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WO2019154772A1 - Dispositif d'entraînement et procédé pour limiter le régime - Google Patents

Dispositif d'entraînement et procédé pour limiter le régime Download PDF

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Publication number
WO2019154772A1
WO2019154772A1 PCT/EP2019/052695 EP2019052695W WO2019154772A1 WO 2019154772 A1 WO2019154772 A1 WO 2019154772A1 EP 2019052695 W EP2019052695 W EP 2019052695W WO 2019154772 A1 WO2019154772 A1 WO 2019154772A1
Authority
WO
WIPO (PCT)
Prior art keywords
retarder
oil
oil reservoir
drive
failure
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/EP2019/052695
Other languages
German (de)
English (en)
Inventor
Tobias Stolz
Peter Vogel
Tobias SEEBERGER
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.)
Voith Patent GmbH
Original Assignee
Voith Patent 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 Voith Patent GmbH filed Critical Voith Patent GmbH
Publication of WO2019154772A1 publication Critical patent/WO2019154772A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • F16H3/721—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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T1/00—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles
    • B60T1/02—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels
    • B60T1/08—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels using fluid or powdered medium
    • B60T1/087—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels using fluid or powdered medium in hydrodynamic, i.e. non-positive displacement, retarders
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T10/00—Control or regulation for continuous braking making use of fluid or powdered medium, e.g. for use when descending a long slope
    • B60T10/02—Control or regulation for continuous braking making use of fluid or powdered medium, e.g. for use when descending a long slope with hydrodynamic brake
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D57/00—Liquid-resistance brakes; Brakes using the internal friction of fluids or fluid-like media, e.g. powders
    • F16D57/04—Liquid-resistance brakes; Brakes using the internal friction of fluids or fluid-like media, e.g. powders with blades causing a directed flow, e.g. Föttinger 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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/10—Braking arrangements
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/12—Detecting malfunction or potential malfunction, e.g. fail safe ; Circumventing or fixing failures

Definitions

  • the invention relates to a drive device comprising a superposition gear, a main drive machine which is connected to an input shaft of the superposition gearing, one or more auxiliary drives, a hydrodynamic retarder for braking the auxiliary drive and an output shaft of the superposition gearing, which can be connected to a work machine; wherein the superposition gear comprises a planetary gear with a ring gear, a sun gear, a planet carrier and a plurality of planet gears, wherein the input shaft with the ring gear, the output shaft with the sun gear and the or the auxiliary drives are connected via at least one gear stage with constant translation with the planet carrier and wherein the retarder is connected to an auxiliary drive.
  • the invention relates to a method for speed limitation in case of failure or rapid shutdown of the main drive machine or an auxiliary drive to such a drive device.
  • a superposition gearbox In a superposition gearbox generally two shafts of the planetary gear are driven by mutually independent drives so that the rotational speeds on the third shaft, the output shaft, are added or subtracted. If one of the drives can be regulated, then a stepless speed control for the output shaft can be achieved.
  • Such drive devices are used in particular for driving pumps, compressors or compressors with high performance, as used for example in the oil and gas industry or in thermal power plants.
  • Such a drive device additionally equipped with a braking device which is connected to an auxiliary drive, is shown in DE 102014210868 A1.
  • a hydrodynamic retarder is also generally mentioned.
  • the braking device is provided therein solely for braking or stopping the output shaft.
  • auxiliary drive and the transmission can be damaged if the auxiliary drive fails during operation or must be disconnected from the mains. Such a failure can occur if a so-called blackout - a complete power failure - occurs or if faults on one of the drives or on one of the switchgear cause a shutdown. Since in the above-mentioned applications usually the inertia of the main drive machine is much larger than that of the driven machine, the speed of the machine will quickly go to zero even in case of failure or shutdown of the drive torque to the main drive machine. Due to the speed balance on the planetary gear is in this transmission variant of the Planet carrier and the auxiliary drive greatly accelerated.
  • the object is achieved by a drive device according to claim 1.
  • a drive device according to claim 1.
  • the device is equipped with an oil reservoir, which is designed so that during rapid shutdown or failure of the power supply of one of the drives, the retarder for activation with oil from this oil reservoir can be filled without an external power supply is needed.
