EP3497338A1 - Système d'entraînement hydraulique, en particulier sans accumulateur de pression, pour un consommateur et comprenant un consommateur, en particulier pour des presses, et procédé permettant de faire fonctionner un tel système d'entraînement hydraulique - Google Patents

Système d'entraînement hydraulique, en particulier sans accumulateur de pression, pour un consommateur et comprenant un consommateur, en particulier pour des presses, et procédé permettant de faire fonctionner un tel système d'entraînement hydraulique

Info

Publication number
EP3497338A1
EP3497338A1 EP17761799.0A EP17761799A EP3497338A1 EP 3497338 A1 EP3497338 A1 EP 3497338A1 EP 17761799 A EP17761799 A EP 17761799A EP 3497338 A1 EP3497338 A1 EP 3497338A1
Authority
EP
European Patent Office
Prior art keywords
pump
drive
piston
cylinder
hydraulic
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.)
Pending
Application number
EP17761799.0A
Other languages
German (de)
English (en)
Inventor
Manfred Mitze
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.)
MAE Maschinen und Apparatebau Goetzen GmbH
Original Assignee
MAE Maschinen und Apparatebau Goetzen 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 MAE Maschinen und Apparatebau Goetzen GmbH filed Critical MAE Maschinen und Apparatebau Goetzen GmbH
Publication of EP3497338A1 publication Critical patent/EP3497338A1/fr
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members

