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    • 专利摘要:
    For starting a drive train with a drive shaft (2) of a working machine (1), with a drive machine (4) and with a differential gear (3) with three drives or drives (13, 14, 16), wherein an output (13) with the drive shaft (2), a first drive (14) with the drive machine (4) and a second drive (16) with a differential drive (5) is connectable, the drive machine (4) is approached by a speed of zero or approximately zero while the differential drive (5) is simultaneously connected to the first (14) and the second (16) drive.
    公开号:AT517170A1
    申请号:T643/2015
    申请日:2015-10-01
    公开日:2016-11-15
    发明作者:Gerald Dipl Ing Hehenberger；Markus Waldner；Miha Erjavec
    申请人:Set Sustainable Energy Tech Gmbh；
    IPC主号:
    专利说明:

    The invention relates to a drive train with the features of the preamble of claim 1.
    The invention further relates to a method for starting up a drive train with the features of the preamble of claim 23.
    A common problem of working machines, such as conveyors, e.g. Pumps, compressors and fans, or mills, crushers, vehicles, etc., are efficient, variable-speed operation, or start-up under load. In the following, electrical machines are used as examples of drive machines, but the principle applies to all possible types of drive machines, such as e.g. for internal combustion engines.
    The most commonly used electric drives today are three-phase machines, such as those described in US Pat. Asynchronous machines and synchronous machines, which are operated essentially only at constant speed.
    In addition, a three-phase machine and a downstream power supply must be designed to be large enough so that they can deliver a required drive torque from standstill away. For this reason, electrical machines are often designed in combination with a frequency converter as a variable-speed drive instead of being connected directly to a grid.
    This can indeed realize a variable-speed operation of zero speed without burdening the network heavily, but the solution is expensive and associated with significant loss of efficiency. A comparatively more cost-effective and also better in terms of efficiency alternative is the use of differential systems-for example, according to AT 507 394 A. The basic limitation here is that depending on the gear ratio of the differential stage, only a relatively small speed range and therefore in the so-called differential mode, i. at a speed change by means of the differential drive at operating speed of the drive machine, virtually no low speeds can be achieved on the drive shaft of a work machine.
    To realize this, there are different possibilities. According to DE 20 2012 101 708 U, for example, one can set the transmission ratio of the differential gear to 1. On this basis, one can drive the complete driveline with the differential drive or bring the prime mover to synchronous speed and then synchronize it with the network.
    Disadvantage of this solution is that the differential drive and its downstream frequency converter are dimensioned much smaller than the prime mover and therefore can only deliver a correspondingly small torque. This is not enough to accelerate the prime mover to the synchronous speed when the work machine is in operation.
    The AT 514 396 A shows a solution with which one can accelerate drive machines in a high-torque speed range and in a further step, the work machine can start from zero speed away. We solve this by the fact that the prime mover is approached by a speed of zero or approximately zero, while acting on the drive shaft, an external, braking torque, and that is braked in an acceleration phase of the drive shaft of the second drive. Disadvantage of this solution is that the necessary braking device is complex and with a differential drive in the size of about 20% of the total system power only a speed range of about 50% to 100% of the working speed can be realized.
    The object of the invention is therefore to find a solution with which it is possible to accelerate drive motors, preferably under load, for example by e.g. synchronized directly to a network, electrical machines to synchronize with the network, or can realize a large working speed range.
    Solves this problem with a drive train with the features of claim 1.
    This object is further achieved by a method having the features of claim 21.
    The core of a differential system is a differential gear, which may be a simple planetary gear stage with three inputs and outputs in a simple embodiment, wherein an output to the drive shaft of a work machine, a first drive with a prime mover and a second drive is connected to a differential drive , Thus, the machine can be operated variable speed at constant speed of the engine, the differential drive allows variable speed of the drive shaft.
    To operate a work machine from a standstill and, if the prime mover is an electric machine, to additionally bring a prime mover to synchronous speed from a standstill, operation of the system may be accomplished according to the invention e.g. take place in the following 3 phases:
    Phase 1: A differential drive is connected at standstill with both the first drive and the second drive of the differential system. Then the differential drive is accelerated and the machine starts to work. Depending on the torque characteristic of the driven machine and the power of the differential drive, a working speed range of up to about 50% of the rated working speed of the working machine is preferably realized in this operating mode I. The prime mover remains disconnected from the mains in this operating mode I. The gear ratios of the gear stages, via which the differential drive is connected to the two drives, are preferably selected so that the drive engine at least approximately reaches its operating speed as soon as the differential drive comes close to its power limit. The differential drive operates in this phase by motor - i. he draws energy from the network.
    Phase 2: The drive machine connected to the first drive of the differential system and now running in the operating speed range is now connected to the grid. Since the differential drive operates regeneratively in the lower working speed range of operating mode II -d.h. It supplies energy to the grid. In the next step, the torque of the differential drive is regulated from motor to generator mode. As a result, the prime mover is continuously loaded more and more, until the entire
    Differential system preferably comes within the range of the lower limit of the working speed range of the operating mode II.
    In order to keep the system loads as low as possible, preferably the transition from the motor to the regenerative operation of the differential drive is damped, i. not abrupt.
    Phase 3: As soon as an operating point in the lower operating speed range of the operating mode II has been set on the differential drive and on the drive machine with respect to speed and torque, the differential drive is disconnected from the first drive of the differential system. The system now operates in differential mode, allowing for maximum torque at maximum input speed for the work machine in this third phase.