  • the oil reservoir is designed so that the amount of oil is sufficient to slow down the planet carrier using the retarder can so that no harmful overspeed occurs.
  • the planet carrier does not necessarily have to be braked to a standstill.
  • two or more oil reservoirs may possibly be present.
  • the oil reservoir is arranged and connected to the retarder via oil lines, that the filling of the retarder is possible without additional power supply.
  • the oil reservoir can store the oil under increased pressure.
  • it is designed so that it can be put under pressure in the event of a power failure. The advantage of such a solution is that reliably - even in the accident described above - an overspeed on the planet carrier, the weakest link in the drive device can be avoided.
  • the retarder can have a parabolic braking behavior due to the hydrodynamic action, that is, that the braking torque is high at high differential speed and then decreases, the more the auxiliary drive is braked. As a result, the auxiliary drive is not unnecessarily slowed down, but only as far as the risk of overspeed is no longer given.
  • the brake is also wear-free and therefore very easy to maintain.
  • the retarder can be used well in potentially explosive atmospheres. In contrast to friction brakes, the retarder performs the heat energy generated during braking reliably and in a controlled manner via the oil. Explosion protection requirements are mainly present in the market area oil and gas. This system can be braked reliably even with the developed solution even if the drive with its winding temperature has exceeded the permissible temperature threshold value and no deceleration via the frequency converter is possible.
  • the arrangement is well suited for high speeds at the output, as they are required for example in high-speed compressors or large fans, because thereby the space and the weight of the drive device can be kept relatively low.
  • the inventive embodiment when the main drive machine is only constant speed operable and the one or more auxiliary drives are operated speed controlled and in particular the one or more auxiliary drives are designed as low-voltage motors.
  • Much of the drive power can be applied by the constantly operating main drive machine. This does not require a frequency converter, which saves investment costs.
  • the main drive machine is designed as a medium-voltage motor, ie with a voltage of more than 1 kV.
  • the speed control is via the auxiliary drives, which require a lower power and which are preferably designed as low-voltage motors with a voltage of less than 1 kV.
  • the required frequency converters are smaller and less expensive.
  • a gear stage is understood to mean a drive connection which transmits power and torque with a constant gear ratio, ie a fixed speed ratio.
  • the inflow of oil can be controlled via a throttle in the supply line between the oil reservoir and the retarder.
  • the time course of the braking behavior can be influenced.
  • the necessary heat dissipation from the retarder can be ensured in case of failure.
  • a cooling circuit for the oil in the retarder may be present, in particular, the cooling of the lubricating oil circuit of the drive device may be used.
  • the oil reservoir can be placed under increased pressure in order to build up sufficient pressure to fill the retarder in case of energy failure.
  • the pressure may, for example, permanently abut the oil reservoir and be generated for example by a separate pump, in particular by a Flochtikpumpe, or by a spring preload or by gas pressure or by the system pressure from a lubricating oil system for the drive device.
  • the variants for pressure generation can also be combined.
  • the gas pressure can also be generated by a compressed air system or by a propellant charge, which gives only in case of failure increased pressure on the oil reservoir.
  • the oil reservoir can be designed as a piston accumulator.
  • the piston accumulator can be designed on one side or with a pressurized on both sides with oil, sealing piston as a media separator.
  • the oil reservoir can be designed as a bladder accumulator with an elastomer bladder or as a membrane reservoir with an elastomer membrane.
  • the oil reservoir may alternatively or additionally be arranged at a higher level and thus provide pressure for filling the retarder by the geodetic height without the need for a power supply. He is then trained as a so-called high tank.
  • the oil reservoir is filled with a separate pump or with the help of system pressure from a lubricating oil system.
  • oil is to be understood as meaning a fluid which is suitable for producing the necessary braking torque in the retarder. This may be a coolant or water.
  • a separate pump for filling the oil reservoir is provided, which is mechanically connected to a shaft of the planetary gear, and thus activated during operation of the drive device.
  • it can be powered by a motor and with the help of an uninterruptible power supply.
  • the drive device is designed so that the oil reservoir can be filled with oil from a lubricating oil system for the drive device and that the retarder can be filled exclusively with oil from the oil reservoir. This makes the execution easier and requires no additional oil supply.