Definitions

  • Hydraulic in particular pressure accumulatorless, drive arrangement for and with a consumer, in particular for presses, and method for operating a hydraulic drive assembly
  • the invention relates to a hydraulic, in particular pressure accumulator-free, drive arrangement for and with a consumer, in particular for presses having the features of the preamble of claim 1 or 10, and a method for operating a hydraulic drive arrangement having the features of the preamble of claim 4 or 5.
  • the invention is based on a hydraulic drive arrangement with at least one working piston and, if necessary, a supplementary rapid-action piston and, if appropriate, a ring-type, return piston, in particular if it comprises a double-acting, at least one reversibly movable working piston and at least one cylinder chamber -
  • Sending piston / cylinder arrangement comprises, wherein the at least one cylinder chamber or the cylinder chambers at least one of the working piston with fluid pressure acting on the (first) piston chamber and, preferably, at least a second piston chamber comprises / include.
  • the piston chambers can be supplied with pressure medium via pressure lines.
  • At least one pump arrangement is provided with at least one, preferably at least variable speed driven, pump and with at least one at least one pump driving, preferably variable speed, drive.
  • At least one pressure medium tank hydraulically connected or connectable to the piston / cylinder arrangement and the pump arrangement can be provided.
  • the at least one pump can be connected or connectable via a first pressure line to the first piston chamber, so that the hydraulic drive arrangement can be operated by means of at least one single-motor drive train in both directions of movement and, preferably, also reaches high working pressures during the operation.
  • An adjusting device of the at least one pump can be provided with a dropping means for the latter, wherein the delivery flow of the at least one pump can be changed by means of the adjusting device which can be actuated by the adjusting means.
  • the hydraulic accumulatorless hydraulic drive arrangement can comprise a third piston chamber which supplements the first piston chamber is supplied by a pressure line.
  • the pump (s) supplying pressure fluid to the piston chamber (s) can also be driven or driven in rotation speed and, if desired, also in rotational direction.
  • Variable-speed hydraulic drives in particular for large cylinders, are carried out in accordance with WO 2010/020427 or WO 2012/110259, for example.
  • the hydraulic cylinder may be equipped with an additional rapid traverse piston chamber.
  • the disadvantage is the high construction costs for the two motor pump stations. Especially with large consumers, the inverter controls and power supplies used for the motor drive are quite expensive.
  • the large directional control valves for switching the pump delivery flow from the rapid traverse piston to the large piston surface are also expensive.
  • the second is based on WO2010 / 020427 on the concept, in a pressure-storable hydraulic drive arrangement with working piston, supplementary rapid traverse piston and ring-like return piston to provide a direction of rotation variable pump assembly of a variable speed motor with at least two pumps and the three cylinder (or piston) spaces via three pressure lines individually and directly to the pumps to connect such that in both directions a rapid traverse occurs.
  • variable displacement pumps used so far are based on a pump-internal, usually purely hydromechanical torque or pressure control of the delivery flow.
  • the adjustment device (the adjustment system) of the variable displacement pump / s for the piston and possibly the annular space of the working cylinder is characterized by an adjusting means in the form of a hydraulic cylinder with spring return. When the operating pressure of the variable displacement pump increases, the variable displacement pump pivots against the spring and pivots the variable displacement pump back so that the flow rate per pump revolution (displacement) decreases.
  • the drive torque of the drive motor is proportional to the product of hydraulic pressure and displacement of the driven working piston.
  • the spring characteristic By a suitable choice of the spring characteristic, it is possible to keep the engine drive torque almost constant pressure-independent and not to exceed the rated torque of the engine.
  • an electrical adjusting device of the variable displacement is known.
  • the object of the invention is therefore to further develop a generic drive arrangement so that the utilization of the drive motor and if possible also its converter can be improved.
  • a hydraulic accumulator arrangement which may be free of pressure accumulator, for and with a consumer, in particular for presses with the features of claim 1 or 10 and a method with the features of claim 4 or 5, is proposed.
  • the invention based on WO 2010/020427 or WO2012 / 110259, based on the method concept (claim 5), that in a generic hydraulic drive assembly caused by a hydromechanical or mechanical pump regulation or -Verchez change, in particular reduction, the delivery flow of the at least one pump by means of a hydromechanical or mechanical pump control superimposed or the pump adjustment causing externally controllable hydraulic or mechanical drive means is delayed so far until the drive torque of the engine is utilized as much as desired.
  • the invention can u.
  • the drive torque of the motor and the thermal or electrical limits of motor or inverter can be exploited as much as desired.