    Preferred embodiments of the invention are subject of the dependent claims.
    Hereinafter, preferred embodiments of the invention will be explained with reference to the accompanying drawings. It shows:
    1 shows the principle of a differential system for driving a pump according to the prior art,
    Fig. 2 shows an embodiment of the invention
    Differential system for high-speed drives,
    2a is a diagram with a typical torque curve of a pump,
    3 shows a further embodiment according to the invention of a differential system for high-speed drives,
    4 shows a time profile of speed and performance parameters of a differential system during startup,
    Fig. 5 shows an embodiment of the invention
    Differential system for slow running drives,
    6 shows a further embodiment according to the invention, in which a differential drive can be connected to a second drive and an output of a differential system,
    Fig. 7 shows a further embodiment of the invention, in which a
    Output is connectable to a second drive of a differential system j,
    8 shows a further embodiment according to the invention, in which a differential drive can be connected via a second drive to a first drive of a differential system,
    9 shows an embodiment according to the invention of a differential system with a plus transmission,
    10 shows a further embodiment according to the invention of a differential system with a plus gear, and FIG. 11 shows a further embodiment of a differential gear according to the invention
    Differential system for an energy recovery plant.
    Fig. 1 shows the principle of a differential system for a drive train using the example of a pump. In this case, the working machine 1 is the symbolically represented rotor of a pump which is driven by a drive machine 4 via a drive shaft 2 and a differential gear 7 to 9. The prime mover 4 is preferably a medium-voltage three-phase machine, which is connected to a network 12, which in the example shown is a medium-voltage network due to a medium-voltage three-phase machine. The selected voltage level depends on the application and above all on the power level of the engine 4 and can have any desired voltage level without affecting the basic function of the system according to the invention. According to the number of pole pairs of the prime mover 4 results in a design-specific operating speed range. The operating speed range is that speed range in which the drive machine 4 can deliver a defined or desired or required torque, and in which the drive machine 4 are synchronized with the network 12 in the case of an electric drive machine, or started in the case of an internal combustion engine or can be operated. A planet carrier 7 of the differential gear is connected to the drive shaft 2, the drive machine 4 with a ring gear 8 and a sun gear 9 of the differential gear with a differential drive. 5
    The differential drive 5 is preferably a three-phase machine and in particular an asynchronous machine or a permanent magnet synchronous machine.
    Instead of the differential drive 5 and a hydrostatic adjusting gear can be used. In this case, the differential drive 5 is replaced by a hydrostatic pump / motor combination, which are connected to a pressure line and which both are preferably adjustable in the flow volume. Thus, as in the case of a variable speed, electric differential drive the speeds are adjustable.
    The core of the differential system is in this embodiment thus a simple planetary gear stage with three inputs and outputs, with an output to the drive shaft 2 of the work machine 1, a first drive to the prime mover 4 and a second drive to the differential drive 5 is connected.
    In order to be able to optimally adapt the speed range of the system, an adaptation gear 10 is implemented between the planet carrier 7 and the working machine 1. As an alternative to the spur gear shown, the adjustment gear 10, for example, be multi-stage or run as a toothed belt or chain drive and / or combined with a planetary gear or a bevel gear. With the adjustment gear 10 can also realize a misalignment for the working machine 1, which allows a coaxial arrangement of the differential drive 5 and the prime mover 4. Electrically, the differential drive 5 by means of preferably a low-voltage inverter 6 and, if necessary - a transformer 11 connected to the network 12. An essential advantage of this concept is that the drive machine 4 can be connected to the network 12 directly, that is to say without elaborate power electronics. The compensation between the variable rotor speed and the fixed speed of the network-connected drive machine 4 is realized by the variable-speed differential drive 5.
    The torque equation for the differential system is: Torque] 3-differential drive Torque output shaft * y / X,
    The size factor y / x is a measure of the gear ratios in the differential gear 3 and the adjustment gear 10. The torque at the drives and drives is proportional to each other, whereby the differential drive 5 can control the torque throughout the drive train. The power of the differential drive 5 is substantially proportional to the product of the percentage deviation of the speed of the work machine 1 from its basic speed x drive shaft power.
    The base speed is that speed which is set on the working machine 1 when the differential drive 5 has the speed equal to zero. Accordingly, a large working speed range of the working machine 1 basically requires a correspondingly large dimensioning of the differential drive 5. If the differential drive 5 has, for example, a nominal power of about 20% of the total system power (rated power of the working machine), this means taking advantage of a typical so-called field weakening range of the differential drive 5, that at the working machine 1 minimum working speeds of about 50% of the rated working speed can be realized. This is also the reason to see why differential systems according to the prior art are particularly well suited for small working speed ranges, but basically every working speed range can be realized. However, it can be stated that higher-pole three-phase machines usually allow higher overspeeds in relation to the synchronous speed by default, which in principle allows a (for the same nominal power of the differential drive 5) larger working speed range of the machine 1.
    In order to approach the differential system of a speed equal to zero, the differential drive 5 is separably connected by means of a clutch 25 with the sun gear 9. A synchronization brake 24 acts on the second drive of the differential system and thus on the sun gear 9 and thus on the entire drive train. When starting, in this embodiment of a differential system in a first step, the differential drive 5 is decoupled by the clutch 25 from the rest of the differential system. Now, if the prime mover 4 is started up and connected to the network 12, the sun gear 9 rotates freely and it can build up no significant torque throughout the drive train. Thus remains in this case, the
    Work machine 1 in a range of low speed and the prime mover 4 can be connected to the network 12 without significant external counter-torque.
