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WO2010083991A2 - Procédé pour faire fonctionner un consommateur - Google Patents

Procédé pour faire fonctionner un consommateur Download PDF

Info

Publication number
WO2010083991A2
WO2010083991A2 PCT/EP2010/000304 EP2010000304W WO2010083991A2 WO 2010083991 A2 WO2010083991 A2 WO 2010083991A2 EP 2010000304 W EP2010000304 W EP 2010000304W WO 2010083991 A2 WO2010083991 A2 WO 2010083991A2
Authority
WO
WIPO (PCT)
Prior art keywords
hydraulic
drive
motor
output shaft
drive shaft
Prior art date
Application number
PCT/EP2010/000304
Other languages
German (de)
English (en)
Other versions
WO2010083991A3 (fr
Inventor
Daniel Witte
Helmut Schildknecht
Original Assignee
List Holding Ag
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 List Holding Ag filed Critical List Holding Ag
Publication of WO2010083991A2 publication Critical patent/WO2010083991A2/fr
Publication of WO2010083991A3 publication Critical patent/WO2010083991A3/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • 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
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/46—Automatic regulation in accordance with output requirements
    • F16H61/47—Automatic regulation in accordance with output requirements for achieving a target output speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/20—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by changing the driving speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
    • F04C14/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/08—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the rotational speed
    • 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
    • F16H39/00—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution
    • F16H39/02—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution with liquid motors at a distance from liquid pumps
    • 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
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/44—Control of exclusively fluid gearing hydrostatic with more than one pump or motor in operation
    • F16H61/444—Control of exclusively fluid gearing hydrostatic with more than one pump or motor in operation by changing the number of pump or motor units in operation