  • a reduction in the flow rate of the pump may be delayed until the thermal or electrical limits of the motor or inverter have been exploited as much as desired.
  • the speed variability can be achieved with at least one asynchronous motor and at least one frequency converter. If desired, a reversal of the direction of rotation of the pump can be achieved without the motor itself having to reverse its direction of rotation. If desired, further, the swash plate of the (axial piston) pump beyond the angle "0 °" out, in particular in the negative angle range, are rotated, so that the (gear and pressure) ports of the pump each reverse their function.
  • the adjustment of the pump can therefore comprise a known hydraulic cylinder, possibly with (spring) reset. As the operating pressure increases, the pump pivots against the return (spring). When swiveling forwards and / or backwards, the flow rate per pump revolution (displacement) is changed.
  • At least one, preferably external, in particular electrically controlled, drive device is provided for varying the position of the adjusting element of the adjusting device of the at least one pump, and in which the actuating means of the at least one pump are at least one hydromechanical device. sches drive member, such as an actuating cylinder,
  • the at least one drive means for varying the position of the adjusting means of the adjusting device of the at least one pump comprises a (second) pump and one of the (second) pump associated drive means, wherein the (second) pump with the actuating means of at least one pump, in Verstellsinn is fluidically connected, and that by controlling the (second) pump associated drive means with the aid of an external, in particular electrical, the flow rate of the (second) pump influencing control signal, the adjusting means is displaceable in variable positions.
  • the drive device for varying the position of the adjusting means of the adjusting device of the at least one pump of the drive assembly is also hydraulic in this alternative (second) implementation of the invention, although - unlike the first implementation - not the working or operating pressure of the drive assembly itself but the working pressure of a comparatively small, externally driven (further) pump is used.
  • it is in a hydraulic, in particular pressure accumulatorless, drive arrangement for and with a consumer, in particular for presses,
  • At least one, preferably external, in particular electrically controlled, drive means for varying the position of the adjusting means of the adjusting device of the at least one pump is provided, and in which as adjusting means of the at least one pump at least one mechanical drive member, such as an adjusting spindle (51 C), serves,
  • the at least one drive device for varying the position of the adjusting means of the adjusting device of the at least one pump comprises a drive means assigned to the at least one mechanical drive element, and that by controlling the drive means associated with the mechanical drive element (adjusting means) by means of an external, in particular electric, the position of the drive means influencing the control signal, the adjusting means is displaceable in variable positions.
  • the drive device for varying the position of the adjusting means of the adjusting device of the at least one pump of the drive assembly is mechanical in this alternative (third) implementation of the invention, although - unlike the first and second realization - not the pump pressure but the adjustment of the external NEN drive means itself is used.
  • variable-speed motor-pump combinations such as, for example, with a single motor pump station with one or more pumps of which an adjustment according to the invention takes place at least on one pump or with a plurality of motor pump stations each having one or more pumps, at least at a motor pump station providing a flow adjustment according to the invention is.
  • variable-speed hydraulic drives have drive motors that can be loaded for a short time well beyond the rated torque. For example, a factor that is four times faster can be called up for about two seconds, and a 10 percent overrun is allowed for several minutes. The higher limits are due to the thermal load capacity of the motor windings and the power semiconductors of the Inverter determined.
  • the current I is quadratic, the duration t of the current is linear.
  • I 2 t-bill For evaluation of the limits of the system, the respective load collective is evaluated (“I 2 t-bill”) .
  • This potential can be used by the invention in a simple and cost-effective manner, whereas known hydraulic drives automatically limit the engine torque by pivoting in the pump that a higher torque can therefore only be used to a limited extent without the utilization of the inverter and motor utilization values for a short time.
  • Adjustable pump controller without further control modules and sensors z. B. controlled directly from the inverter.
  • the arrangement should preferably be such that determined according to the t with the internal inverter 2 l account by the drive current load factor of the engine and drive the pump is operated as long as possible with a high tilt angle in order to utilize the motor and inverter optimal.
  • the flow rate increased in this way makes it possible to significantly shorten the system cycle time or, alternatively, to select a smaller drive motor. It was also recognized that the above-mentioned, typical load profiles of a press with only a short time higher forces allow it to retrieve significantly higher moments during the work process, if the subsequent rapid traverse and breaks for loading and unloading the system are used again for cooling ,