  • the retarder is arranged outside the gearing housing of the superposition gearing.
  • the retarder is connected to the auxiliary drive such that it has the same speed as the auxiliary drive.
  • auxiliary drive usually has a higher speed as the planet carrier and the retarder has a better braking effect at high speed. This allows for greater deceleration, or a smaller retarder can be used than when the retarder is installed at a lower speed location.
  • At least one valve in particular a directional control valve, is provided between the oil reservoir and the retarder, which has two switch positions, a first in which the retarder is separated from the oil reservoir and a second, in which the oil reservoir is connected to the retarder. If there is pressure from the reservoir side at this valve, oil can flow from the reservoir to the retarder when switching to the second position and fill it.
  • valve is designed so that it is in normal operation in the first switching position and goes in case of failure or interruption of the power supply in the second switching position. This means that the valve is closed in normal operation and goes in the event of a fault in the open position.
  • a sensor is provided on the oil reservoir, which monitors the level and / or the pressure in the oil reservoir. If the fill level and / or the pressure is insufficient, a warning can be output or, for example, it can be prevented that the drive device can be approached or the drive device can be shut down automatically. This offers a higher reliability of the drive device.
  • the drive device is designed so that of the three speeds: that of the main drive machine, the output shaft and the auxiliary drive at least two speeds can be detected or measured, in particular by means of pulse generator on the drive and / or speed sensors.
  • the third of the speeds can be determined, even if they are not measured becomes.
  • errors can be detected early, and can respond to incidents quickly or even anticipatory.
  • a bypass line (36) on the retarder (12) is also provided, which is designed such that it leads oil from the exit of the retarder back to the inlet to the retarder, and has an adjustable throttling possibility
  • the retarder is designed so that the oil from the retarder can be discharged into an oil sump, in particular a throttle between retarder and oil sump is present. so that the oil drain can be set.
  • the braking behavior and the heat dissipation from the retarder can be designed controlled.
  • the object is achieved by an embodiment according to claim 13 - using a device according to the invention. Further advantageous features of the method according to the invention, which further improve this, can be found in the following subclaims for the method.
  • the inventive method has the advantage that - regardless of the power supply - a reliable braking and avoiding overspeed of the auxiliary drives, the planet carrier or other system components is possible.
  • the retarder works wear-free and it is also suitable for explosion protection.
  • the braking of the drive device does not necessarily have to be stopped.
  • an emergency operation at reduced speed can be made possible with the retarder.
  • the auxiliary drives of the retarder can muster the necessary supporting moment to decelerate the still in operation main drive machine so that a lower load point can be maintained with the drive device.
  • the detection of a failure or an emergency shutdown is included, for example, via the drive control and / or signals from the power supply, in particular in case of failure of the supply network or triggering safety devices or emergency stop Facilities, done.
  • fault or fault messages can be used.
  • a speed measurement is preferably provided on the planet carrier or on one or more auxiliary drives.
  • the measurement can be carried out via speed sensors at a suitable point or via pulse generators on the drives.
  • the triggering of the deceleration process occurs when a certain speed limit is reached or exceeded. This speed limit is specified by the permissible maximum mechanical limit speed. io
  • auxiliary drives it is advantageous if an impending failure of the auxiliary drives can already be detected before entry.
  • upper temperature limits for the winding temperature and / or for the storage temperature of one or more drives can be monitored by one or more temperature sensors.
  • current acceleration values from the measured or determined rotational speeds can additionally be used to detect a failure or imminent failure.
  • a failure can be detected and the method according to the invention for speed limitation can be carried out.
  • Fig.3b Exemplary speed curve without unwanted overspeed after a failure
  • the superposition gear 17 has a housing 9 and comprises a planetary gear 18.
  • the input shaft 14 connects the main drive machine 2 with the ring gear 4 of the planetary gear and the output shaft 15 connects the sun gear 7 with the work machine 1.
  • the third wave of the superposition gear is through the auxiliary drive shafts 16.1 and 16.2 formed. These connect via the gear stage 6.1 a / b and 6.2a / b, the auxiliary drives 3.1 and 3.2 with the planet carrier 10.