    As soon as the prime mover 4 accelerates over a certain speed and the working machine 1 is substantially stationary, a high rotational speed corresponding to the transmission ratio of the differential gear sets in on the sun gear 9, which speed is usually above the permitted regulating rotational speed range of the differential drive 5. The control speed range is the speed range in which the differential drive 5 operates to realize the working speed range of the work machine 1 can. The control speed range is determined primarily by the voltage, current and speed limits specified by the manufacturer.
    The differential drive 5 can not be connected to the sun gear 9 in this embodiment in this phase. In a further step, the second drive of the differential system connected to the sun gear 9 is therefore decelerated to a speed which is within the control speed range of the differential drive 5 by means of synchronization brake 24. This can be done depending on the realized brake system 24 or the requirements of the drive train, both speed / torque-controlled and -ungeregelt. Subsequently, the differential-gear-side part of the clutch 25 is preferably synchronized by means of differential drive 5 with the speed of the second drive of the differential system and then the clutch 25 is closed.
    By actuation of the synchronization brake 24 (shown symbolically in FIG. 1 as a hydrodynamic brake) and thus deceleration of the second drive of the differential system, the drive shaft 2 is forcibly accelerated, the torque available for this purpose being determined by the minimum of the braking force acting on the drive shaft 2 Synchronization brake 24 on the one hand and the tilting torque of the engine 4 on the other hand is determined.
    Fig. 2 shows an embodiment according to the invention of a differential system, which is a supersynchronous
    Working speed range without adjustment gear allows. These
    Embodiment is preferably used in high-speed work machines. The drive train shown here also has, as in FIG. 1, a working machine 1, a drive shaft 2, a drive machine 4 and a differential drive 5, which are connected to the drives or drives of a differential gear 3. The differential drive 5 is connected by means of an inverter 6 (consisting of preferably motorseitigem and netzseitigem inverter - here simplified as a unit) and a transformer 11 to a network 12. The engine 4 is connected by means of a switch 23 to the network 12.
    Since in the example shown, the work machine 1 is operated at a speed which is well above the synchronous speed of the prime mover 4, the drive shaft 2 is connected to the sun gear 13 and the prime mover 4 by means of a connecting shaft 19 with the ring gear 14. The differential drive 5 is connected to the planet carrier 16 with two or more planetary gears 15. This can be achieved in a simple way with a planetary gear stage and without adjustment gear a translation between the engine 4 and machine 1 of, for example, 2.5 to 6.5. With, for example, a stepped planetary set, much higher ratios can be achieved beyond that. A stepped planetary set is characterized in that the planet gears 15 each have two gears, which are rotatably connected to each other and have different pitch circle diameter, wherein a gear with the sun gear and the second gear with the ring gear 'cooperates.
    As a working machine 1, a pump is shown symbolically in FIGS. 1 to 3, 5 and 8 to 10 by way of example. However, the principles described here and in the following figures are also applicable to drives for working machines, such as e.g. Compressors, fans and conveyor belts, mills, crushers, etc. or energy recovery plants and the like applicable.
    As a turbomachine, a pump has a quadratic torque curve, which is superimposed with construction-typical breakaway torques from the mounting of the drive train elements etc. during startup. As a result, when starting up, first a torque in the amount of e.g. 20% of the rated torque of the working machine 1 is overcome. With increasing speed then decreases the required drive torque (by eliminating the breakaway torque) and it turns according to the working speed of the machine 1 (approximately square) increasing torque, which reaches the rated torque at rated speed. The torque curve described is illustrated by way of example in a diagram in FIG. 2a.
    With a determined by the engine 4 speed of the ring gear 14 and an operationally required speed of the sun gear 13 inevitably results in a set speed or a torque to be set on the planet carrier 16, which are to be controlled by the differential drive 5.
    The planet carrier 16 may be embodied, for example, in one or more parts with components which are connected to one another in a rotationally fixed manner. Since the torque on the planet carrier 16 is high, it is advantageous, e.g. a translation stage 17, 18 between the planet carrier 16 and the differential drive 5 to implement. For this purpose, for example, a spur gear, wherein the gear 17 rotatably connected to the planet carrier 16 and the gear 18 is connected to the differential drive 5. Alternatively, the translation stage, for example, be multi-stage, or run as a toothed belt, chain drive, planetary stage or as an angle gear. Instead of the translation stage 17, 18, an optionally in stages or continuously variable transmission gear can be implemented.
    Fig. 2 shows a differential drive 5 with an inverter 6. Likewise, several differential drives can drive the planet carrier 16, whereby the torque to be transmitted of the translation stage 17, 18 is distributed to these differential drives. The differential drives can be distributed uniformly or asymmetrically over the circumference of the gear 17. Preferably - but not necessarily - the differential drives are controlled by a common inverter 6, in which case preferably a differential drive as a so-called "master" and the / the further (s) differential drive (e) act as a so-called "slave". The differential drives can also be controlled individually or in groups by several motor-side inverters, these so-called motor-side inverters connected to the differential drives preferably having a common, grid-side inverter connected to the grid 12 via transformer 11 via a DC link connected via DC link.
    If the system is equipped with a plurality of differential drives, then preferably only the first differential drive 5 will be connected via an auxiliary gear to the prime mover 4 - as shown in Fig. 2. In this case, drives at least a second differential drive via translation stage 17, 18 and planet carrier 16, the auxiliary gear 20 in addition to the first differential drive 5 at. Thus, only one auxiliary transmission 20 is required.