  • the current degree of utilization as a controlled variable.
  • the load value of the motor and the converter is considered, but on the other hand, the rate of change of this value.
  • the adjustment of the pump, such as the swivel angle, to reduce the engine torque is relatively quickly withdrawn, while at a slowly increasing load value adjustment can be slower or even completely omitted.
  • load factor for motor and drive can be considered according to the invention as a further control variable for adjusting the pump and the knowledge of the respective work process of the entire system. If it is known, for example, that a particularly high power requirement is only needed for a short period of time, then a high degree of adjustment, such as a high tilt angle, can be maintained, although the course of the utilization factor indicates an imminent emergency shutdown.
  • variable-speed drives which have hitherto been carried out according to the state of the art from which the invention is based are based-as already mentioned-only on a pump-internal, usually purely hydromechanical, control of the delivery flow.
  • a pump-internal usually purely hydromechanical
  • the flow rate of the pump With increasing pressure, the flow rate of the pump is automatically withdrawn so far that the drive torque of the motor, which is proportional to the product of hydraulic pressure and displacement remains largely constant.
  • Characteristic of this known control is the fact that the adjustment is done inside the pump and responsible for the motion control inverter has no influence on it.
  • these self-sufficient, purely hydromechanical Governors could alternatively also be designed, for example, such that the operating pressure is kept constant as a manipulated variable for the variation of the displacement (pressure regulator). This was useful in such control for that pump which was connected to the annular space of the cylinder. Its only purpose was to support the cylinder and possibly attached masses against gravity and to prevent cavitation of the pump connected to the annulus during the upward movement.
  • Fig. 1 shows a (first) embodiment of a pressure accumulatorless hydraulic drive assembly with an external, in particular electrically controlled, drive means for Influencing the position (position) of a hydromechanical drive element (adjusting means) of the adjusting device of the at least one pump of the drive arrangement, wherein the drive means hydraulically superimposed on the position of the actuating means for influencing the flow rate of the at least one pump by means of the working pressure of the drive assembly - as a block diagram;
  • FIG. 2 shows a (second) embodiment of an accumulatorless hydraulic drive arrangement with an external, in particular electrically controlled, drive device for influencing the position (position) of a hydromechanical drive element (adjusting means) of the adjusting device of the at least one pump of the drive arrangement, wherein the drive device is the position the actuating means for influencing the flow rate of the at least one pump by means of the working pressure of the drive assembly hydraulically superimposed changed - as a block diagram;
  • 3 shows an alternative realization of a hydraulic drive arrangement with an external, in particular electrically controlled, drive device for influencing the position of a hydromechanical drive element (adjusting means) of the adjusting device of the at least one pump of the drive arrangement, wherein the drive device controls the position of the actuating means for influencing the Flow rate of the at least one pump NEN by means of the working pressure of a separate pump hydraulically changed - as a block diagram;
  • Fig. 4 shows a further alternative realization of a hydraulic drive assembly with an external, in particular electrically controlled, Antnebseinnchtung for influencing the position (position) of a mechanical drive member (adjusting means) of the adjusting device of the at least one pump of the drive assembly, wherein the drive means the position of the mechanical drive member for Influencing the flow rate of the at least one pump by means of a mechanical drive member associated drive means mechanically changed - as a block diagram;
  • FIG. 5 shows a (second) embodiment modified from the further alternative realization according to FIG. 4, as a block diagram
  • FIG. 6 is a comparison with the further alternative embodiment of FIG. 4 or 5 changed (third) embodiment - as a block diagram
  • Fig. 7 shows a relation to the further alternative realization of Fig. 4, 5 or 6 changed (fourth) embodiment - as a block diagram.
  • FIG. 1 is a double-acting, a piston 21, a piston rod 22 and a cylinder chamber comprehensive piston / cylinder assembly 20 can be seen in the reversibly movable piston 21, the cylinder chamber on the one hand in a first piston chamber 23A (or working cylinder) and on the other a second piston space 23C (or annulus or remindholzylinder) surrounding the piston rod 22 divided.
  • a rapid traverse piston not shown in this and the other figures, can be oriented in a direction opposite to the piston rod 22, or in the same direction as the piston rod.
  • the piston / cylinder arrangement 20 is connected to a first pressure line D1 supplying the first piston chamber 23A with a pressure medium and to an optional second pressure line D3 supplying the optional annular space 23C with pressure medium.
  • a single, designed as a servomotor drive 33 drives a double pump in the form of two, in particular variable speed pumps 31, 32 on a single drive shaft 33A.