  • the planet carrier 10 contributes to a planetary gears 5 on the planet pins and on the other hand it is formed with external teeth as a gear that with the respective gears 8.1, 8.2 meshes and forms a further gear stage.
  • the gears 8.1 and 6.1 b and 8.2 and 6.2b are preferably formed as a so-called step wheel.
  • the gear on the planet carrier 10 may also be joined, it does not necessarily have to be formed in one piece from the planet carrier.
  • the preferred variant for the gear stage is shown in the form of a spur gear.
  • this version is equipped with two auxiliary drives 3.1 and 3.2; However, the invention can also be implemented with only one auxiliary drive or with several, for example three auxiliary drives. It is important that the auxiliary drives via at least one gear stage 6.1 a / b, 6.2a / b, 8.1, 8.2 are coupled with constant translation with the planet carrier 10.
  • the auxiliary drives 3.1, 3.2 are designed as controllable motors with lower power and the main drive machine 2 as a motor with higher power but constant speed.
  • the auxiliary drives can be designed as low-voltage motors, since they often only have about 10 to 30% of the total drive power.
  • the main propulsion engine 2 is designed as a medium voltage motor in many applications to provide the total power required, and can be executed without control.
  • Such drive devices are particularly interesting at high powers of several MW, such as occur in high-speed pumps, compressors or fans in the oil and gas industry or in thermal power plants.
  • the speed at the output shaft 15 can be increased or decreased by a certain proportion.
  • the limits of this range at maximum speed of the auxiliary drives 3.1, 3.2 once in positive and once in negative direction specify the possible control range.
  • auxiliary drives 3.1, 3.2 and especially the planet gears 5 and their bolts can be damaged.
  • a safe design of the planetary gear 18 for this particular accident would make the drive device unnecessarily large and expensive.
  • the auxiliary drives 3.1, 3.2 and the planet carrier 10 can be reliably braked in case of failure. This prevents an unacceptable overspeed.
  • the oil reservoir 13 is under elevated pressure or the oil reservoir 13 is pressurized in case of failure to fill the retarder 12 independently of an external power supply via a line 35.
  • the oil for the oil reservoir 13 is preferably obtained from a lubricating oil system 40 of the drive device via a filling line 31.
  • the braking does not necessarily have to be stopped. It can be maintained at reduced speed in some cases, an emergency operation, for example, when the auxiliary drives 3.1, 3.2 fail and the main drive machine 2 is still in operation.
  • the retarder 12 brings the necessary support torque to brake the main drive machine 2, and so according to speed / torque characteristics of the retarder 12 to be able to hold a lower load point.
  • the oil supply of the retarder 12 must be designed for emergency operation.
  • speed sensors 20, 21, 22 may be provided on the drives 2, 3.1, 3.2. These can be formed for example by the pulse generator of the motors. Alternatively or additionally, a speed sensor on the gear of the gear stage 6.1 a / b, 6.2a / b, a speed sensor on the gear of the planet carrier 10 or a speed sensor on the output shaft 15 may be present. Thus, variants are given, with which all speeds n1, n2, n3 and that of the planet carrier can be measured. Ultimately, however, it is sufficient if two of these speeds are measured, because the other speeds can then be determined by the speed equation of the planetary gear 18 and the translations. Thus, not all the speed sensors mentioned are necessary at the same time.
  • the determination of the speeds and in particular the knowledge of their course in case of failure offer the advantage that it can be determined as the Brake characteristic and the braking process must be designed. These can be influenced by controlling the filling of the retarders 12.
  • the drive device represents an overall system with the drive device according to the invention, with the work machine 1 and the connection to the power supply network 50.
  • the drive device comprises a superposition gear 17 with input shaft 14 and output shaft 15, a main drive 2 and two auxiliary drives 3.1, 3.2.
  • the main drive 2 is connected via a switching device 54 to the power supply network 50 and we operated at a constant speed.
  • the auxiliary drives 3.1, 3.2 are via an inverter 52, 53 and a corresponding
  • Power supply unit 51 connected to the network 50.
  • the auxiliary drives can be operated variable speed.
  • Fig.3a the case for a drive device according to the prior art is shown.