    With the connecting shaft 19 and subsequently with the prime mover 4 and the first drive of the differential system, an auxiliary transmission 20 is connected. This auxiliary transmission 20 is connected by means of a clutch 22 to the differential drive 5 and preferably also drives a lubricating oil pump 21. The clutch 22 is preferably designed as a dog clutch, gear coupling or multi-plate clutch. The prime mover 4 may also be connected to a transmission intermediate stage of the auxiliary transmission 20, wherein the connection of the auxiliary transmission 20 remains with the first drive.
    The differential drive 5 is connected via a clutch 25 separable with the translation stage 17, 18. To start the system, the differential drive 5 is connected by closing the clutch 25 with the gear stage 17, 18 and by closing the clutch 22 to the auxiliary gear 20. By then the differential drive 5 is raised, therefore, work machine 1 and the prime mover 4 accelerate simultaneously.
    If the prime mover 4 is designed as an asynchronous machine, then this is preferably brought to operating speed and then the
    Switch 23 is closed and the prime mover 4 connected to the network 12. This pulls, when it is connected to the network 12, only a short time a magnetizing current. Although this is higher than the rated current of the prime mover 4, but is only for a few grid periods and is well below the self-adjusting current that the prime mover would pull 4 when it is connected to the grid under load. Subsequently, the clutch 22 is opened and the differential system operates in the so-called differential mode.
    If the prime mover 4 is designed as a synchronous machine, then this can be synchronized with the network according to the recognized rules of the art and thus connected to the grid bumplessly. The differential drive 5 helps to synchronize the drive machine 4 with the network by this can regulate the speed and the phase angle of the drive machine 4 and synchronize with the network 12.
    If the prime mover 4 is an internal combustion engine, it can be started with the assistance of the differential drive 5.
    In the event of a malfunction (e.g., power failure), in the worst case, both the prime mover 4 and the work machine 1 would run out uncontrollably. In order to protect the operating in the differential mode differential drive 5 from overspeeding in such a case, you can either use a brake 26, which acts on the second drive of the differential system, or a brake 27, which acts directly on the differential drive 5. A better solution is also to open the clutch 25 and thereby separate the differential drive 5 from the rest of the differential system.
    In a further embodiment of the invention, it is also possible to use the brake 26 to brake the second drive of the differential system during the described start-up procedure in order to avoid a simultaneous start-up of the planet carrier 16. The clutch 22 remains closed and the clutch 25 is opened. So you can operate the machine 1 away from a working speed zero. The maximum achievable drive power for the
    Work machine 1, however, is limited according to the power capacity of the differential drive 5. However, since the operation e.g. a boiler water feed pump also operations with low speed (less than the achievable operating speed in the differential mode) and low power or maintenance-related commissioning includes, these can be realized by this embodiment.
    A similar result is achieved by braked with a brake the first drive (in the case of Fig. 2 by way of example with a brake 28 on the prime mover 4). The clutch 25 is closed in this application and the clutch 22 is opened. So you can drive the planetary carrier 16 and subsequently the work machine 1 at a stationary ring gear 14 with the differential drive 5.
    As shown in FIGS. 1 and 2, in a differential system, the first and second drives and the output may alternatively be connected to a ring gear or a planet carrier or a sun gear. In a further variant according to the invention, the differential drive 5 is connected to the ring gear 14, the drive machine 4 to the planet carrier 16 and the working machine 1 to the sun gear 13. Other alternative combinations are also covered by the invention.
    The configuration shown in Fig. 2 shows an embodiment with which you can easily and inexpensively high speeds on the working machine 1 realize. An exemplary configuration in which the work machine 1 is connected to the ring gear 14, the prime mover 4 to the sun gear 13 and the differential drive 5 to the planet carrier 16, is a possible variant for translations at low speed.
    Fig. 3 shows a further embodiment of a differential system according to the invention for high-speed drives. The differential system is basically the same structure as described in Fig. 2. In contrast to Fig. 2, the translation stage 29 is shown as Kegelradgetriebestufe. Thus, the axis of rotation of the differential drive 5 is arranged with an angular offset to the axis of rotation of drive machine 4 and machine 1. This results in that an auxiliary transmission 30 is to be executed as an angle gear. With the angular offset can be achieved that the center distance between the differential drive 5 and machine 1 is increased and thereby the work machine 1 can move closer to the differential system. Likewise, one can arrange the differential drive 5 mirror-inverted in the direction of the drive machine 4 (cf., Fig. 2 and Fig. 5) and thus the drive machine 4 zoom closer to the differential system.
    The auxiliary gear 30 as well as the auxiliary gear 20 is preferably designed so that (a) the direction of rotation of work machine 1 and drive machine 4 is opposite and (b) the prime mover 4 preferably reaches its operating speed as soon as the differential drive 5 comes within the range of its power limit.
    The auxiliary transmission 30 is connected by means of a clutch 31 to the differential drive 5 and preferably also drives a lubricating oil pump 21. The clutch 31 may be arbitrarily positioned in the path between differential drive 5 and connecting shaft 19, but is preferably arranged between lubricating oil pump 21 and differential drive 5 to ensure emergency operation of the lubricating system. If the differential drive 5 is arranged mirror-inverted in the direction of the drive machine 4, the first gearwheel of the auxiliary gearbox 30 preferably can be coupled to the connecting shaft between the differential drive 5 and the second drive of the differential system (compare FIGS. 2 and 5).