  • Both pumps are each equipped with a device (50, 51, D1 ', D3') for adjusting their delivery volume.
  • the adjustment takes place on the one hand, in particular inside the pump, in each case by a control device (adjusting device 38, 38A, 38B), in particular in the form of adjusting cylinders 51; 51A, 51 B, the flow in a known manner the current, over the connecting lines D1 'and D3' at her pending operating pressure of the associated pump 31 and 32 following, for example by means of a pump pivoting mechanism 52, changed.
  • a hydraulically upstream adjusting device 50 (hydraulic valve) in the form of a proportional valve; 50A, 50B are used per pump, which responds to hydraulic or, in particular, electrical control variables of an external control, such as in an inverter.
  • the drive device 60 for this overlapping delivery flow adjustment is accordingly of hydromechanical nature and comprises in addition to the connection lines DT and D3 'for the supply of the hydraulic valves 50 with pressurized fluid - the externally controlled and electrically adjustable hydraulic valves 50 via signal lines 150A and 150B. The latter - as described in more detail below - depending on the state of the drive 33 and / or the inverter U, the amount of fluid for adjusting the flow rate of the associated pump 31 and 32 by the hydromechanical drive member 51 A and 51 B.
  • the servomotor 33 closest to the pump 32 is hydraulically connected in the present embodiment with the cylinder serving as a working piston chamber 23A and the other pump 31 with the opposite piston chamber 23C.
  • the pumps 31, 32 are fluidically connected on one side to a tank 40 and on the other side to the piston chamber 23A and to the annular space 23C.
  • the installed on the piston rod 22 encoder 36 reports the current piston position to the drive 33 supplying voltage to the drive U.
  • a possibly present mechanical transmission 37 for the transmission of torque from the drive 33 is associated with both pumps of the same drive train, in particular in order to use motors with relatively high speeds compared to the pumps. It is also helpful if the pump arrangement comprises a brake, in particular in order to promote a switch-valve-less operation.
  • At least one hydraulic valve in particular a proportional valve 50A or 50B, is hydraulically connected in or eg at the ends of at least one connecting line D1 ', D3'.
  • the at least one connecting line D1 ', D3' is provided between the / for at least one of the pumps 32 and 31 associated,, Stellzylinder / n 51 A and 51 B and the pressure lines D1 and D3 of the pumps 32 and 31.
  • Die Actuating cylinder 51 A and 51 B may be integrated into the respectively associated with them pump 32 and 31, respectively.
  • the adjusting cylinders 51 A and 51 B can be subjected to a variable pressure which can be adjusted within the limits of 0 to the applied pump pressure.
  • the respective pump with, in particular in particular one each, for example electrical, control signal externally via the proportional valves 50A and 50B are adjusted.
  • freely programmable control systems can be used in currently available converters.
  • the control algorithm can access all system sizes of the drive (eg engine utilization, engine temperature, tappet travel position, torque and engine speed) for optimal control of the pump displacement, particularly the pump swing angle.
  • the existing sensors for the position, in particular the swivel angle, and pressure can be omitted, because with the current signals of the cylinder encoder and the inverter internally available values for motor current and speed and, if necessary, a mathematical model of the pump behavior swivel angle and system pressure can be calculated indirectly. In addition, it is possible and so far preferred to install the pump without maintenance problems to save space and sound-insulating below the oil level.
  • the connected to the piston chamber 23A pump 32 is, for example, only then adjusted, in particular pivoted back when the degree of utilization of the motor 33 requires this.
  • the pump 31 connected to the annular space 23C is pivoted, for example, so that the pressure on the side of the annular space to compensate for the force of gravity is around 20 bar.
  • control algorithm can access all system variables of the drive 33 (for example, degree of utilization of the engine, engine temperature, travel position of the tappet, torque and speed of the engine), in order to optimize the control of the pump (in particular) the pump swivel angle to use.
  • the pump 32 delivers oil into the piston chamber 23A when the servomotor 33 rotates.
  • the pump 31 sucks oil from the annulus 23C.
  • the oil flow required to fill the piston space 23A serving as the working cylinder can be sucked from the tank 40.
  • the pump 31 is z.
  • the delivery flow is preferably set to the maximum via the adjustment device of each pump. This happens at comparatively low pump pressure.
  • the pump 32 fills the large piston chamber 23A alone.
  • the delivery volume of the pump 32 is thereby withdrawn, optionally pressure-dependent or with superimposing help of the controlled over the inverter proportional valve 50A to a predetermined value.
  • the positioning process is carried out in the usual way by stopping the servomotor 33.
  • the direction of rotation of the servomotor 33 is reversed.
  • the pressurized oil drives the servomotor, which now acts as a generator.
  • the resulting electrical energy can be fed back into the electrical grid.
  • the reversed pump 31 now conveys into the annular space 23C of the piston / cylinder arrangement 20, so that the piston rod 22 retracts at rapid traverse speed.
