.
  • a preferably low-voltage inverter 6 consisting of a motor-side and a grid-side inverter, and a transformer 11.
  • Transformer 11 is similar to any existing ones
  • the main advantage of this concept is that the drive machine 4 directly, that is without consuming
  • Power electronics can be connected to the network 12.
  • the balance between the variable speed of the work machine 1 and the fixed speed of the network-connected drive machine 4 is determined by the variable-speed (controllable) differential drive 5
  • Torque differential drive torque drive shaft * y / x, where the size factor y / x is a measure of the
  • the power of the differential drive 5 is substantially proportional to the product of percent deviation of the pump speed of the basic speed x
  • Fig. 2 shows a differential system according to the invention, which allows a super-synchronous speed range without precursor.
  • a drive shaft 2 a prime mover 4 and a differential drive 5 for a differential gear 3, which by means of an inverter 6 (consisting of preferably motor Jeem and netz gloveem inverter - shown here simplified as a unit ) and one
  • Transformers 11 is connected to a network 12.
  • the inverter may be designed as a so-called 2Q system, whereby the differential drive 5 is then operated only by motor.
  • the drive shaft 2 is to be operated at a speed which is well above the synchronous speed of the prime mover 4, the drive shaft 2 with a sun gear 13 and the prime mover 4 with a ring gear 14 of a differential stage 15, with two or more Planet gears 16, connected.
  • This can be achieved in a simple way with a planetary gear stage and without gear precursor a translation between the prime mover 4 and working machine 1, for example, 2.5 to 6.5.
  • a stepped planetary set much higher ratios can be achieved beyond that.
  • Planet gears 16 each have two gears, which are rotatably connected to each other and different
  • Planet carrier 17 may, for example, in one or more parts be executed with non-rotatably interconnected components.
  • Differential drive 5 to implement.
  • a spur gear on for example, a spur gear on, but this, because of the high torque, very solid.
  • an additional separate planetary stage and / or an angular gear stage could be used.
  • Planet carrier 17 is required. This thus carries the two or more planet gears 16 of the main path (first planetary stage 15) and the planet gears 19 of the secondary path (second
  • the ring gear 20 of the sub-path is (directly or indirectly) connected to the transmission housing.
  • Differential drive 5 is coupled directly or indirectly to the sun gear 21 of the second planetary stage 15.
  • the ring gear 20 of the differential drive 5 can be driven variable speed.
  • the differential drive 5 is then directly or indirectly coupled to the ring gear 20.
  • the sun gear 21 is rotatably connected to the transmission housing.
  • the arrangement of the differential drive 5 is either coaxial with the sun gear 21 and ring gear 20, but may be offset in both cases and as shown in Fig. 2, via a matching gear 22.
  • the adjustment gear 22 is either coaxial with the sun gear 21 and ring gear 20, but may be offset in both cases and as shown in Fig. 2, via a matching gear 22.
  • the adjustment gear 22 is either coaxial with the sun gear 21 and ring gear 20, but may be offset in both cases and as shown in Fig. 2, via a matching gear 22.
  • the adjustment gear 22 is either coaxial with the sun gear 21 and ring gear 20, but may be offset in both cases and as shown in Fig. 2, via a matching gear 22.
  • the adjustment gear 22 is either coaxial with the sun gear 21 and ring gear 20, but may be offset in both cases and as shown in Fig. 2, via a matching gear 22.
  • the adjustment gear 22 is either coaxial with the sun gear 21 and ring gear 20, but may be offset in both cases and as shown in Fig. 2, via a matching gear 22.
  • the planet gears 16, 19 of both planetary stages 15, 18 can be mounted together on planet pins 23. In this variant, it follows that the axial distance of the planet wheels 16, 19 from the axis of rotation of the planet carrier 17 for both
  • the number can be as needed
  • the planet gears for the planetary stage 15 and / or 18 can also be designed as a stepped planet.
  • the planet gears 19 preferably offers a rolling bearing.
  • the planetary gears 16 are operated at a relatively high speed, which preferably offers a sliding bearing for this purpose.
  • the bearing of the planetary gears is to be selected according to the given technical conditions and not limited to the respectively preferred embodiment.
  • a helical gearing is required, for example for vibration or noise reasons, the following alternatives are available.
  • gears Disadvantage of an arrow toothing is an increased production and assembly costs. Instead of an arrow toothing, the gears can each consist of two gears and it can thereby subsequently, by selective choice of
  • the drive machine 1 operates in
  • a differential drive 5 for a pump as a work machine 1 has an output of about 15% of the total system power. That in turn means that with the
  • prime mover 4 can reduce the startup current, it also reduces the realizable startup torque.
  • Fig. 3 shows an embodiment according to the invention for a start-up method, which is characterized in that the drive machine 4 in a first step to a
  • Ring gear 20 is synchronized by means of a synchronization device 25 with the speed of the differential drive 5.
  • the synchronization device 25 is positioned in FIG. 3 between the sun gear 21 and the adaptation gear 22. However, it can also after the adjustment gear 22 and in multi-stage execution of a matching gear on an intermediate shaft of the
  • Adaptation gear 22 are attached. Thus, one can vary the specific torque and the specific speed for the synchronization device 25.
  • a corresponding matching gear can also be between
  • Synchronization device 25 apply analogously.
  • a Synchronization device 25 for example, if it is designed as a preferably oil-cooled multi-plate clutch, in a first step, for example, only flushed with oil and / or not or only
  • Synchronizer 25 a so-called drag torque (external braking torque), whereby the working machine 1 is set in slight rotational movement, wherein the
  • Differential drive 5 has to provide a counter-torque in the at least the same height. According to the constructive
  • Synchronization device 25 are preferably transmitted 2-20%, in particular 5 to 15%, of the transferable nominal torque.