    The clutch 31 is preferably designed as a multi-plate clutch or as a hydrodynamic clutch / torque converter with additional / integrated locking function and can also be used as an emergency brake system by being closed as soon as a malfunction in the driveline occurs in the differential mode and the differential drive 5 from overspeed must be protected (see corresponding explanations to Fig. 2). Alternatively (or in addition), e.g. also a brake 27, which acts directly on the differential drive 5, and the clutch 31 is preferably used as e.g. simple claw coupling or gear coupling are executed. In principle, however, any type of coupling can be used according to the invention.
    In contrast to FIG. 2, however, in principle neither a clutch between the differential drive 5 and the second drive nor a brake which acts on the second drive are required here.
    The clutch 34 shown in Fig. 3 is used primarily as well as the clutches 32 and 33 for connecting the working machine 1, 4 engine and differential drive 5 with the transmission part of the differential system. If the use of a simple and inexpensive coupling 31 is preferred, it is recommended that the clutch 34, as already described with reference to FIG. 2, detachable during operation (possibly also with an automatic opening at overspeed) to the differential drive 5 in the case For example, to separate a malfunction of the second drive of the differential system. Thus, in principle, the brake 27 is no longer required. Alternatively, one can use instead of the clutch 34 or parallel to this a lockable freewheel between the differential drive 5 and second drive, which prevents an overspeed at the differential drive 5 in case of malfunction. This is possible because in the case of an error in the differential mode (operating mode II) the speeds of the working machine 1 and the prime mover 4 always go in the direction of "lowest working speed" and thus the required freewheeling direction is defined accordingly.
    The startup and operation of the differential system up to its nominal operating point take place in three phases, as will be explained with reference to FIG. These three phases are:
    Phase 1: The differential drive 5 is connected to the second drive of the differential system and is additionally connected by closing the clutch 31 by means of auxiliary gear 30 with the first drive (including connecting shaft 19 and drive machine 4) of the differential system. Subsequently, the differential drive 5 is accelerated and the work machine 1 begins to work. Depending on the torque characteristic of the working machine 1 and the power of the differential drive 5 is in this mode I preferably a continuously variable working speed from zero to, for example, about 50% of rated working speed of the working machine 1 can be realized.
    The prime mover 4 remains disconnected from the network in this mode of operation I.
    The gear ratios of the effective in this case gear 3, 29 and 30 are chosen so that the prime mover 4 reaches its operating speed as soon as the differential drive 5 comes close to its power limit. That the differential drive 5 is designed to be (a). overcome the inherent breakaway torques of a power train and (b) in operating mode I reaches a working speed which is in the range of the lower working speed achievable in the differential mode (operating mode II).
    Preferably, one allows, inter alia, in favor of a control hysteresis for phase 2, a more or less large overlap of the working speed ranges of the operating modes I and II. Will you interpret the differential drive 5 performance as small as possible, you can also a working speed gap between operating mode I and II provide. However, when switching over between operating modes I and II, it is necessary to accept torque and speed jumps, which are preferably controlled or even with dampers / and / or clutches and / or hydrodynamic torque converters with additional / integrated locking function - e.g. the clutch 31 can compensate. If a working speed gap exists between operating mode I and operating mode II, the differential drive 5, as described above, can not accelerate the drive machine 4 up to its operating speed. The prime mover 4 is then connected to the network 12 at a speed lower than its synchronous speed, which leads to corresponding power surges. However, these are lower than when the prime mover 4 is switched to the network 12 at a speed equal to zero. The differential drive 5 is separated in this phase from the auxiliary gear and "generates" a reaction torque on the second drive of the differential system.
    In any case, in this first phase (operating mode I) the differential drive 5 operates by motor - i. he draws energy from the network.
    Phase 2: As soon as the drive machine 4 has reached its operating speed, it is, as already described with reference to FIG. 2, synchronized with the network 12 and the switch 23 is closed.
    Since the differential drive 5 in the lower working speed range of the operating mode II operates as a generator -. he supplies energy into the network, in the next step the torque of the
    Differential drive 5 regulated by the required for the operating mode I motor in the required for the operating mode II generator operation. As a result, the prime mover 4 is continuously loaded more heavily until the differential system preferably comes in the lower region of the working speed range of the operating mode II.
    In order to keep the system loads as low as possible, preferably the transition from the motor to the regenerative operation of the differential drive is damped, i. not abrupt.
    Phase 3: Once the differential system has reached the operating point described in Phase 2 in the lower working speed range of the operating mode II, the differential drive 5 is separated from the first drive of the differential system by the clutch 31 is opened. The system now operates in operating mode II (= differential mode), whereby in this third phase for the working machine 1, a maximum torque at maximum input speed can be realized.
    To switch the differential system from operating mode II to operating mode I - e.g. in order to switch off the working machine 1 or for a lower delivery rate, the following procedure is preferably recommended:
    First, the lower portion of the working speed range of the operating mode II is controlled. After vorzugsweiser synchronization of the two coupling halves (by means of speed control of the differential drive 5). the clutch 31 is closed. As the next step, the torque of the differential drive 5 is controlled by the required for the operating mode II generator in the required for the operating mode I motor operation. As a result, the prime mover 4 is continuously relieved until it no longer supplies torque. By subsequently opening the switch 23, the prime mover 4 can be separated from the net 12 bumplessly. The differential system now operates in operating mode I and can thus be operated at zero working speed.
    FIG. 4 shows on a dimensionless time axis the progression of the torque and speed of the work machine 1, the drive machine 4, the differential drive 5 and the clutch 31 during the phases described above.