  • the pump 32 sucks the oil from the piston chamber 23A.
  • the pump 31 is preferably operated at full flow to assist a possibly provided switchable filling valve during emptying of the working cylinder.
  • the utilization value of motor and inverter is considered, on the other hand, but also the rate of change of this value.
  • the swivel angle for reducing the engine torque must be reduced relatively quickly, while with a slowly increasing load value, an adaptation can take place more slowly or even completely cease.
  • the embodiment of Figure 2 each contains a motor pump station for the piston and the annulus.
  • a first and a second drive motor 33C and 33B are provided with inverter.
  • the significantly lower requirements for delivery rate and pressure for the annular space side 23C require only a low engine output and small pumps.
  • a simple fixed displacement pump 34 can be used for the annular space side 23C.
  • the variation of the delivery flow to the annular space side 23C is achieved exclusively via the engine speed.
  • the cylinder space is arranged vertically, it is particularly advantageous to keep the annulus pressure constant by regulating the engine torque.
  • a double-acting piston / cylinder arrangement 20 comprising a working piston 21, a piston rod 22 and a cylinder chamber
  • the reversibly movable working piston 21 moves the cylinder chamber into a first piston chamber 23A (or working cylinder) and on the other hand divided into a surrounding the piston rod 22 annulus 23C (or remindylinder).
  • a rapid motion piston which is provided approximately, can be oriented, as not shown, in a direction pointing in the opposite direction to the piston rod, or in the same direction as the piston rod.
  • the piston / cylinder arrangement 20 is connected to a first pressure line D1 supplying the first piston chamber 23A with a pressure medium and a pressure line D3 supplying the annular space 23C with pressure medium.
  • Two drives 33B and 33C each designed as variable-speed motors, each drive one, in particular variable-speed, pump 32 or 34.
  • Only the pump 33C is equipped with means 50, 51 for adjusting its delivery volume.
  • the adjustment takes place on the one hand, in particular pumpeintem, by a control device, in particular in Shape of an actuating cylinder 51A, which changes the flow rate in a known manner following the current pressure.
  • a hydraulically upstream adjustment device in the form of a proportional valve 50 is used, which responds to hydraulic or, in particular, electrical manipulated variables of an external control, such as in a converter U.
  • the pump flow rate can be adjusted hydraulically depending on an external input signal up to the maximum flow rate.
  • the motor 32C associated pump 32 is hydraulically connected in the present embodiment with the cylinder serving as a working piston chamber 23A. Both pumps 32 and 34 are fluidically connected on one side with a tank 40 and on the other side with the piston chamber 23A and with the annular space 23C.
  • the installed on the piston rod 22 encoder 36 reports the current piston position to the drive 33B and 33C supplied with electrical voltage converter U.
  • the equipment of the two motors 33C and 30 with suitable (not shown in any of the figures, optional) brakes can be a dangerous Falling of the piston 21 under gravity Schwerkraftei flow with vertically installed cylinder unit 20, for example, prevent power failure. On previously used in such cases switching valves can be dispensed with.
  • a small, in particular mechanical, drive means 62; 62A, 62B preferably in the form of a servomotor, used for the adjustment operation. It acts either via a further pump 61, preferably in the form of a small gear pump, on the adjusting piston, ie on a hydromechanical drive member 51 A, 51 B, which is preferably designed as a positioning cylinder ( Figure 3), or it acts on a mechanical drive member 51st C, which is preferably designed as an adjusting spindle ( Figures 4 to 7).
  • a further pump 61 preferably in the form of a small gear pump
  • the at least one pump 31, 32 can also be pivoted without a pending hydraulic pressure.
  • the energy consumption is significantly lower.
  • the control x motor revolutions generate y degrees pump swivel angle
  • a use of the targeted tilting to "0" as an observable security function is possible. borrowed.
  • electrically pivotable pumps are possible to swivel them beyond the zero point. It then change suction and pressure side. In this way, one can also avoid a reversal of the direction of rotation of the motor and, instead, "swivel" the pump, in particular.
  • a simple asynchronous motor with frequency converter can be used instead of the servomotor.
  • Example: For a cylinder with the piston / ring area ratio of 2: 1, two identical pumps with a delivery volume of, for example, a maximum of 40 cm 3 would be selected. When the piston is extended, there is a delivery volume of 40 + 40 80 cm 3 on the piston side.
  • the piston pump can therefore be dimensioned much smaller.
  • the delivery volume can be adjusted so that the pressure in the annulus assumes the desired value (eg, about 5 bar in the downward travel, 20 bar in the upward travel). Since both pumps can be pivoted independently of each other - as shown for example in Figure 6, the swing angle change can be realized with increasing engine utilization.
  • the pumps can be smaller in size (40 + 40 instead of 80 + 40). Noise level and power loss and pump price decrease.
  • piston rod 51 C mechanical drive member, such as
  • Annulus or recoil cylinder 51 C "mechanical drive link, such as