  • the resulting advantage is that, by the working machine 1 is set in rotational motion, the maximum speed of the planet carrier 17 and thus the maximum on the bearing of the planet gears 16, 19 acting (and growing quadratically with the speed) centrifugal forces are reduced. With e.g. 5% of the rated torque as a drag torque can be achieved in the case of a pump about 25% of the rated speed of the working machine 1. This in turn means that the maximum centrifugal forces at the bearing of the planet wheels 16, 19 can be reduced by about 40%. In addition, the maximum rotational speed of the planetary gears 16, 19 that occurs during the startup process is reduced by about 25%.
  • the drag torque can also be selected to be higher, for example. 15-20%
  • a multi-plate clutch (also referred to as Reiblamellenkupplung) consists of at least one inner and one outer plate.
  • the inner plate (s) is (are) toothed with a shaft and the outer plate (s) is (are) of an internally toothed,
  • Actuating force can be transmitted through the larger surface area higher torques.
  • the characteristic feature of a multi-plate clutch compared to other clutches is the arrangement of several friction linings in series. The same contact pressure acts on all friction pairs. Multi-plate clutches are switchable under load. Most of these are in oil and running
  • the multi-plate clutch is designed as a so-called fail-safe clutch, then it is e.g. closed against spring pressure or oil pressure, etc.
  • the advantage is that it allows the system to be "fail-safe.” This means that in the event of a system failure (e.g., power failure, etc.), the clutch will automatically open, thus protecting the differential drive 5 from damaging overspeed, for example.
  • a viscous coupling or a retarder can also be used as the synchronization device 25.
  • a viscous coupling or a retarder preferably a locking device must be provided in order to synchronize the rotational movement of the
  • a visco-coupling is e.g. in the powertrain of
  • Used motor vehicles In principle, it transmits in its interior a rotary motion over a circular disk
  • Differential drive 5 the speed difference between this (taking into account a possibly existing matching gear 22) and the sun gear 21 (or ring gear 20) are controlled according to the desired torque to be transmitted.
  • Differential drive 5 can transmit slippage.
  • Fig. 4 shows an embodiment of the invention
  • Ring gear 20 freely with and it can build up no significant torque throughout the drive train.
  • the work machine 1 remains smaller in an area
  • Speed and the prime mover 4 can be synchronized with the network 12 without appreciable external counter-torque.
  • a star / delta circuit may be implemented or the prime mover 4 may be implemented by an auxiliary device - e.g. a small, preferably
  • Variable speed drive - brought to (nearly) synchronous speed and then synchronized with the network 12
  • the control speed range is the speed range in which the
  • Differential drive 5 operates to realize the working speed range of the working machine 1 can.
  • Control speed range is thereby v.a. determined by the voltage, current and speed limits specified by the manufacturer.
  • the differential drive 5 can not be connected to the network 12.
  • a synchronization brake 27 for example a
  • Differential drive-side part of the clutch 26 (preferably by means of differential drive 5) preferably synchronized with the speed of the second drive of the differential gear and then the clutch 26 is closed.
  • the coupling 26 is preferably a positive-locking dog clutch or a frictional multi-plate clutch.
  • non-positive multi-plate clutch is that, if it is designed for this, no synchronization of the two coupling halves is necessary.
  • Synchronization brake 27 on the one hand and the tilting torque of the engine 4 on the other hand is determined. That In contrast to the starting options according to the prior art, the multiple rated torque can be realized as a starting torque of zero speed away, since the typical overturning a
  • Three-phase machine is at about 2 to 3 times their rated torque.
  • a so-called synchronous brake 27 can also be used
  • Rotational movement is offset) can be applied.
  • this start-up method can also be used at e.g.
  • the clutch 26 and the synchronization brake 27 are positioned in FIG. 4 between the sun gear 21 and the adjustment gear 22. However, you can also after the adjustment gear 22 and in multi-stage design on an intermediate shaft of the
  • Adaptation gear 22 are attached.
  • the clutch 26 and the synchronization brake 27 also need not necessarily be positioned one behind the other and can be realized to realize the start-up procedure according to the design conditions freely between
  • Differential drive 5 and sun shaft 21 are positioned.
  • Differential drive 5 and ring gear 20 are attached.
  • Adaptation gear 22 protects against unauthorized overspeed.
  • Retarder hydraulic brake
  • Hydrodynamic retarders usually work with oil or water, which is directed into a converter housing if necessary.
  • the converter housing consists of two rotationally symmetrical and opposite
  • Paddle wheels and previously a rotor, which is connected to the driveline of the system, and a fixed stator.
  • the rotor accelerates the supplied oil and the centrifugal force pushes it outwards. Due to the shape of the rotor blades, the oil is conducted into the stator, which thereby induces a braking torque in the rotor and subsequently also brakes the entire drive train.
  • an electrodynamic retarder e.g. an eddy current brake
  • rotors e.g. two steel discs (rotors), which are not magnetized, connected to the drive train. In between lies the stator with electric coils.
  • When power is applied by activation of the retarder magnetic fields are generated which are closed by the rotors. The opposing magnetic fields then generate the braking effect.
  • the resulting heat is e.g. discharged through internally ventilated rotor discs again.
  • An essential advantage of a retarder as service brake is its freedom from wear and good controllability.
  • the drive train according to the invention (according to FIGS. 3 and 4) can also be used to drive the engine 4 in FIG.
  • Drive machine 4 can supply reactive power in or out of the network 12, without the work machine 1 is operated.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Power Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Structure Of Transmissions (AREA)