    Phase 1: At time TO the complete differential system is available. As soon as the differential drive 5 starts to rotate, the work machine 1 and the drive machine 4 accelerate until the latter reaches its operating speed - marked T 1 in FIG. 4. Between the time marks TO and Tl, the differential system operates in operating mode I.
    Phase 2: In the next step, the up to this time working without load drive machine 4 is synchronized with the network 12 and at time T2, the switch 23 is closed.
    Then, in the following step (between T2 and T3), the torque of the differential drive 5 is controlled by the motor in the generator mode (-> the torque of the differential drive 5 changes the direction). As a result, the prime mover 4 is continuously loaded more heavily (the torque of the engine 4 increases) until the differential system preferably reaches the lower range of the working speed range of the operating mode II. Due to the resulting new load distribution in the differential system, the torque originally flowing through the clutch 31 is controlled to zero and the clutch 31 is opened. At time T4, phase 2 is completed.
    The speeds for the input and output of the differential system in phase 2 preferably remain substantially constant, but may also vary due to operational requirements of the working machine 1. In this regard, an overlap of the operating speeds of the operating modes I and II is advantageous because it allows a between the times T3 and T4 acting on the clutch 31 torque with the differential drive 5 to zero control and the clutch 31 can solve load-free and thus bum-free for the differential system ,
    Phase 3: The differential system now operates between times T4 and T6 in operating mode II (= differential mode). The range between T4 and T5 shows a partial load range in which the system power is variably controlled until it remains between T5 and T6 in the rated power range with constant torque and constant speed. In the range between T4 and T5, the differential drive 5 changes from regenerative to engine operation, which becomes visible in its speed ("differential drive" speed.) The speed of the drive machine 4 ("drive machine" speed) remains in operating mode II in the case of a three-phase machine essentially constant.
    The temporal relations of the time axis can be designed individually and are based on the design criteria of the differential system or the operational requirements.
    Fig. 5 shows an embodiment of a differential system according to the invention for preferably slowly running drives. The principle is derived from the explanations to Fig. 1, 2 and 3 and can also be used for high-speed drives. The essential difference from the concept according to FIGS. 2 and 3 is that the differential drive 5 with the sun gear 9 as the second drive of the differential system (instead of the planet carrier 16 in FIGS. 2 and 3) and the working machine 1 with the planet carrier 7 (instead of the sun gear 13 in Fig. 2 and 3) is connected.
    By means of a clutch 31, the differential drive 5 can be connected to the auxiliary transmission 20 and preferably also drives a lubricating oil pump 21. The clutch 31 may be arbitrarily positioned in the path between differential drive 5 and connecting shaft 19, but is preferably arranged between lubricating oil pump 21 and differential drive 5 to ensure emergency operation of the lubricating system.
    6 shows a further embodiment according to the invention, in which a differential drive 5 can be connected to the second drive and the output of a differential system. In this embodiment, the differential drive 5 is connected on the one hand to the second drive of the differential system and on the other hand by means of a clutch 31 and via an auxiliary gear 61 to the output of
    Differential system or the drive shaft 2 connectable. Basically, the same applies as already described with reference to FIGS. 2 to 5, except that the differential drive 5 drives the drive machine 4 via the planet carrier 7 and the ring gear 8. An adaptation gear stage 60 is provided in FIG. 6 for optimizing the speed control range of the differential drive 5.
    Fig. 7 shows a further embodiment of the invention, in which the output is connectable to the first drive of a differential system. In this illustration, on the one hand, the differential drive 5 is connected to the second drive and on the other hand, the output of the differential system or the drive shaft 2 via an auxiliary gear 62 by means of coupling 63 to the first drive of the differential system or the prime mover 4 connectable. Basically, the same applies as already described with reference to FIGS. 2 to 6, except that the differential drive 5 drives the drive machine 4 via the output of the differential system or drive shaft 2.
    Fig. 8 shows a further embodiment of the invention, in which the differential drive 5 via the second drive, a transmission gear 36 and an auxiliary gear 42 to the first drive of the differential system is connectable.
    In the case of the use of the system according to the invention in an energy production plant, the drive machine 4 is an electric machine which operates essentially in generator mode. As a result, the power flow in the entire drive train rotates in comparison to the representations in FIGS. 1 to 8 or the description thereof. This affects u.a. also the reversal of the torque direction of the differential drive 5 between T2 and T3 described with reference to FIG. 4.
    Fig. 9 shows an embodiment according to the invention of the differential system with a so-called plus gear (also referred to as epicyclic gearbox). In this case, the drive shaft 19 of the first drive of the differential system with a first sun gear 44 and the working machine 1 with a second sun gear 45 is connected.
    A planet carrier 46 is equipped with two or more stepped planets 47, 48. Stepped planets are characterized in that the planet gears each have two gears 47,48, which are rotatably connected to each other and have different pitch circle diameter. In the illustrated embodiment of the invention, the gear 48 cooperates with the sun gear 44 and the gear 47 with the sun gear 45 together. The differential drive 5 drives the planet carrier 46 variable speed. To implement the operating mode I, the planetary carrier 46 can be connected via a transmission stage 49 and an auxiliary transmission 50 to the first drive of the differential system or the drive machine 4. The directions of rotation of the prime mover 4 and the working machine 1 are the same here and the translation stage 49 rotates in combination with the auxiliary gear 50, the direction of rotation relative to the planet carrier 46 to. The illustrated embodiment of a differential system in the form of a positive gear allows small ratios between the engine 4 and the machine 1 and is due to the lack of ring gears also inexpensive to manufacture.