Definitions

  • the invention relates to a method for operating a consumer by means of a hydraulic motor, which is supplied by a pumping device with fluid.
  • Hydraulic drives are used to transfer power from electric or diesel drives to slow-speed shafts with high torques.
  • Conventional hydraulic actuators consist of: a) a drive motor for constant speed electric drives; b) a pump that pumps hydraulic oil to c) the hydraulic motor connected to d) hydraulic lines connecting the pump to the motors and e) various ancillary equipment, such as Oil reservoir that collects the leakage current, and a pump that pumps the leak oil back into the main circuit.
  • the hydraulic motor is connected to the hydraulic lines with flexible hoses.
  • a major advantage of this drive system is that the hydraulic motor is flexibly mounted on the output shaft. This is particularly advantageous because the output axis z. B. by thermal expansion of the consumer during operation shifts.
  • the hydraulic motor is relatively lightweight and can be mounted on the output shaft usually without additional support.
  • Another advantage of this drive concept is that very short and extreme load fluctuations (vibrations) in the hydraulic oil are damped, thus preventing damage to the bearing and the output shaft.
  • the pump unit can also be installed at some distance from the output shaft, which is particularly beneficial for consumers at risk of exfoliation.
  • the hydraulic motor has a constant displacement per revolution. Since the hydraulic pressures in the supply line at nominal and maximum conditions are usually standardized in order to standardize components, automatically results in a specific torque for each hydraulic motor, which must be taken into account in the design.
  • the maximum transferable capacity corresponds to the hydraulic pressure gradient times the volume flow of hydraulic oil. Since the engine speed at constant engine displacement is proportional to the volume flow of hydraulic oil (the oil is approximately compressible) and the hydraulic pressure of the engine is approximately constant, the hydraulic pressure in the engine intake is a representative quantity to describe the torque. Since this hydraulic pressure can be limited by means of a pressure relief valve, it is possible with simple means to protect the output shaft from too high a torque load.
  • Another advantage of the hydrodrive is that you can distribute the torque to several hydraulic motors. This is how the output shaft of drive both sides with simple means. With two identical hydraulic motors, the drive torque is half that of a double-sided motor on one drive side. It is also often the case that the consumption of the torque on the output shaft takes place uniformly over a large part of the length. Then the shaft is additionally relieved of hydraulic motors, which are mounted on both sides, and the shaft deflection due to the load decreases.
  • the stroke volume of the pump is varied in conventional systems.
  • the hydraulic pressure in the supply line is kept constant by the consuming hydraulic motor.As the oil consumption in the line increases, the stroke volume of the pump is adjusted automatically so that the pressure does not drop, and vice versa.
  • the advantage of this control concept is that you can install any number of hydraulic motors for a pump station system that has an intake and an exhaust manifold for all hydraulic motors, but the torque for all hydraulic motors is then constant.
  • the stroke of the pump is kept constant and the hydraulic pressure of the motor supply line is allowed to vary.
  • This control concept means that each output shaft has its own pumping system, as otherwise the torques of the different output axles would be interfered with Since the stroke of the pump is kept constant, the speed of the output shaft also remains constant. If the hydraulic motors are very large, a pump to operate is no longer sufficient.
  • the largest axial piston pumps currently available on the market have a stroke of 1000 cc. Up to 500 cc, the pumps can be operated at 1800 rpm, in addition, these pumps must be operated at a lower speed. Therefore, the achievable pumping volume of a 1000 cc pump is not twice as high as that of a 500 cc pump.
  • the maximum continuous speed of a pump with 1000 cc is for example 1200 rpm, which also does not correspond to the electrical mains frequency. It is therefore necessary to have a gearbox for this pump in order to get from the mains speed of 50 Hz (1500 rpm) or 60 Hz (1800 rpm) to 1200 rpm, or one must use a lower-pole electric motor.
  • Hydromotors are always considerably better than the pumps. It is therefore not only wasted electrical energy, but it must also be strongly cooled the oil circuit. This cooling performance is often underestimated, which limits the flexibility of the drive system.
  • the pumping stations must be connected to each other via manifolds and then to the engine.
  • the piping effort, especially for drives with high power is very high.
  • the line length increases at several pumping stations for a drive and thus also the power loss due to friction dissipation in the lines. It does not make sense, therefore Pumping stations too far away from the hydraulic motor to install. Since the pumping stations are very large and take up a lot of space, that is a disadvantage.
  • Oil quantity elastically compressed and the oil flow rate at the engine decreases or decreases. This leads to speed fluctuations on the output shaft.
  • Torque is the inertia (moment of inertia) of the shaft and the
  • the object of the invention is to find a method of the type mentioned above, large hydraulic drives for rotating shafts, the large amounts of circulating Hydraulic oil need to be realized with little effort on hydraulic pump units, the method or a corresponding device provides a speed control with minimized speed fluctuations of the output shaft.
  • the pumping means is associated with a drive shaft and a speed control of an output shaft for the consumer takes place via a speed control of the drive shaft and / or the pumping device has a constant displacement per revolution.
  • the described disadvantages of the hydraulic drive at high powers are inventively improved so that the pump stations are replaced by hydraulic motors that act as pumps.
  • These pump hydraulic motors are mounted on the drive axle and connected via a transmission gearbox with an electric motor or diesel engine.
  • the electric or diesel drive has a variable speed z. B. with frequency converter. In a diesel engine then makes a diesel-electric drive with frequency converter sense.
  • the Pumphydromotoren have a much larger displacement per revolution than axial piston pumps.
  • the nominal speed of these pumped-motor motors is most advantageously around 300 rpm, with a usual rotational speed of the output shaft of 30 rpm.
  • the torque of the drive shaft of the pumped motor is 10 times smaller than that of the output shaft.
  • This translation corresponds to a gearbox that covers the high, mechanically heavily loaded torque range of the drive.
  • the number of required Pumphydromotoren is one to two per hydraulic motor on the output axis and thus by a factor of two to three lower. Only one electric motor per output shaft is needed, because the pump hydraulic motors can be mounted on a drive shaft. The distance between these pump hydraulic motors is lower and the piping effort is considerably reduced. Also reduced is the noise level of the hydro drive. Hydromotors cause comparatively little noise, while axial rotary lobe pumps produce considerable noise.
  • Another advantage of the inventive method is that the frequency converter can react very quickly to load fluctuations. Thus, it is possible to compensate for the oil volume flow fluctuations at the inlet of the hydraulic motor on the output shaft by the load adjustments of the electric motor. This is only partially possible with axial piston pumps, since the control here is hydraulic and therefore relatively sluggish.
  • Another advantage of the inventive drive concept is that the speed control of the drive by a frequency converter, the
  • Electric motor is fed, realized and this frequency converter can be installed relatively far away from the electric motor, without affecting the efficiency of the electric motor
  • Another advantage of the inventive drive concept is that the hydraulic efficiency of the drive is much higher than in the conventional hydro drive. Thus, the required cooling capacity of the hydraulic circuit is smaller and less electrical energy is consumed.
  • Figure 1 is a block diagram representation of a hydraulic drive according to the prior art
  • Figure 2 is a block diagram representation of an electrical drive of a consumer
  • Figure 3 is a block diagram representation of a drive of a consumer with hydraulic speed control
  • Figure 4 is a block diagram representation of an inventive electro-hydraulic drive concept for a consumer.
  • three hydraulic piston pumps 1.1 to 1.3 are connected via a collecting line 2 to a hydraulic motor 3.
  • This hydraulic motor 3 attacks a consumer 4.
  • the piston pumps 1.1 to 1.3 are operated by means of electric motors 9.1 to 9.3, so that hydraulic oil is pumped by the piston pumps 1.1 to 1.3 through the manifold 2 to the hydraulic motor 3. A return flow of the oil goes back to the piston pumps 1.1 to 1.3, which takes place via a common supply line 10.
  • a possible leakage flow flows into a reservoir 5 and is fed back via a pump 6, which in turn is driven by a motor 7, via a heat exchanger 8 in the collecting supply line 10.
  • the motors 9.1 to 9.3 or 7 rotate with constant uncontrolled speed.
  • the required amount of oil is adjusted by changing the stroke of a piston rod of the piston pumps 1.1 to 1.3.
  • an electric motor 9 is provided according to Figure 2, to which a frequency converter 11 is assigned. This sets the frequency for the electric motor 9, wherein the phase angle of the drive axle is measured and used in the frequency converter computationally.
  • a cooling 17 is provided for the frequency converter 11 is still a cooling 17 is provided
  • a drive axle 12 drives a transmission 13 for setting a speed range.
  • An output shaft 14, which leads to the load 4 must be screened against expansion by means of a corresponding compensating device 15, furthermore, a safety clutch 16 is provided, which protects the output shaft 14 in case of overload.
  • an electric motor 9 with a constant and uncontrolled speed drives a hydraulic transmission 18.
  • a speed of an output shaft 14 can be adjusted, wherein a speed range is adjusted via the transmission 13.
  • the output shaft 14 must in turn be protected by a compensation device 15 against expansion and a safety clutch 16 against overload. It drives the consumer 4.
  • the hydraulic transmission 18 must still be cooled by means of a cooling 17.
  • FIG. 4 shows an electrohydraulic drive concept according to the present invention.
  • a frequency converter 11 ensures the power frequency for an electric motor 9, wherein the phase angle of the drive axle is measured and used in the frequency converter 11 computationally.
  • the drive axle 12 drives the transmission 13 to set a speed range.
  • a hydraulic motor 20 sits on the drive axle, which consists in the present embodiment of two hydraulic pumps 21.2 and 21.2 with constant displacement.
  • the amount of oil from the hydraulic motor 20 is supplied via the manifold 2 to the hydraulic motor 3, which operates the consumer 4.
  • a return line 22 connects the hydraulic motor 3 to the hydraulic motor 20.
  • a leakage flow flows into the reservoir 5 and is pumped back via the pump 6, which in turn is driven by the motor 7, via the heat exchanger 8 in the oil circuit.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Auxiliary Drives, Propulsion Controls, And Safety Devices (AREA)
  • Control Of Non-Positive-Displacement Pumps (AREA)