  • the speed n1 of the machine falls very quickly to zero due to the low moment of inertia.
  • the speed n2 of the main drive machine is slowing down.
  • the speed n3 of the auxiliary drives increases sharply after the fault.
  • the planet carrier and coupled with him mechanical elements which are coupled to the auxiliary drives 3.1, 3.2, strongly and in many cases accelerated to impermissibly high speeds. This can cause damage especially to the planet pins and other system components.
  • the auxiliary drives can be accelerated beyond their permissible mechanical limit speed, resulting in damage.
  • FIG. 3 b shows exemplary rotational speed curves as can be achieved with a drive device according to the invention and a method according to the invention. Due to the advantageous embodiment with retarder and energy-independent filling of the retarder from an oil reservoir, the acceleration of the auxiliary drives can be avoided. The speed n3 decreases due to the braking effect of the retarder after the accident. At the same time, the work machine is decelerated faster due to the coupling in the planetary gear, which can represent a further advantage. It can also be seen that the braking effect is initially stronger and then decreases at reduced speed. The characteristic of the course of n3 can be adjusted via the filling control, for example with throttles in the supply line to the retarder or in the discharge line from the retarder into the oil sump.
  • the oil reservoir 13 is designed as a pressure accumulator.
  • the oil reservoir 13 is filled via the filling line 31 from the lubricating oil system 40 of the drive device.
  • the pressure for filling and thus also for storage in the oil reservoir 13 is built up exclusively via the lubricating oil pump 41 in the lubricating oil circuit.
  • a throttle and a check valve may be provided in the filling line 31.
  • the connection to the lubricating oil system 40 may be arranged before or after a lubricating oil heat exchanger 42 or a lubricating oil filter 43.
  • a branching lubricating oil line 30 is present to the retarder, this may also have a throttle.
  • the lubrication of the retarder 12 is ensured with the illustrated wiring regardless of the operation of the retarder.
  • the lubricating oil pipe 30 may additionally or alternatively, if no lubrication is necessary, for example, because of foreign storage, serve to lead in normal operation, so always without braking some oil through the retarder 12. So, heat that comes from the no-load losses, reliably dissipated. And it is reduced by this small amount of oil, the idle loss.
  • the oil reservoir 13 is preferably equipped with a level and / or pressure sensor 23. If the level or pressure is insufficient at the beginning of the operation, it may be possible to prevent the system from starting or to issue a warning.
  • the activation of the retarder 12 takes place in case of failure via the opening of the valve 19.1.
  • the retarder 12 is filled with oil as soon as the valve 19.1 releases the passage.
  • the valve 19. 1 can be designed as a 0/1 valve or as a 2/2-way valve, as shown here.
  • the temperature development in the retarder and the braking time can be influenced via the adjustable throttle located in the discharge line 32 and the additionally throttleable bypass line 36. As long as the temperature development is not too high, oil can be passed through the throttling bypass line 36 from the outlet back to the inlet to the retarder. Thus, the existing amount of oil from the oil reservoir 13 can be exploited even better in terms of its thermal capacity. To avoid unwanted heating, a portion of the oil can be discharged via the throttling drain line 32 into the oil sump 34. On the discharge line 32, the retarder 12 can also be emptied when no more braking is desired.
  • the control of the valve 19.1 can be done electrically, pneumatically or hydraulically.
  • the valve 19.1 is designed so that the rest position without power supply - as shown here as position 1 - is the position to release the passage. This can be achieved for example via a spring action. This always ensures that the retarder 12 is filled in the event of a fault.
  • position 2 of the Valve 19.1 the oil reservoir 13 is filled until the pressure in the oil reservoir 13 corresponds to the system pressure of the lubricating oil system.
  • oil reservoirs 13 can be provided.
  • the embodiment of Figure 4b differs in that the filling of the oil reservoir 13, a separate pump 11 is used.
  • This pump 11 may be designed as a high-pressure pump, so as to increase the pressure in the oil reservoir 13 with respect to the lubricating oil system pressure. As a result, the required volume of the oil reservoir can be reduced. In addition, with increased pressure in the oil reservoir 13, the filling of the retarder 12 can be done faster.