    10 shows a further embodiment of the differential system according to the invention in the form of a positive gear. Basically, its function is derived from the comments on FIG. 9. In this embodiment, however, the auxiliary gear 52 is connectable to the transmission gear 51.
    As FIGS. 2 to 10 show by way of example, there are a multiplicity of possibilities according to the invention for realizing the function of the startup according to the invention. Basically, it is always about bridging the differential system, e.g. by means of an auxiliary transmission 20, 30, 50, 52, 53, 61, 62, so that the prime mover 4 reaches its operating speed as soon as the working machine 1 reaches a lower working speed in operating mode II. A more or less large overlap of the working speed ranges of
    Operating modes I and II or a working speed gap may be present as explained. According to the invention, however, the drive machine 4 and working machine 1 are raised in parallel in all embodiments by means of differential drive 5.
    11 shows a further embodiment of a differential system according to the invention for a power generation plant. In the case of the use of the system according to the invention in a
    Energy recovery system, the prime mover 42 is an electrical machine that operates essentially in generator mode (see also explanations to Fig. 8).
    The working machine 38 (for example the rotor of a wind turbine) drives the planet carrier of a differential stage 40 via the adaptation gear 39. The drive machine described in connection with FIGS. 1 to 11 is thus operated in the operating operating range as a generator 42. A connected via the inverter 6 and the transformer 11 to the network 12 differential drive 5 is connected by means of the shaft 35 (which is guided coaxially in a rotor shaft 43 of the generator 42) with the second drive of the differential gear 40. The differential drive 5 is connected by means of an auxiliary gear 53 and the clutch 54 with the rotor shaft 43 of the drive machine 42, wherein the planet carrier of the auxiliary gear 53 rotatably connected to the housing of the generator 42 and is integrated into this. The auxiliary gearbox 53 schematically illustrated as a planetary stage can also be replaced by one or more spur gear or bevel gear stage (s). This applies in particular if, according to AT 511 720 A, the differential system is designed with a plurality of differential drives connected via a spur gear stage. In principle, however, any type of gear or belt drives and the like can be used.
    If the differential system for a so-called pump turbine (working machine operates temporarily as a turbine and temporarily as a pump) can be realized with the system according to the invention, both a generator (turbine) and a motor (pump) operation, wherein continuously from one mode to another can be switched.
    In principle, the concept described here can also be expanded according to the functions and designs described in FIGS. 3 to 11.
    Instead of the differential drive 5, a hydrostatic adjusting gear can be used. In this case, the differential drive 5 and the inverter 6 are replaced by a two- or multi-part hydrostatic pump / motor combination, which are connected to a pressure line and both are preferably adjustable in the flow volume. Thus, as in the case of a variable speed electric differential drive, the speeds are adjustable. In this case, part of the pump / motor combination is preferably connected to the drive shaft 2, and / or by means of an electric drive at least temporarily connected to the network 12, and / or a part of the pump / motor combination is driven by another drive unit temporarily.
    This embodiment variant is analogously applicable even when using a hydrodynamic torque converter as a differential drive.
    The described differential system can also be integrated analogously in the adaptation gear 39 - for example, based on FIG. 5, but as already mentioned with a modified power flow.
    The system according to the invention can also be used to operate the prime mover 4 or the generator 42 in phase shifting operation. That is, the prime mover, either as a motor 4 or as a generator 42, can supply reactive power to and from the grid 12 without operating the work machine 1. In this case, the prime mover 4 or 42 is preferably synchronized and connected only by means of differential drive 5 with the network 12 and then the differential drive 5, preferably by opening the clutch 22, 25, 31, 54, 63 separated from the drive machine, without the further steps of the described Startup process to perform. This takes place only when the working machine 1 has to start operation.
    权利要求:
    Claims (40)
    [1]
    claims:
    1. drivetrain with a drive shaft (2) of a working machine (1, 38), with a prime mover (4, 42) and with a differential gear (3, 7 to 9, 40) with three inputs or outputs, with an output with the drive shaft (2), a first drive with the drive machine (4, 42) and a second drive with a differential drive (5) is connectable, characterized in that the differential drive (5) at the same time on the one hand with the first drive or the output and on the other the second drive is connectable.
    [2]
    2. Driveline according to claim 1, characterized in that the differential drive (5) with the first drive or the output is separable and permanently connected to the second drive.
    [3]
    3. Driveline according to claim 1 or 2, characterized in that the differential drive (5) is connectable simultaneously with the second drive and via the output to the first drive.
    [4]
    4. Driveline according to claim 1 or 2, characterized in that the differential drive (5) with the second drive and the second drive can be connected simultaneously with the first drive.
    [5]
    5. Driveline according to one of claims 1 to 4, characterized in that the differential drive (5) with the first drive and / or with the output via an auxiliary transmission (20, 30, 50, 52, 53, 61, 62) is connectable ,
    [6]
    6. Driveline according to one of claims 1 to 5, characterized in that the differential drive (5) with the first and / or second drive and / or the output via a coupling (22, 25, 31, 54, 63) is connectable.
    [7]
    7. drivetrain according to claim 6, characterized in that the coupling (22, 25, 31, 54, 63) is a dog clutch, toothed clutch or multi-plate clutch.
    [8]
    8. Driveline according to claim 6, characterized in that the coupling is a hydrodynamic coupling, optionally with an additional locking function.