Abstract

L'invention concerne un procédé pour faire fonctionner un consommateur (4) au moyen d'un moteur hydraulique (3) qui est alimenté en fluide par un dispositif de pompe (20) selon lequel un arbre d'entraînement (12) doit être associé au dispositif de pompe (20) et une commande de vitesse d'un arbre d'entraînement pour le consommateur (4) doit avoir lieu par l'intermédiaire d'une commande de vitesse de l'arbre d'entraînement (12) et/ou le dispositif de pompe (20) doit avoir une cylindrée constante par révolution.
PCT/EP2010/000304 2009-01-20 2010-01-20 Procédé pour faire fonctionner un consommateur WO2010083991A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH85/09 2009-01-20
CH852009A CH700301A2 (de) 2009-01-20 2009-01-20 Hydraulische Methode der drehzahlgesteuerten Kraftübertragung auf drehende Wellen.

Publications (2)

Publication Number Publication Date
WO2010083991A2 true WO2010083991A2 (fr) 2010-07-29
WO2010083991A3 WO2010083991A3 (fr) 2010-11-04

Family

ID=42356258

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/000304 WO2010083991A2 (fr) 2009-01-20 2010-01-20 Procédé pour faire fonctionner un consommateur

Country Status (2)

Country Link
CH (1) CH700301A2 (fr)
WO (1) WO2010083991A2 (fr)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3149362A4 (fr) * 2014-06-02 2018-02-21 Project Phoenix LLC Ensemble et système de transmission hydrostatique
US10294936B2 (en) 2014-04-22 2019-05-21 Project Phoenix, Llc. Fluid delivery system with a shaft having a through-passage
US10465721B2 (en) 2014-03-25 2019-11-05 Project Phoenix, LLC System to pump fluid and control thereof
US10539134B2 (en) 2014-10-06 2020-01-21 Project Phoenix, LLC Linear actuator assembly and system
US10544810B2 (en) 2014-06-02 2020-01-28 Project Phoenix, LLC Linear actuator assembly and system
US10598176B2 (en) 2014-07-22 2020-03-24 Project Phoenix, LLC External gear pump integrated with two independently driven prime movers
US10677352B2 (en) 2014-10-20 2020-06-09 Project Phoenix, LLC Hydrostatic transmission assembly and system
US10808732B2 (en) 2014-09-23 2020-10-20 Project Phoenix, LLC System to pump fluid and control thereof
US10865788B2 (en) 2015-09-02 2020-12-15 Project Phoenix, LLC System to pump fluid and control thereof
US11085440B2 (en) 2015-09-02 2021-08-10 Project Phoenix, LLC System to pump fluid and control thereof
US11118581B2 (en) 2014-02-28 2021-09-14 Project Phoenix, LLC Pump integrated with two independently driven prime movers
US20220290545A1 (en) * 2019-08-13 2022-09-15 Spm Oil & Gas Inc. Hydraulic Drive Train for a Frac Pump