  • FIGS. 5a-e show various embodiments of the oil supply for the retarder 12 of a drive arrangement according to the invention; All variants are equipped with a piston accumulator as oil reservoir 13.
  • the piston accumulator has a space for storing the oil and a pressure build-up space 13a on the opposite side; the two rooms are separated by a media burner.
  • the storage space is filled via the filling line 31 with oil from the lubricating oil system 40 of the drive device and wherein the pressure build-up chamber 13 a is pressurized in case of failure via the pressure buildup line 33 from the lubricating oil system 40 and thus ensures that the retarder 12 with oil from the oil reservoir thirteenth is filled.
  • About the drain line 32 oil is discharged into the oil sump 34.
  • this line 34 has an adjustable throttle, with which the braking characteristics, the braking length and the temperature development in the retarder can be selectively influenced.
  • the lubricating oil system 40 includes a lubricating oil pump 41, a lubricating oil heat exchanger 42, and a lubricating oil filter 43.
  • the branch to the oil reservoir 13 may be provided not only after the filter as shown but also elsewhere in the system. About the lubricating oil pipe 30 to the retarder this is reliably lubricated.
  • the Lubricating oil pump 41 is connected to one of the shafts of the drive device, so that the pump continues to run even in case of power failure, as long as the drive device continues to rotate, or if the lubricating oil pump 41 is equipped with an uninterruptible power supply, so that the pump works even in case of power failure.
  • the different variants now differ in the selection, arrangement and circuit of the valves used.
  • the drive device and the design of the contained retarder with its control can be adapted very well to different applications and machines.
  • Fig.5a an embodiment with two 3/2-way valves is shown.
  • the valve 19.2 goes in case of failure - due to the spring load without power supply - in the position 1, so that the pressure build-up space 13a is pressurized from the lubricating oil system.
  • the valve 19.1 is automatically in the position 4, which releases the line 35 from the oil reservoir 13 to the retarder 12, so that it is filled.
  • the valve 19.1 is switched to position 4, while the other valve 19.2 is switched to position 2 to vent the pressure build-up space 13a.
  • the braking time depends on the oil volume in the oil reservoir 13 and the oil volume flow that can be supplied by the lubricating oil system for pressurizing from.
  • the level in the oil reservoir can be monitored with a sensor 23.
  • a circuit of the valves 19.2, 19.1 to position 2 and 4 or to position 1 and 3 is inadmissible and is prevented by circuitry.
  • the variant according to FIG. 5b differs in that only one 4/2-way valve is used as the valve 19.1 and no further valve is required.
  • position 1 the oil reservoir 13 is filled and vented the pressure build-up space 13 a via the retarder 12.
  • position 2 in which the valve goes in case of failure, the pressure build-up space 13 a is pressurized and the oil reservoir 13 is connected to the retarder 12 and filled.
  • a 5/2-way valve is used instead of the 4/2-way valve.
  • the venting of the pressure build-up space 13a can take place via a separate outlet on the valve 19.1, and does not have to take place via the retarder.
  • Fig.5d shows a variant with three valves.
  • a 4/2-way valve (19.3.) Is provided.
  • the retarder 12 is filled via the valve 19.1 from the oil reservoir 13, while on the valve 19.2 of the necessary pressure in the pressure build-up space 13a is generated.
  • the cheaper 2/2-way valves or alternatively 0/1 valves (19.1, 19.2) used here are also more suitable for higher volume flows.
  • higher volume flows are desired.
  • no such high volume flows are necessary because the filling time does not play a major role and the filling line is normally throttled so as not to remove too much oil from the lubricating oil circuit 40 in normal operation.
  • FIG. 5e represents an alternative to the embodiment according to FIG. 5a.
  • the originally present 3/2-way valve which causes the filling and activation of the retard 12
  • the pressurization of the pressure build-up space 13a is switched via the valve 19.2 in the position 1, wherein the valve 19.2 is designed as a 3/2-way valve.
  • the embodiment in Figure 6 shows an oil reservoir which is designed as a float tank 13.1.
  • the pressure necessary for the filling of the retarder 12 is generated by the geodetic height of the high tank 13.1.
  • the Hochtankt 13.1 can be filled via the throttled filling line 31 with a check valve.