Abstract

L'invention concerne une chaîne cinématique, qui comporte un arbre primaire (2), un moteur d'entraînement (4) et un train épicycloïdal (3) doté de trois entrées ou sorties. Une sortie est reliée à l'arbre primaire (2), une entrée au moteur d'entraînement (4) et une seconde entrée à un entraînement différentiel (5). Le train épicycloïdal (3) comporte deux étages planétaires (15, 18). L'arbre primaire (2) est relié à la roue solaire (13) d'un étage planétaire (15), dont la couronne (14) est reliée au moteur d'entraînement (4). L'entraînement différentiel (5) est relié à la roue solaire (21) ou la couronne (20) de l'autre étage planétaire (18) et les porte-satellites (17) des deux étages planétaires (15, 18) sont reliés l'un à l'autre de manière solidaire en rotation.
PCT/AT2015/000121 2014-12-12 2015-09-17 Chaîne cinématique et procédé permettant de mettre en marche une chaîne cinématique Ceased WO2016090390A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ATA911/2014A AT516038B1 (de) 2014-12-12 2014-12-12 Antriebsstrang
ATA911/2014 2014-12-12

Publications (1)

Publication Number Publication Date
WO2016090390A1 true WO2016090390A1 (fr) 2016-06-16

Family

ID=54329338

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/AT2015/000121 Ceased WO2016090390A1 (fr) 2014-12-12 2015-09-17 Chaîne cinématique et procédé permettant de mettre en marche une chaîne cinématique

Country Status (2)

Country Link
AT (1) AT516038B1 (fr)
WO (1) WO2016090390A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT202000002695A1 (it) * 2020-02-11 2021-08-11 Ge Avio Srl Gruppo trasmissione ad ingranaggi provvisto di un motore elettrico
EP4282763A1 (fr) * 2022-05-26 2023-11-29 RTX Corporation Distribution sélective de puissance pour un système de propulsion d'aéronef
US12135076B1 (en) 2023-09-29 2024-11-05 Rtx Corporation Fluid device(s) for supporting rotating structure(s) of a turbine engine
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IT202000002695A1 (it) * 2020-02-11 2021-08-11 Ge Avio Srl Gruppo trasmissione ad ingranaggi provvisto di un motore elettrico
US11591971B2 (en) 2020-02-11 2023-02-28 Ge Avio S.R.L. Hybrid transmission on propeller gearbox
US12116939B2 (en) 2020-02-11 2024-10-15 Ge Avio S.R.L. Hybrid transmission on propeller gearbox
EP4282763A1 (fr) * 2022-05-26 2023-11-29 RTX Corporation Distribution sélective de puissance pour un système de propulsion d'aéronef
US11958624B2 (en) 2022-05-26 2024-04-16 Rtx Corporation Selective power distribution for an aircraft propulsion system
US12135076B1 (en) 2023-09-29 2024-11-05 Rtx Corporation Fluid device(s) for supporting rotating structure(s) of a turbine engine
US12188551B1 (en) 2023-09-29 2025-01-07 Rtx Corporation Reduced clearance interface between a fluid device and a rotating structure for a geartrain
US12292107B2 (en) 2023-09-29 2025-05-06 Rtx Corporation Fluid damper for turbine engine geartrain assembly
US12331683B2 (en) 2023-09-29 2025-06-17 Rtx Corporation Bearing arrangement for turbine engine geartrain

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