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US3953787A (en) * 1974-03-07 1976-04-27 Edward Helbling Drive system
US5141402A (en) * 1991-01-29 1992-08-25 Vickers, Incorporated Power transmission
US5778671A (en) * 1996-09-13 1998-07-14 Vickers, Inc. Electrohydraulic system and apparatus with bidirectional electric-motor/hydraulic-pump unit
JP3892840B2 (ja) * 2002-12-25 2007-03-14 一義 福地 電動モータを利用した油圧駆動装置

Non-Patent Citations (1)

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Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11713757B2 (en) 2014-02-28 2023-08-01 Project Phoenix, LLC Pump integrated with two independently driven prime movers
US12060883B2 (en) 2014-02-28 2024-08-13 Project Phoenix, LLC Pump integrated with two independently driven prime movers
US11118581B2 (en) 2014-02-28 2021-09-14 Project Phoenix, LLC Pump integrated with two independently driven prime movers
US10465721B2 (en) 2014-03-25 2019-11-05 Project Phoenix, LLC System to pump fluid and control thereof
US10294936B2 (en) 2014-04-22 2019-05-21 Project Phoenix, Llc. Fluid delivery system with a shaft having a through-passage
US11280334B2 (en) 2014-04-22 2022-03-22 Project Phoenix, LLC Fluid delivery system with a shaft having a through-passage
US10544861B2 (en) 2014-06-02 2020-01-28 Project Phoenix, LLC Hydrostatic transmission assembly and system
US10544810B2 (en) 2014-06-02 2020-01-28 Project Phoenix, LLC Linear actuator assembly and system
EP3149362A4 (fr) * 2014-06-02 2018-02-21 Project Phoenix LLC Ensemble et système de transmission hydrostatique
US11867203B2 (en) 2014-06-02 2024-01-09 Project Phoenix, LLC Linear actuator assembly and system
US10738799B2 (en) 2014-06-02 2020-08-11 Project Phoenix, LLC Linear actuator assembly and system
US11060534B2 (en) 2014-06-02 2021-07-13 Project Phoenix, LLC Linear actuator assembly and system
US11067170B2 (en) 2014-06-02 2021-07-20 Project Phoenix, LLC Hydrostatic transmission assembly and system
US10598176B2 (en) 2014-07-22 2020-03-24 Project Phoenix, LLC External gear pump integrated with two independently driven prime movers
US10995750B2 (en) 2014-07-22 2021-05-04 Project Phoenix, LLC External gear pump integrated with two independently driven prime movers
US11512695B2 (en) 2014-07-22 2022-11-29 Project Phoenix, LLC External gear pump integrated with two independently driven prime movers
US10808732B2 (en) 2014-09-23 2020-10-20 Project Phoenix, LLC System to pump fluid and control thereof
US11408442B2 (en) 2014-09-23 2022-08-09 Project Phoenix, LLC System to pump fluid and control thereof
US10539134B2 (en) 2014-10-06 2020-01-21 Project Phoenix, LLC Linear actuator assembly and system
US11242851B2 (en) 2014-10-06 2022-02-08 Project Phoenix, LLC Linear actuator assembly and system
US10677352B2 (en) 2014-10-20 2020-06-09 Project Phoenix, LLC Hydrostatic transmission assembly and system
US11054026B2 (en) 2014-10-20 2021-07-06 Project Phoenix, LLC Hydrostatic transmission assembly and system
US11846283B2 (en) 2015-09-02 2023-12-19 Project Phoenix, LLC System to pump fluid and control thereof
US10865788B2 (en) 2015-09-02 2020-12-15 Project Phoenix, LLC System to pump fluid and control thereof
US11085440B2 (en) 2015-09-02 2021-08-10 Project Phoenix, LLC System to pump fluid and control thereof
US12060878B2 (en) 2015-09-02 2024-08-13 Project Phoenix, LLC System to pump fluid and control thereof
US20220290545A1 (en) * 2019-08-13 2022-09-15 Spm Oil & Gas Inc. Hydraulic Drive Train for a Frac Pump

Also Published As

Publication number Publication date
WO2010083991A3 (fr) 2010-11-04
CH700301A2 (de) 2010-07-30

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