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Fluid Gearings (AREA)

Abstract

L'invention concerne un système d'entraînement (10) hydraulique, en particulier sans accumulateur de pression, pour un consommateur et comprenant un consommateur, en particulier pour des presses, comprenant un ensemble piston/cylindre (20) à double action comportant au moins un piston de travail (21) déplaçable de manière réversible et au moins une chambre de cylindre, dans lequel ladite chambre de cylindre ou les chambres de cylindre comportent au moins une première chambre de piston (23A) soumettant le piston de travail (21) à une pression de fluide et, éventuellement, au moins une deuxième chambre de piston (23C), des conduites sous pression (D1,...) alimentant les chambres de piston en fluide sous pression, au moins un ensemble de pompage (30 ; 30A, 30B), lequel comporte au moins une pompe (31 ; 32) entraînée au moins suivant une vitesse de rotation variable et au moins un entraînement (33) à vitesse de rotation variable entraînant ladite pompe (31, 32), au moins un réservoir de fluide sous pression relié ou pouvant être relié hydrauliquement à l'ensemble piston/cylindre (20) et à l'ensemble de pompage (30 ; 30A, 30B), dans lequel ladite pompe (31) est reliée ou peut être reliée à la première chambre de piston (23A) par le biais d'une première conduite sous pression (D1), de sorte que l'ensemble d'entraînement (10) hydraulique peut fonctionner au moyen d'une seule chaîne cinématique dotée d'un seul moteur dans au moins une direction de déplacement et que des pressions de travail élevées sont atteintes lors de l'étape de travail. Selon l'invention, une utilisation à pleine charge améliorée du moteur d'entraînement et autant que possible également de son convertisseur est obtenue par au moins un cylindre de réglage (51 ; 51A) hydromécanique respectif de ladite pompe (32), une conduite de liaison (D1') hydraulique qui est active entre le cylindre de réglage (51 ; 51A) et la conduite sous pression (D1) disposée entre ladite pompe (32) et la chambre de piston (23A) qui lui est associée, ainsi qu'au moins une soupape hydraulique, en particulier une soupape proportionnelle (50 ; 50A), ladite soupape hydraulique étant active hydrauliquement dans ladite conduite de liaison (D1') entre le cylindre de réglage (51 ; 51A) et la conduite sous pression (D1) de telle sorte que, par variation de la position de cette soupape hydraulique au moyen d'un signal de réglage externe, en particulier électrique, influençant la position de la soupape hydraulique, le cylindre de réglage (51 ; 51A) peut être soumis à une pression variable.
EP17761799.0A 2016-08-11 2017-08-11 Système d'entraînement hydraulique, en particulier sans accumulateur de pression, pour un consommateur et comprenant un consommateur, en particulier pour des presses, et procédé permettant de faire fonctionner un tel système d'entraînement hydraulique Pending EP3497338A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102016009691 2016-08-11
DE102016011778.8A DE102016011778A1 (de) 2016-08-11 2016-10-04 Hydraulische, insbesondere druckspeicherlose, Antriebsanordnung für und mit einem Verbraucher, insbesondere für Pressen, sowie Verfahren zum Betreiben einer solchen hydraulischen Antriebsanordnung
DE102017003963.1A DE102017003963A1 (de) 2016-08-11 2017-04-25 Hydraulische, insbesondere druckspeicherlose, Antriebsanordnung für und mit einem Verbraucher, insbesondere für Pressen, sowie Verfahren zum Betreiben einer hydraulischen Antriebsanordnung
PCT/EP2017/000971 WO2018028832A1 (fr) 2016-08-11 2017-08-11 Système d'entraînement hydraulique, en particulier sans accumulateur de pression, pour un consommateur et comprenant un consommateur, en particulier pour des presses, et procédé permettant de faire fonctionner un tel système d'entraînement hydraulique