    [9]
    9. Driveline according to one of claims 1 to 8, characterized in that the second drive with a brake (26) is connected.
    [10]
    10. Driveline according to one of claims 1 to 9, characterized in that the first drive with a brake (28) is connected.
    [11]
    11. Driveline according to one of claims 1 to 10, characterized in that the differential drive (5) is a three-phase machine, in particular an asynchronous machine or a permanent magnet synchronous machine is.
    [12]
    12. Driveline according to one of claims 1 to 10, characterized in that the differential drive (5) is a hydrostatic pump / motor combination.
    [13]
    13. Driveline according to one of claims 1 to 12, characterized in that the differential gear is a planetary gear.
    [14]
    14. Driveline according to one of claims 1 to 13, characterized in that the drive machine (4) with the ring gear (14), the differential drive (5) with the planet carrier (16) and the working machine (1) with the sun gear (13) connected is.
    [15]
    15. Driveline according to one of claims 1 to 13, characterized in that the drive machine with the planet carrier, the differential drive (5) with the ring gear (14) and the working machine with the sun gear (13) is connected.
    [16]
    16. Driveline according to one of claims 1 to 13, characterized in that the drive machine (4) with the ring gear (8), the differential drive (5) with the sun gear (9) and the working machine (1, 38) with the planet carrier ( 7) is connected.
    [17]
    17. Driveline according to one of claims 1 to 16, characterized in that two or more differential drives (5) are provided.
    [18]
    18. Driveline according to one of claims 1 to 17, characterized in that in the drive train between the differential drive (5) and the first drive, a lubricating oil pump (21) is arranged.
    [19]
    19. Driveline according to claim 18, characterized in that the coupling (22, 31), via which the differential drive (5) is connectable to the first drive, between the differential drive (5) and the lubricating oil pump (21) is arranged.
    [20]
    20. Driveline according to one of claims 1 to 19, characterized in that the working machine (1) is a pump, a compressor, fan, conveyor belt, crusher or a mill.
    [21]
    21. Driveline according to one of claims 1 to 19, characterized in that the working machine (38) is an energy production plant, in particular a wind turbine, hydropower plant or ocean current system, is.
    [22]
    22. Driveline according to one of claims 1 to 21, characterized in that the differential drive (5) is connected via a freewheel with the first or second drive.
    [23]
    23. A method for starting a drive train with a drive shaft (2) of a work machine (1, 38), with a drive machine (4, 42) and with a differential gear (3, 7 to 9, 40) with three drives or drives, wherein an output with the drive shaft (2), a first drive with the drive machine (4, 42) and a second drive with a differential drive (5) is connectable, characterized in that the drive machine (4, 42) of a speed of zero or approaching zero, while the differential drive (5) is simultaneously connected on the one hand to the first drive or the output and on the other hand to the second drive.
    [24]
    24. The method according to claim 23, characterized in that the drive machine (4, 42) is an electrical machine and is separated in this phase from the network (12).
    [25]
    25. The method of claim 23 or 24, characterized in that the differential drive (5) operates by motor and at the same time on the one hand drives the first drive or the output and the other drive.
    [26]
    26. The method according to any one of claims 23 to 25, characterized in that the working machine is accelerated in this phase to a speed range of up to about 50% of the nominal working speed of the working machine (1).
    [27]
    27. The method according to any one of claims 23 to 26, characterized in that the differential drive (5) operates as a generator and is driven by the second drive.
    [28]
    28. The method according to any one of claims 23 to 26, characterized in that the drive machine (4, 42) is then synchronized with a network (12) and connected.
    [29]
    29. The method according to claim 28, characterized in that by means of the differential drive (5), the rotational speed and in particular the phase angle of the electric machine (4, 42) with the network (12) is synchronized.
    [30]
    30. The method of claim 28 or 29, characterized in that the differential drive (5) after the synchronization of the drive machine (4, 42) from the motor to the generator mode changes.
    [31]
    31. The method of claim 28 or 29, characterized in that the differential drive (5) after the synchronization of the drive machine (4, 42) changes from regenerative to motor operation.
    [32]
    32. The method according to any one of claims 23 to 31, characterized in that subsequently the differential drive (5) is separated from the first drive.
    [33]
    33. The method according to claim 23, characterized in that the drive machine (4) is a Ve'rbrennungskraftmaschine and is started with the assistance of the differential drive (5).
    [34]
    34. Method according to claim 23, wherein the second drive is decelerated before it is connected to the differential drive.
    [35]
    35. The method according to any one of claims 23 to 34, characterized in that the second drive is braked or blocked while it is separated from the differential drive (5).
    [36]
    36. The method according to any one of claims 23 to 35, characterized in that the drive machine (4, 42) substantially reaches its operating speed as soon as the differential drive (5) comes within the range of its power limit.
    [37]
    37. The method according to any one of claims 23 to 36, characterized in that the drive machine (4, 42) operates in the phase-shifting mode after it has been synchronized by the differential drive (5) with the network (12).
    [38]
    38. The method according to any one of claims 23 to 37, characterized in that the first drive for operation of the working machine in the low speed range with a brake (28) is braked or blocked, while the differential drive (5) drives the second drive.
    [39]
    39. The method according to any one of claims 23 to 37, characterized in that the second drive is braked or blocked for operation of the working machine in the low speed range with a brake (26), while the differential drive (5) drives the first drive.
    [40]
    40. The method according to any one of claims 23 to 39, characterized in that the differential drive (5) is connected in the event of a malfunction with the first and second drive.
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