  • the filling and activation of the retarder 12 via a simple 2/2-way valve or a 0/1 valve (19.1).
  • Another alternative for the design of the oil reservoir 13 and the pressure build-up for filling the retarder 12 is shown in Figs. 7a and 7b.
  • the oil reservoir 13 is set in case of failure by means of a propellant charge 24 or a compressed air reservoir under pressure.
  • Activation of the retarder 12 is necessary, for example, in that they are spring-loaded.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Transmission Of Braking Force In Braking Systems (AREA)

Abstract

L'invention concerne un dispositif d'entraînement comprenant une transmission à superposition (17), un moteur d'entraînement principal (2) qui est relié à un arbre d'entrée (14) de la transmission à superposition, un ou plusieurs entraînements auxiliaires (3.1,3.2), un ralentisseur (12) hydrodynamique conçu pour freiner l'entraînement auxiliaire (3.1,3.2) et un arbre de sortie (15) de la transmission à superposition qui peut être relié à un engin de travail (1). La transmission à superposition (17) comprend une boîte de vitesses à trains épicycloïdaux (18) comportant une couronne (4), un planétaire (7), un porte-satellites (10) et plusieurs satellites (5), l'arbre d'entrée (14) étant relié à la couronne (4), l'arbre de sortie (15) au planétaire (7), et l'entraînement auxiliaire ou les entraînements auxiliaires (3.1,3.2) étant relié(s) au porte-satellites (10), respectivement par l'intermédiaire d'au moins un étage de transmission, avec un rapport de transmission constant, le ralentisseur (12) étant relié à un entraînement auxiliaire (3.1,3.2). En outre, un réservoir d'huile (13) est prévu et conçu pour permettre le remplissage du ralentisseur (12) en huile provenant de ce réservoir d'huile (13), en cas d'arrêt d'urgence ou de rupture de l'approvisionnement en énergie d'un des entraînements (2,3.1,3.2).
PCT/EP2019/052695 2018-02-09 2019-02-05 Dispositif d'entraînement et procédé pour limiter le régime Ceased WO2019154772A1 (fr)

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DE102018102910.1A DE102018102910A1 (de) 2018-02-09 2018-02-09 Antriebsvorrichtung und Verfahren zur Drehzahllimitierung

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DE102021121301A1 (de) 2021-08-17 2023-02-23 Voith Patent Gmbh Antriebsvorrichtung mit Überlagerungsgetriebe für Turbokompressoren
EP4353906A1 (fr) * 2022-10-12 2024-04-17 BOMAG GmbH Procédé de freinage d'une machine de compactage et machine de compactage
CN118912190A (zh) * 2024-08-02 2024-11-08 中国重汽集团济南动力有限公司 一种齿轮箱润滑油的最佳油位确定方法、系统、设备及介质

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CN110985638A (zh) * 2019-12-02 2020-04-10 中国铁道科学研究院集团有限公司通信信号研究所 一种液压车辆减速器监控系统

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DE102014225738A1 (de) * 2014-12-12 2016-06-16 Siemens Aktiengesellschaft Verfahren zum Betreiben eines Antriebsstrangs

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DE102014210868A1 (de) 2014-06-06 2015-12-17 Voith Patent Gmbh Vorrichtung zur Leistungsübertragung und Maschinenanordnung damit
DE202015104656U1 (de) * 2014-09-22 2015-11-23 Gerald Hehenberger Antriebsstrang einer Energiegewinnungsanlage
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021121301A1 (de) 2021-08-17 2023-02-23 Voith Patent Gmbh Antriebsvorrichtung mit Überlagerungsgetriebe für Turbokompressoren
EP4353906A1 (fr) * 2022-10-12 2024-04-17 BOMAG GmbH Procédé de freinage d'une machine de compactage et machine de compactage
DE102022210736A1 (de) * 2022-10-12 2024-04-18 Bomag Gmbh Verfahren zum abbremsen einer verdichtungsmaschine und verdichtungsmaschine
CN118912190A (zh) * 2024-08-02 2024-11-08 中国重汽集团济南动力有限公司 一种齿轮箱润滑油的最佳油位确定方法、系统、设备及介质

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