Publications (1)

Publication Number Publication Date
EP3497338A1 true EP3497338A1 (fr) 2019-06-19

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EP17761799.0A Pending EP3497338A1 (fr) 2016-08-11 2017-08-11 Système d'entraînement hydraulique, en particulier sans accumulateur de pression, pour un consommateur et comprenant un consommateur, en particulier pour des presses, et procédé permettant de faire fonctionner un tel système d'entraînement hydraulique

Country Status (3)

Country Link
EP (1) EP3497338A1 (fr)
DE (2) DE102016011778A1 (fr)
WO (1) WO2018028832A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202018003042U1 (de) * 2018-06-29 2019-10-01 M A E Maschinen- Und Apparatebau Götzen Gmbh Hydraulischer Zylinderantrieb und hydraulischer Pressenantrieb
DE102021200407A1 (de) 2021-01-18 2022-07-21 Zf Friedrichshafen Ag Hydraulikvorrichtung für ein elektrifiziertes Nutzfahrzeug, Steuereinrichtung für eine Hydraulikvorrichtung und Verfahren zum Betreiben einer Hydraulikvorrichtung
DE102021123914A1 (de) 2021-09-15 2023-03-16 HMS - Hybrid Motion Solutions GmbH Hydraulisches Antriebssystem mit einer 2x2Q Pumpeneinheit
DE102022203979A1 (de) 2022-04-25 2023-10-26 Robert Bosch Gesellschaft mit beschränkter Haftung Hydraulischer Linearantrieb

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Publication number Priority date Publication date Assignee Title
DE4335403C1 (de) * 1993-10-18 1994-12-15 Karl Hehl Hydraulikeinrichtung
DE10259315C5 (de) * 2002-12-18 2009-07-02 Brueninghaus Hydromatik Gmbh Regelvorrichtung für einen Hydromotor
US8033107B2 (en) * 2006-06-02 2011-10-11 Brueninghaus Hydromatik Gmbh Hydrostatic drive having volumetric flow equalisation
DE102007007005B4 (de) * 2007-02-08 2021-12-02 Robert Bosch Gmbh Elektrohydraulische Steueranordnung
DE102008039011B4 (de) 2008-08-21 2020-01-16 MAE Maschinen- u. Apparatebau Götzen GmbH Druckspeicherlose hydraulische Antriebsanordnung sowie Verfahren zum druckspeicherlosen hydraulischen Antreiben eines Verbrauchers
US8522543B2 (en) * 2008-12-23 2013-09-03 Caterpillar Inc. Hydraulic control system utilizing feed-forward control
DE102010027183A1 (de) * 2010-07-14 2012-01-19 Robert Bosch Gmbh Hydroaggregat
DE102011011750A1 (de) 2011-02-18 2012-08-23 MAE Maschinen- u. Apparatebau Götzen GmbH Druckspeicherlose hydraulische Antriebsanordnung für und mit einem Verbraucher, insbesondere für Pressen sowie Verfahren zum Betreiben einer solchen druckspeicherlosen hydraulischen Antriebsanordnung
US8857168B2 (en) * 2011-04-18 2014-10-14 Caterpillar Inc. Overrunning pump protection for flow-controlled actuators
US20120297758A1 (en) * 2011-05-23 2012-11-29 Caterpillar, Inc. Large Displacement Variator

Also Published As

Publication number Publication date
DE102017003963A1 (de) 2018-02-15
WO2018028832A1 (fr) 2018-02-15
DE102016011778A1 (de) 2018-02-15
WO2018028832A4 (fr) 2018-04-05

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